EP2032834B1 - Fuel injection device for an internal combustion engine - Google Patents

Fuel injection device for an internal combustion engine Download PDF

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Publication number
EP2032834B1
EP2032834B1 EP07728518A EP07728518A EP2032834B1 EP 2032834 B1 EP2032834 B1 EP 2032834B1 EP 07728518 A EP07728518 A EP 07728518A EP 07728518 A EP07728518 A EP 07728518A EP 2032834 B1 EP2032834 B1 EP 2032834B1
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EP
European Patent Office
Prior art keywords
chamber
pressure
fuel injection
injection device
valve element
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.)
Not-in-force
Application number
EP07728518A
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German (de)
French (fr)
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EP2032834A1 (en
Inventor
Falko Bredow
Martin Katz
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP2032834A1 publication Critical patent/EP2032834A1/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
    • 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
    • F02M63/0054—Check 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
    • 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
    • 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
    • F02M2200/706—Valves for filling or emptying hydraulic chamber

Definitions

  • the invention relates to a fuel injection device for an internal combustion engine according to the preamble of claim 1.
  • a valve element is arranged in a housing, which in the region of a fuel outlet opening has a total acting in the opening direction of the valve element pressure surface.
  • a control surface acting in the closing direction is present, which delimits a control chamber. The control surface acting in the closing direction is greater overall than the pressure surface acting in the opening direction when the valve element is open.
  • a high fuel pressure is present at a region of the pressure surface acting in the opening direction and at the control surface acting in the closing direction, as is provided, for example, by a fuel rail.
  • the pressure applied to the control surface is lowered until the hydraulic force resultant in the opening direction on the pressure surface exceeds the force acting in the closing direction. As a result, opening of the valve element is effected.
  • a hydraulic pressure booster for a fuel injection device is off US 2003/0116640 A1 known, in which between a first larger piston and a second smaller piston, a leakage gap is present.
  • a check valve serves as a pressure-holding valve, which is intended to prevent the high-pressure fuel from flowing out.
  • Object of the present invention is to develop a fuel injection device of the type mentioned so that the closing force is increased to close the nozzle needle and that it works reliably.
  • the inventively provided check valve now prevents the control piston, when the nozzle needle comes into contact with the valve seat, on a "fluid cushion" is seated, which was not available before opening the valve element. In the worst case, this fluid cushion would be at each opening and Enlarge closing operation of the valve element until an opening of the valve element would not be possible at all.
  • a valve element of the check valve is acted upon by a spring in its closed position.
  • the valve element is securely held in the pressureless idle state of the fuel injection device by such a spring.
  • such a spring allows the setting of a certain opening-pressure difference, whereby a secure closing of the nozzle needle is ensured.
  • a valve element of the check valve has such a maximum lift that a predetermined maximum time interval between a closing and a subsequent opening of the valve element can be maintained. Especially for multiple injections within a working cycle very short time intervals between a closing and opening of the valve element are required. By limiting the maximum stroke of the check valve element ensures that the check valve can close quickly when the pressure in the hydraulic coupling chamber begins to decrease at the beginning of an opening operation.
  • a gap between the control piston and a housing section bounding the coupling space to a high-pressure chamber can be designed such that opening of the nozzle needle takes place with a delay.
  • the smallest quantity capability of the fuel injection device according to the invention is improved: During an opening movement of the control piston, fluid passes through the gap into the coupling space, which leads to a delayed reaction of the nozzle needle. This is different when closing, where no later than when the spool comes into contact with the nozzle needle, an immediate closing of the nozzle needle is forced.
  • an internal combustion engine carries the reference numeral 10. Overall, it serves to drive a motor vehicle, not shown.
  • a high-pressure conveyor 12 conveys fuel from a fuel reservoir 14 into a fuel pressure accumulator 16 ("rail"). In this, the fuel, such as diesel or gasoline, stored under very high pressure.
  • the fuel such as diesel or gasoline, stored under very high pressure.
  • To the rail 16 a plurality of fuel injection devices 20 are connected by means of a high pressure port 18, which inject the fuel directly into them associated combustion chambers 22.
  • the fuel injection devices 20 also each have a low-pressure connection 24, via which they are connected to a low-pressure region, in the present case to the fuel reservoir 14.
  • the fuel injection device 20 comprises a housing 26 having a nozzle body 28, a main body 30 and an end body 32.
  • a stepped recess 34 in which a needle-like valve element 36 is received. This is in two parts: It consists of a control piston 38 and a nozzle needle 40th
  • the nozzle needle 40 has pressure surfaces 42, which delimit a pressure chamber 44 and their hydraulic force resulting in the opening direction of the nozzle needle 40 shows. At her in FIG. 2 lower end, the nozzle needle 40 works in FIG. 2 not shown manner with a housing-side valve seat (without reference numerals) together. In this way, fuel outlet openings 46 can be separated from the pressure chamber 44 or connected thereto.
  • the nozzle needle 40 has a portion 48 with a smaller and a portion 50 with larger Diameter up. With the section 50, the nozzle needle 40 is guided longitudinally displaceable in the nozzle body 28.
  • the control piston 38 is received in the main body 30.
  • An in FIG. 2 Upper end portion of the control piston 38 is worked out as a guide, which is received and guided in the end body 32.
  • a spring 52 is supported on a shoulder formed by an annular collar (without reference numeral) on the control piston 38 and acted upon in the closing direction.
  • upper axial end surface of the control piston 38 forms a hydraulic control surface 54 acting in the closing direction of the valve element 36. It defines, together with the end body 32, a hydraulic control chamber 56.
  • the control chamber 56 is connected via an inlet throttle 58 in the end body 32 with a high pressure chamber 60, which can be referred to as a storage space due to its large volume and which is connected to the high pressure port 18.
  • the control chamber 56 is further connected to an electromagnetically actuated 2/2-way switching valve 64 through an outlet throttle 62, which is incorporated in the end body 32. Depending on the switching position, this connects or blocks the outlet throttle 62 to the low pressure port 24.
  • the high pressure chamber 60 is further, in yet to be shown manner, connected via a connecting channel 66 to the pressure chamber 44.
  • FIG. 3 The guide element 68 then has a step-shaped through-hole (without reference numeral), whose in FIG. 3 Upper portion forms a guide portion 70.
  • the guide element 72 is slightly larger than the diameter of the portion 50 of the nozzle needle 40, but smaller than the diameter of the control piston 38 in the region which is guided in the end body 32.
  • control piston 38 below the end portion 72 still has an end pin 74 whose diameter is smaller than that of the end portion 72 and also smaller than the control piston 38 adjacent portion of the nozzle needle 40.
  • end pin 74 Approximately at the axial height of this end pin 74 extends from the through hole in the guide member 68 radially inwardly of a circumferential annular collar 76, which forms a stop for the nozzle needle 40, since its inside diameter is smaller than the outside diameter of the end region of the nozzle needle 40 adjacent to it.
  • the stop 76 is not absolutely necessary.
  • the annular space formed between the end journal 74, the end region 72, the nozzle needle 40 and the guide element 68 is referred to as a coupling space 78. It is, as will be explained in more detail below, part of a hydraulic coupler 80, through which the movements of the control piston 38 and the nozzle needle 40 are coupled together.
  • the hydraulic coupler 80 also includes a check valve 82 having a valve member 84 formed as a ball, which is acted upon by a valve spring 86 in a closed position. In the open state, the check valve 82 connects the hydraulic coupling chamber 78 with the high pressure chamber 60. The check valve 82 is aligned so that it opens away from the coupling chamber 78 to the high pressure chamber 60 out.
  • a lying in the guide member 68 portion of the connecting channel 66 includes a flow restrictor 88.
  • An opening portion 90 of the connecting channel 66 to the high-pressure chamber 60 toward is funnel-shaped.
  • the fuel injection device 20 operates as follows: In the initial state, with de-energized switching valve 64, the hydraulic control chamber 56 is separated from the low pressure port 24 and connected via the inlet throttle 58 to the high pressure port 18 and thus to the rail 16. Due to a certain leakage between the guide portion 70 of the guide member 68 and the end portion 72 of the control piston 38 as well as leakage between the nozzle needle 40 and the nozzle body 28 in section 50, this pressure is also in the coupling chamber 78 at. Overall, in this constellation results in a force acting in the closing direction of the valve member 36, which presses this against the valve seat in the region of the fuel outlet openings 46.
  • the switching valve 64 is returned to its closed position, in which the connection of the hydraulic control chamber 56 is locked to the low pressure port 24.
  • the pressure in the hydraulic control chamber 56 increases.
  • the control piston 38 is again moved in the closing direction, since the pressure in the coupling chamber 78 is initially lower than in the hydraulic control chamber 56.
  • the pressure in the coupling chamber 78 increases due to the reduction in volume again, which ultimately leads to a total in the closing direction of the nozzle needle 40 leads to this acting force.
  • the movement of the nozzle needle 40 is at an end when this with its in FIG. 2 bottom end rests again on the housing-side valve seat and thus no fuel can escape through the fuel outlet openings 46.
  • the control piston 38 Since, as already mentioned above, in the meantime fuel has passed from the high-pressure chamber 60 and the pressure chamber 44 into the coupling chamber 78, the control piston 38 encounters a "fuel cushion" at the end of its closing movement, which leads to a dynamic pressure increase in the coupling chamber 78 to a pressure , which is greater than the pressure in the high-pressure chamber 60. As a result, the check valve 82 opens, so that the fuel which has penetrated into the coupling chamber 78 can escape into the high-pressure chamber 60. At the end of its closing movement, therefore, the control piston 38 again comes into abutment against the nozzle needle 40.
  • the valve element 36 must be able to open again immediately after it has reached its closed position.
  • the prerequisite for this is that the coupling space 78, after the "excess" fuel present in the coupling space 78 has been removed via the check valve 82 into the high-pressure chamber 60, again forms a closed volume as quickly as possible, which couples the nozzle needle 40 to the opening movement of the control piston 38.
  • This is achieved by limiting the stroke of the valve member 84 of the check valve 82 to a very small maximum lift. If the pressure in the coupling chamber 78 thus drops again due to an opening movement of the control piston 38, the valve element 84 has to travel only a small stroke until it is in its closed position again and thus the coupling space 78 can form a closed volume.
  • the configuration of the mouth region 90 of the connecting channel 66 in the form of a funnel which widens towards the high-pressure chamber 60 has the following effect: Due to the opening and closing of the valve element 36, pressure oscillations occur in the high-pressure chamber 60, which, however, are hardly noticeable there due to the size of the high-pressure chamber 60 , However, the connecting channel 66 and the pressure chamber 44 have a significantly smaller volume than the high-pressure chamber 60, so that pressure fluctuations would have an increased effect there and thus would reduce the injection accuracy.
  • the funnel-shaped configured mouth region 90 attacks: Through this impact waves striking the mouth region 90 are "dispersed" or reduced, so that the pressure fluctuations are transmitted only reduced in the connecting channel 66 into it. Therefore, the fuel can be metered with the fuel injection device 20 presented here with particularly high accuracy.

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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

A fuel injection device for an internal combustion engine includes a housing and a valve element arranged within the housing. The valve element interacts with a valve seat lying in the region of a fuel outlet opening. It is proposed that at least one control piston and a nozzle needle of the valve element be coupled to one another via a hydraulic coupler. The hydraulic coupler has a coupling space and a non-return valve connected to the coupling space and which opens away therefrom.

Description

Stand der TechnikState of the art

Die Erfindung betrifft eine Kraftstoff-Einspritzvorrichtung für eine Brennkraftmaschine nach dem Oberbegriff des Anspruchs 1.The invention relates to a fuel injection device for an internal combustion engine according to the preamble of claim 1.

Vom Markt her bekannt ist eine Kraftstoff-Einspritzvorrichtung, mit der der Kraftstoff direkt in einen ihr zugeordneten Brennraum einer Brennkraftmaschine eingespritzt werden kann. Hierzu ist in einem Gehäuse ein Ventilelement angeordnet, welches im Bereich einer Kraftstoff-Austrittsöffnung eine insgesamt in Öffnungsrichtung des Ventilelements wirkende Druckfläche aufweist. Am entgegengesetzten Ende des Ventilelements ist eine in Schließrichtung wirkende Steuerfläche vorhanden, welche eine Steuerraum begrenzt Die in Schließrichtung wirkende Steuerfläche ist insgesamt größer als die bei geöffnetem Ventilelement in Öffnungsrichtung wirkende Druckfläche.From the market known is a fuel injection device with which the fuel can be injected directly into its associated combustion chamber of an internal combustion engine. For this purpose, a valve element is arranged in a housing, which in the region of a fuel outlet opening has a total acting in the opening direction of the valve element pressure surface. At the opposite end of the valve element, a control surface acting in the closing direction is present, which delimits a control chamber. The control surface acting in the closing direction is greater overall than the pressure surface acting in the opening direction when the valve element is open.

Bei geschlossener Kraftstoff-Einspritzvorrichtung liegt an einem Bereich der in Öffnungsrichtung wirkenden Druckfläche und an der in Schließrichtung wirkenden Steuerfläche ein hoher Kraftstoffdruck an, wie er beispielsweise von einer Kraftstoff-Sammelleitung (Rail) bereitgestellt wird. Zum Öffnen des Ventilelements wird der an der Steuerfläche anliegende Druck abgesenkt, bis die in Öffnungsrichtung wirkende hydraulische Kraftresultierende an der Druckfläche die in Schließrichtung wirkende Kraft übersteigt. Hierdurch wird ein Öffnen des Ventilelements bewirkt.When the fuel injection device is closed, a high fuel pressure is present at a region of the pressure surface acting in the opening direction and at the control surface acting in the closing direction, as is provided, for example, by a fuel rail. To open the valve element, the pressure applied to the control surface is lowered until the hydraulic force resultant in the opening direction on the pressure surface exceeds the force acting in the closing direction. As a result, opening of the valve element is effected.

Zur Reduzierung der Leckagemenge bei Kraftstoff-Einspritzvorrichtungen wurde bereits in WO 2007/012510 A1 vorgeschlagen, ein Ventilelement zum Öffnen und Schließen von Kraftstoff-Eintrittsöffnungen zweiteilig auszuführen und beide Teile dem Hochdruck des von der Kraftstoff-Sammelleitung gelieferten Einspritzdrucks auszusetzen. Bei dieser Art von Kraftstoffinjektoren sind die in Öffnungsrichtung und in Schließrichtung wirkenden Flächen dem gleichen Hochdruck ausgesetzt, so dass die auf das Ventilelement wirkende Schließfeder nicht zum Aufbringen der erforderlichen Schließkraft für ein schnelles Schließen der Kraftstoff-Austrittsöffnungen ausreichtTo reduce the leakage amount in fuel injectors has already been in WO 2007/012510 A1 proposed to make a valve element for opening and closing of fuel inlet openings in two parts and to suspend both parts of the high pressure of the injection pressure supplied by the fuel rail. In this type of fuel injectors, the surfaces acting in the opening direction and the closing direction are exposed to the same high pressure, so that the closing spring acting on the valve element is not sufficient to apply the required closing force for a quick closing of the fuel outlet openings

Aus DE 101 60 191 A1 ist ein Servor-Ventil mit einem ersten Ventilkolben und einem zweiten Ventilkolben bekannt, welche über einen Kopplerraum antriebgekoppelt sind. Der Kopplerraum ist über ein Rückschlagventil mit einem Hochdruckanschluss verbunden, um eine Druckschwelle aufzubauen, bis zu welcher der Kopplerraum aus der Absteuermenge gefüllt werden kann. Dadurch wird die Absteuermenge nicht ungenutzt in die Niederdruckseite abgeleitetOut DE 101 60 191 A1 a servo-valve with a first valve piston and a second valve piston is known, which are drive-coupled via a coupler space. Of the Coupler space is connected via a check valve to a high pressure port to build a pressure threshold to which the coupler space can be filled from the Absteuermenge. As a result, the Absteuermenge is not dissipated unused in the low pressure side

Ein hydraulischer Druckverstärker für eine Kraftstoff-Einspritzvorrichtung ist aus US 2003/0116640 A1 bekannt, bei dem zwischen einem ersten größeren Kolben und einem zweiten kleineren Kolben ein Leckagespalt vorhanden ist. Ein Rückschlagventil dient dabei als Druckhalteventil, das ein Abströmen des unter hohem Druck eingeschlossenen Kraftstoffs verhindern soll.A hydraulic pressure booster for a fuel injection device is off US 2003/0116640 A1 known, in which between a first larger piston and a second smaller piston, a leakage gap is present. A check valve serves as a pressure-holding valve, which is intended to prevent the high-pressure fuel from flowing out.

Offenbarung der ErfindungDisclosure of the invention

Aufgabe der vorliegenden Erfindung ist es, eine Kraftstoff-Einspritzvorrichtung der eingangs genannten Art so weiterzubilden, dass die Schließkraft zum Schließen der Düsennadel erhöht wird und dass sie zuverlässig arbeitet.Object of the present invention is to develop a fuel injection device of the type mentioned so that the closing force is increased to close the nozzle needle and that it works reliably.

Diese Aufgabe wird durch eine Kraftstoff-Einspritzvorrichtung mit den Merkmalen des Anspruchs 1 gelöst Vorteilhafte Weiterbildungen der Erfindung sind in Unteransprüchen genannt. Wichtige Merkmale der Erfindung finden sich ferner in der nachfolgenden Beschreibung und in der Zeichnung. Dabei sei an dieser Stelle darauf hingewiesen, dass die Merkmale auch in ganz unterschiedlichen Kombinationen für die Erfindung wesentlich sein können, ohne dass hierauf explizit hingewiesen wird.This object is achieved by a fuel injection device having the features of claim 1. Advantageous developments of the invention are specified in subclaims. Important features of the invention can also be found in the following description and in the drawing. It should be noted at this point that the features can also be essential in very different combinations for the invention, without being explicitly pointed out.

Bei der erfindungsgemäßen Kraftstoff-Einspritzvorrichtung mit dem vorgesehenen Rückschlagventil tritt beim Schließvorgang in dem den Steuerkolben umgebenden Hochdruckraum ein größerer Druck als im Kopplerraum auf. Dadurch wirkt im Hochdruckraum eine Schließkraft auf den Steuerkolben, die größer ist als die in Öffnungsrichtung im Kopplerraum auf den Steuerkolben wirkende Kraft. Durch das Rückschlagventil kann weiterhin der Koppelraum nach einem Schließvorgang des Ventilelements entlastet werden. Dem liegt folgende Überlegung zugrunde: Bei geöffnetem Ventilelement und der damit einhergehenden Druckabsenkung im Koppelraum kommt es aufgrund unvermeidbarer Leckagen zu einem Zufluss von Hydraulikfluid in den Koppelraum. Dies bedeutet, dass sich beim Schließen des Ventilelements im Koppelraum mehr Fluid befindet als vor dem Öffnen. Das erfindungsgemäß vorgesehene Rückschlagventil verhindert nun, dass der Steuerkolben dann, wenn die Düsennadel am Ventilsitz in Anlage kommt, auf einem "Fluidpolster" aufsitzt, welches vor dem Öffnen des Ventilelements noch nicht vorhanden war. Im ungünstigsten Fall würde sich dieses Fluidpolster bei jedem Öffnungs- und Schließvorgang des Ventilelements vergrößern, bis ein Öffnen des Ventilelements überhaupt nicht mehr möglich wäre. Durch das Rückschlagventil wird also die Zuverlässigkeit im Betrieb der erfindungsgemäßen Kraftstoff-Einspritzvorrichtung, vor allem die Reproduzierbarkeit von Ausgangs- und Endzustand, deutlich verbessert.In the fuel injection device according to the invention with the proposed check valve occurs during the closing process in the surrounding the control piston high-pressure chamber to a greater pressure than in the coupler space. As a result, a closing force acts on the control piston in the high-pressure chamber, which force is greater than the force acting on the control piston in the opening direction in the coupler space. Through the check valve can continue to be relieved of the coupling space after a closing operation of the valve element. This is based on the following consideration: When the valve element is open and the associated pressure reduction in the coupling space occurs due to unavoidable leakage to an inflow of hydraulic fluid in the coupling space. This means that more fluid is present when closing the valve element in the coupling space than before opening. The inventively provided check valve now prevents the control piston, when the nozzle needle comes into contact with the valve seat, on a "fluid cushion" is seated, which was not available before opening the valve element. In the worst case, this fluid cushion would be at each opening and Enlarge closing operation of the valve element until an opening of the valve element would not be possible at all. By the check valve thus the reliability in operation of the fuel injection device according to the invention, especially the reproducibility of the initial and final state, significantly improved.

In einer ersten vorteilhaften Weiterbildung wird vorgeschlagen, das ein Ventilelement des Rückschlagventils von einer Feder in seine Schließposition beaufschlagt wird. Zum einen wird durch eine solche Feder das Ventilelement auch im drucklosen Ruhezustand der Kraftstoff-Einspritzvorrichtung sicher gehalten. Zum anderen gestattet eine solche Feder die Einstellung einer bestimmten Öffnungs-Druckdifferenz, wodurch ein sicheres Schließen der Düsennadel gewährleistet wird.In a first advantageous embodiment, it is proposed that a valve element of the check valve is acted upon by a spring in its closed position. On the one hand, the valve element is securely held in the pressureless idle state of the fuel injection device by such a spring. On the other hand, such a spring allows the setting of a certain opening-pressure difference, whereby a secure closing of the nozzle needle is ensured.

Besonders vorteilhaft ist es, wenn ein Ventilelement des Rückschlagventils einen solchen maximalen Hub aufweist, dass ein vorgegebener maximaler zeitlicher Abstand zwischen einem Schließen und einem nachfolgenden Öffnen des Ventilelements eingehalten werden kann. Vor allem für Mehrfacheinspritzungen innerhalb eines Arbeitsspiels sind sehr kurze zeitliche Abstände zwischen einem Schließen und einem Öffnen des Ventilelements erforderlich. Durch eine Begrenzung des maximalen Hubs des Rückschlagventilelements wird gewährleistet, dass das Rückschlagventil schnell schließen kann, wenn der Druck im hydraulischen Koppelraum zu Beginn eines Öffnungsvorgangs abzusinken beginnt.It is particularly advantageous if a valve element of the check valve has such a maximum lift that a predetermined maximum time interval between a closing and a subsequent opening of the valve element can be maintained. Especially for multiple injections within a working cycle very short time intervals between a closing and opening of the valve element are required. By limiting the maximum stroke of the check valve element ensures that the check valve can close quickly when the pressure in the hydraulic coupling chamber begins to decrease at the beginning of an opening operation.

Ein Spalt zwischen dem Steuerkolben und einem den Koppelraum zu einem Hochdruckraum begrenzenden Gehäuseabschnitt kann so ausgelegt sein, dass ein Öffnen der Düsennadel verzögert erfolgt. Hierdurch wird die Kleinstmengenfähigkeit der erfindungsgemäßen Kraftstoff-Einspritzvorrichtung verbessert: Bei einer Öffnungsbewegung des Steuerkolbens gelangt nämlich durch den Spalt Fluid in den Koppelraum, der zu einer verzögerten Reaktion der Düsennadel führt. Dies ist anders beim Schließen, wo spätestens dann, wenn der Steuerkolben an der Düsennadel in Anlage kommt, ein sofortiges Schließen der Düsennadel erzwungen wird.A gap between the control piston and a housing section bounding the coupling space to a high-pressure chamber can be designed such that opening of the nozzle needle takes place with a delay. In this way, the smallest quantity capability of the fuel injection device according to the invention is improved: During an opening movement of the control piston, fluid passes through the gap into the coupling space, which leads to a delayed reaction of the nozzle needle. This is different when closing, where no later than when the spool comes into contact with the nozzle needle, an immediate closing of the nozzle needle is forced.

Die Präzision bei der Kraftstoff-Einspritzung und die Reproduzierbarkeit werden nochmals verbessert, wenn die Mündung des Verbindungskanals zum Hochdruckraum hin so ausgebildet ist, dass Druckwellen reduziert werden. Hierdurch wird der Tatsache Rechnung getragen, dass Druckwellen im Hochdruckraum aufgrund von dessen vergleichsweise großem Volumen dort eine eher geringe Rolle spielen, was für den ein vergleichsweise kleines Volumen aufweisenden Verbindungskanal und den Druckraum unmittelbar stromaufwärts vom Ventilsitz nicht gilt. Durch eine entsprechende Ausgestaltung der Mündung können die im Hochdruckraum auftretenden Druckwellen zumindest in Richtung des Verbindungskanals reduziert beziehungsweise gedämpft werden. Eine einfache Möglichkeit hierzu besteht darin, die Mündung trichterförmig auszubilden. Hierdurch wird erreicht, dass auf die Mündung auftreffende Druckwellen "totlaufen".The precision in the fuel injection and the reproducibility are further improved when the mouth of the connecting channel to the high pressure chamber is formed so that pressure waves are reduced. In this way, the fact is taken into account that pressure waves in the high-pressure chamber because of its comparatively large volume there play a rather minor role, which does not apply to the comparatively small volume having connecting channel and the pressure chamber immediately upstream of the valve seat. By a corresponding design of the mouth, the pressure waves occurring in the high-pressure chamber can be reduced or damped at least in the direction of the connecting channel become. A simple way to do this is to make the mouth funnel-shaped. This ensures that impact on the mouth impacting pressure waves "dead run".

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Nachfolgend wird ein besonders bevorzugtes Ausführungsbeispiel der vorliegenden Erfindung unter Bezugnahme auf die beiliegende Zeichnung näher erläutert. In der Zeichnung zeigen:

Figur 1
eine schematische Darstellung einer Brennkraftmaschine mit einer Kraftstoff- Einspritzvorrichtung;
Figur 2
eine schematisierte und teilweise geschnittene Darstellung der Kraftstoff- Einspritzvorrichtung von Figur 1; und
Figur 3
eine detailliertere Darstellung eines Bereichs der Kraftstoff-Einspritzvorrichtung von Figur 1.
Hereinafter, a particularly preferred embodiment of the present invention will be explained in more detail with reference to the accompanying drawings. In the drawing show:
FIG. 1
a schematic representation of an internal combustion engine with a fuel injection device;
FIG. 2
a schematic and partially sectioned representation of the fuel injection device of FIG. 1 ; and
FIG. 3
a more detailed representation of a portion of the fuel injection device of FIG. 1 ,

Ausführungsformen der ErfindungEmbodiments of the invention

In Figur 1 trägt eine Brennkraftmaschine insgesamt das Bezugszeichen 10. Sie dient vorliegend zum Antrieb eines nicht gezeigten Kraftfahrzeugs. Eine Hochdruckfördereinrichtung 12 fördert Kraftstoff aus einem Kraftstoff-Vorratsbehälter 14 in einen Kraftstoff-Druckspeicher 16 ("Rail"). In diesem ist der Kraftstoff, beispielsweise Diesel oder Benzin, unter sehr hohem Druck gespeichert. An das Rail 16 sind mittels eines Hochdruckanschlusses 18 mehrere Kraftstoff-Einspritzvorrichtungen 20 angeschlossen, die den Kraftstoff direkt in ihnen zugeordnete Brennräume 22 einspritzen. Die Kraftstoff-Einspritzvorrichtungen 20 weisen jeweils auch einen Niederdruckanschluss 24 auf, über den sie mit einem Niederdruckbereich, vorliegend mit dem Kraftstoff-Vorratsbehälter 14 verbunden sind.In FIG. 1 an internal combustion engine carries the reference numeral 10. Overall, it serves to drive a motor vehicle, not shown. A high-pressure conveyor 12 conveys fuel from a fuel reservoir 14 into a fuel pressure accumulator 16 ("rail"). In this, the fuel, such as diesel or gasoline, stored under very high pressure. To the rail 16 a plurality of fuel injection devices 20 are connected by means of a high pressure port 18, which inject the fuel directly into them associated combustion chambers 22. The fuel injection devices 20 also each have a low-pressure connection 24, via which they are connected to a low-pressure region, in the present case to the fuel reservoir 14.

Wie aus Figur 2 ersichtlich ist, umfasst die Kraftstoff-Einspritzvorrichtung 20 ein Gehäuse 26 mit einem Düsenkörper 28, einem Hauptkörper 30 und einem Endkörper 32. Im Gehäuse 26 ist in dessen Längsrichtung eine stufenförmige Ausnehmung 34 vorhanden, in der ein nadelartiges Ventilelement 36 aufgenommen ist. Dieses ist zweiteilig: Es besteht aus einem Steuerkolben 38 und einer Düsennadel 40.How out FIG. 2 As can be seen, the fuel injection device 20 comprises a housing 26 having a nozzle body 28, a main body 30 and an end body 32. In the housing 26 is provided in the longitudinal direction thereof a stepped recess 34 in which a needle-like valve element 36 is received. This is in two parts: It consists of a control piston 38 and a nozzle needle 40th

Die Düsennadel 40 weist Druckflächen 42 auf, die einen Druckraum 44 begrenzen und deren hydraulische Kraftresultierende in Öffnungsrichtung der Düsennadel 40 zeigt. An ihrem in Figur 2 unteren Ende arbeitet die Düsennadel 40 auf in Figur 2 nicht näher dargestellte Art und Weise mit einem gehäuseseitigen Ventilsitz (ohne Bezugszeichen) zusammen. Auf diese Weise können Kraftstoff Austrittsöffnungen 46 vom Druckraum 44 getrennt oder mit diesem verbunden werden. Die Düsennadel 40 weist einen Abschnitt 48 mit kleinerem und einen Abschnitt 50 mit größerem Durchmesser auf. Mit dem Abschnitt 50 ist die Düsennadel 40 im Düsenkörper 28 längsverschieblich geführt.The nozzle needle 40 has pressure surfaces 42, which delimit a pressure chamber 44 and their hydraulic force resulting in the opening direction of the nozzle needle 40 shows. At her in FIG. 2 lower end, the nozzle needle 40 works in FIG. 2 not shown manner with a housing-side valve seat (without reference numerals) together. In this way, fuel outlet openings 46 can be separated from the pressure chamber 44 or connected thereto. The nozzle needle 40 has a portion 48 with a smaller and a portion 50 with larger Diameter up. With the section 50, the nozzle needle 40 is guided longitudinally displaceable in the nozzle body 28.

Der Steuerkolben 38 ist im Hauptkörper 30 aufgenommen. Ein in Figur 2 oberer Endbereich des Steuerkolbens 38 ist als Führung ausgearbeitet, der im Endkörper 32 aufgenommen und geführt ist. Eine Feder 52 stützt sich an einer durch einen Ringbund (ohne Bezugszeichen) gebildeten Schulter am Steuerkolben 38 ab und beaufschlagt diesen in Schließrichtung. Die in Figur 2 obere axiale Endfläche des Steuerkolbens 38 bildet eine in Schließrichtung des Ventilelements 36 wirkende hydraulische Steuerfläche 54. Sie begrenzt zusammen mit dem Endkörper 32 einen hydraulischen Steuerraum 56.The control piston 38 is received in the main body 30. An in FIG. 2 Upper end portion of the control piston 38 is worked out as a guide, which is received and guided in the end body 32. A spring 52 is supported on a shoulder formed by an annular collar (without reference numeral) on the control piston 38 and acted upon in the closing direction. In the FIG. 2 upper axial end surface of the control piston 38 forms a hydraulic control surface 54 acting in the closing direction of the valve element 36. It defines, together with the end body 32, a hydraulic control chamber 56.

Der Steuerraum 56 ist über eine Zulaufdrossel 58 im Endkörper 32 mit einem Hochdruckraum 60 verbunden, der aufgrund seines großen Volumens auch als Speicherraum bezeichnet werden kann und der mit dem Hochdruckanschluss 18 verbunden ist. Der Steuerraum 56 ist darüber hinaus durch eine Ablaufdrossel 62, die in den Endkörper 32 eingearbeitet ist, mit einem elektromagnetisch betätigten 2/2-Wege-Schaltventil 64 verbunden. Je nach Schaltstellung verbindet oder sperrt dieses die Ablaufdrossel 62 zu dem Niederdruckanschluss 24 hin. Der Hochdruckraum 60 ist ferner, in noch darzustellender Art und Weise, über einen Verbindungskanal 66 mit dem Druckraum 44 verbunden.The control chamber 56 is connected via an inlet throttle 58 in the end body 32 with a high pressure chamber 60, which can be referred to as a storage space due to its large volume and which is connected to the high pressure port 18. The control chamber 56 is further connected to an electromagnetically actuated 2/2-way switching valve 64 through an outlet throttle 62, which is incorporated in the end body 32. Depending on the switching position, this connects or blocks the outlet throttle 62 to the low pressure port 24. The high pressure chamber 60 is further, in yet to be shown manner, connected via a connecting channel 66 to the pressure chamber 44.

Zwischen dem Düsenkörper 28 und dem Hauptkörper 30 ist ein scheibenförmiges Führungselement 68 verklemmt. Dessen genauer Aufbau geht aus Figur 3 hervor: Danach umfasst das Führungselement 68 eine stufenförmige Durchgangsbohrung (ohne Bezugszeichen), deren in Figur 3 oberer Bereich einen Führungsabschnitt 70 bildet. In diesem ist ein in den Figuren 2 und 3 unterer Endbereich 72 des Steuerkolbens 38 im Gleitsitz geführt. Der Durchmesser des Endbereichs 72 ist etwas größer als der Durchmesser des Abschnitts 50 der Düsennadel 40, jedoch kleiner als der Durchmesser des Steuerkolbens 38 in jenem Bereich, der im Endkörper 32 geführt ist. Diese Durchmesserverhältnisse sind für die Funktion der Kraftstoff-Einspritzvorrichtung 10 wichtig. Aus Figur 3 ist ersichtlich, dass der Steuerkolben 38 unterhalb vom Endbereich 72 noch einen Endzapfen 74 aufweist, dessen Durchmesser kleiner ist als jener des Endbereichs 72 und auch kleiner als der zum Steuerkolben 38 benachbarte Bereich der Düsennadel 40. Etwa auf axialer Höhe dieses Endzapfens 74 erstreckt sich von der Durchgangsbohrung im Führungselement 68 nach radial einwärts ein umlaufender Ringbund 76, der einen Anschlag für die Düsennadel 40 bildet, da seine lichte Weite kleiner ist als der Außendurchmesser des zu ihm benachbarten Endbereichs der Düsennadel 40. Der Anschlag 76 ist jedoch nicht unbedingt erforderlich.Between the nozzle body 28 and the main body 30, a disc-shaped guide member 68 is clamped. Its exact structure goes out FIG. 3 The guide element 68 then has a step-shaped through-hole (without reference numeral), whose in FIG. 3 Upper portion forms a guide portion 70. In this one is in the Figures 2 and 3 lower end portion 72 of the control piston 38 guided in sliding fit. The diameter of the end portion 72 is slightly larger than the diameter of the portion 50 of the nozzle needle 40, but smaller than the diameter of the control piston 38 in the region which is guided in the end body 32. These diameter ratios are important to the function of the fuel injector 10. Out FIG. 3 It can be seen that the control piston 38 below the end portion 72 still has an end pin 74 whose diameter is smaller than that of the end portion 72 and also smaller than the control piston 38 adjacent portion of the nozzle needle 40. Approximately at the axial height of this end pin 74 extends from the through hole in the guide member 68 radially inwardly of a circumferential annular collar 76, which forms a stop for the nozzle needle 40, since its inside diameter is smaller than the outside diameter of the end region of the nozzle needle 40 adjacent to it. However, the stop 76 is not absolutely necessary.

Der zwischen dem Endzapfen 74, dem Endbereich 72, der Düsennadel 40 und dem Führungselement 68 gebildete Ringraum wird als Koppelraum 78 bezeichnet. Er ist, wie weiter unten noch näher erläutert werden wird, Teil eines hydraulischen Kopplers 80, durch den die Bewegungen des Steuerkolbens 38 und der Düsennadel 40 miteinander gekoppelt sind. Der hydraulische Koppler 80 umfasst auch ein Rückschlagventil 82 mit einem als Kugel ausgebildeten Ventilelement 84, welches von einer Ventilfeder 86 in eine Schließstellung beaufschlagt wird. In geöffnetem Zustand verbindet das Rückschlagventil 82 den hydraulischen Koppelraum 78 mit dem Hochdruckraum 60. Das Rückschlagventil 82 ist so ausgerichtet, dass es vom Koppelraum 78 weg zum Hochdruckraum 60 hin öffnet.The annular space formed between the end journal 74, the end region 72, the nozzle needle 40 and the guide element 68 is referred to as a coupling space 78. It is, as will be explained in more detail below, part of a hydraulic coupler 80, through which the movements of the control piston 38 and the nozzle needle 40 are coupled together. The hydraulic coupler 80 also includes a check valve 82 having a valve member 84 formed as a ball, which is acted upon by a valve spring 86 in a closed position. In the open state, the check valve 82 connects the hydraulic coupling chamber 78 with the high pressure chamber 60. The check valve 82 is aligned so that it opens away from the coupling chamber 78 to the high pressure chamber 60 out.

Ein im Führungselement 68 liegender Abschnitt des Verbindungskanals 66 umfasst eine Strömungsdrossel 88. Ein Mündungsbereich 90 des Verbindungskanals 66 zum Hochdruckraum 60 hin ist trichterförmig ausgebildet.A lying in the guide member 68 portion of the connecting channel 66 includes a flow restrictor 88. An opening portion 90 of the connecting channel 66 to the high-pressure chamber 60 toward is funnel-shaped.

Die Kraftstoff-Einspritzvorrichtung 20 funktioniert folgendermaßen: Im Ausgangszustand, bei stromlosem Schaltventil 64, ist der hydraulische Steuerraum 56 vom Niederdruckanschluss 24 getrennt und über die Zulaufdrossel 58 mit dem Hochdruckanschluss 18 und somit mit dem Rail 16 verbunden. Im hydraulischen Steuerraum 56 liegt somit der gleiche Druck an wie im Hochdruckraum 60. Dieser herrscht im stationären Ausgangszustand über den Verbindungskanal 66 auch im Druckraum 44. Aufgrund einer gewissen Leckage zwischen dem Führungsabschnitt 70 des Führungselements 68 und dem Endbereich 72 des Steuerkolbens 38 sowie Leckage zwischen der Düsennadel 40 und dem Düsenkörper 28 im Abschnitt 50 liegt dieser Druck auch im Koppelraum 78 an. Insgesamt ergibt sich in dieser Konstellation eine in Schließrichtung des Ventilelements 36 wirkende Kraft, welche dieses gegen den Ventilsitz im Bereich der Kraftstoff-Austrittsöffnungen 46 drückt.The fuel injection device 20 operates as follows: In the initial state, with de-energized switching valve 64, the hydraulic control chamber 56 is separated from the low pressure port 24 and connected via the inlet throttle 58 to the high pressure port 18 and thus to the rail 16. Due to a certain leakage between the guide portion 70 of the guide member 68 and the end portion 72 of the control piston 38 as well as leakage between the nozzle needle 40 and the nozzle body 28 in section 50, this pressure is also in the coupling chamber 78 at. Overall, in this constellation results in a force acting in the closing direction of the valve member 36, which presses this against the valve seat in the region of the fuel outlet openings 46.

Wird nun das Schaltventil 64 bestromt, wird die Ablaufdrossel 62 mit dem Niederdruckanschluss 24 verbunden. Hierdurch sinkt der Druck im hydraulischen Steuerraum 56 ab. Im Koppelraum 78 herrscht dagegen zunächst noch der hohe Ausgangsdruck. Daher ergibt sich in der Summe nun eine in Öffnungsrichtung auf den Steuerkolben 38 einwirkende Kraft. Dieser beginnt somit, sich entgegen der Kraft der Feder 52 in den Figuren 2 und 3 nach oben zu bewegen. Damit sinkt durch die Volumenvergrößerung der Druck im Koppelraum 78, wohingegen im Druckraum 44 immer noch der hohe Ausgangsdruck herrscht. In der Summe wirkt daher nun auch auf die Düsennadel 40 eine in Öffnungsrichtung wirkende Kraft, aufgrund der sich die Düsennadel 40 in den Figuren 2 und 3 nach oben zu bewegen beginnt, sie hebt also von ihrem Ventilsitz im Bereich der Kraftstoff-Austrittsöffnungen 46 ab. Somit kann Kraftstoff vom Rail 16 über den Hochdruckanschluss 18, den Hochdruckraum 60, den Verbindungskanal 66, den Druckraum 44 und über die Kraftstoff-Austrittsöffnungen 46 in den Brennraum 22 eingespritzt werden. Aufgrund der Strömungsdrossel 88 im Verbindungskanal 76 ergibt sich dabei im Druckraum 44 ein geringerer Druck als im Hochdruckraum 60.If the switching valve 64 is energized, the outlet throttle 62 is connected to the low-pressure connection 24. As a result, the pressure in the hydraulic control chamber 56 decreases. In the coupling space 78, however, initially there is still the high outlet pressure. Therefore, in the sum now a force acting on the control piston 38 in the opening direction. This thus begins, against the force of the spring 52 in the Figures 2 and 3 to move upwards. Thus, due to the increase in volume, the pressure in the coupling chamber 78 drops, whereas in the pressure chamber 44, the high outlet pressure still prevails. In sum, therefore, now also acts on the nozzle needle 40 an acting in the opening direction force, due to which the nozzle needle 40 in the Figures 2 and 3 begins to move upward, so it rises from its valve seat in the region of the fuel outlet openings 46 from. Thus, fuel from the rail 16 via the high pressure port 18, the high pressure chamber 60, the connecting channel 66, the pressure chamber 44 and the fuel outlet openings 46 are injected into the combustion chamber 22. Due to the flow restrictor 88 in the connecting channel 76 results in the pressure chamber 44, a lower pressure than in the high-pressure chamber 60th

Da auch im Koppelraum 78 zumindest zeitweise ein geringerer Druck herrscht als im Hochdruckraum 60, gelangt eine gewisse Kraftstoffmenge durch den Führungsspalt zwischen Führungsabschnitt 70 und Endbereich 72 vom Hochdruckraum 60 und zwischen Düsennadel 40 und Düsenkörper 28 im Abschnitt 50 vom Druckraum 44 in den Koppelraum 78. Durch eine bewusste Dimensionierung des besagten Führungsspaltes kann die vom Hochdruckraum 60 in den Koppelraum 78 überströmende Kraftstoffmenge eingestellt werden, was wiederum eine bewusste Einstellung des Öffnungsverhaltens des Ventilelements 36 ermöglicht. Je größer der Führungsspalt ist, desto "gedämpfter" sinkt der Druck im Koppelraum 78, und umso verzögerter reagiert die Düsennadel 40. Dies ist vor allem dann hilfreich, wenn von der Kraftstoff-Einspritzvorrichtung 20 gefordert wird, dass sie auch Kleinstmengen einzuspritzen in der Lage sein soll.Since in the coupling chamber 78, at least temporarily, a lower pressure prevails than in the high pressure chamber 60, passes a certain amount of fuel through the guide gap between the guide portion 70 and end 72 of the high pressure chamber 60 and between the nozzle needle 40 and nozzle body 28 in section 50 from the pressure chamber 44 in the coupling space 78th By a deliberate dimensioning of the said guide gap, the amount of fuel flowing over from the high-pressure chamber 60 into the coupling chamber 78 can be adjusted, which in turn allows a deliberate adjustment of the opening behavior of the valve element 36. The larger the guide gap, the more "muted" the pressure in the coupling chamber 78 decreases, and the delayed response of the nozzle needle 40. This is especially helpful when required by the fuel injector 20 that they can inject even very small quantities in the situation should be.

Zur Beendigung einer Einspritzung wird das Schaltventil 64 wieder in seine geschlossene Stellung gebracht, in welcher die Verbindung des hydraulischen Steuerraums 56 mit dem Niederdruckanschluss 24 gesperrt ist. Über die Zulaufdrossel 58 steigt der Druck im hydraulischen Steuerraum 56 an. Hierdurch wird der Steuerkolben 38 wieder in Schließrichtung bewegt, da der Druck im Koppelraum 78 zunächst noch geringer ist als im hydraulischen Steuerraum 56. In der Folge steigt der Druck im Koppelraum 78 wegen der Volumenverkleinerung wieder an, was letztlich zu einer insgesamt in Schließrichtung der Düsennadel 40 auf diese einwirkenden Kraft führt. Die Bewegung der Düsennadel 40 ist zu Ende, wenn diese mit ihrem in Figur 2 unteren Ende wieder am gehäuseseitigen Ventilsitz anliegt und somit kein Kraftstoff mehr durch die Kraftstoff-Austrittsöffnungen 46 austreten kann. Da, wie oben bereits erwähnt wurde, zwischenzeitlich Kraftstoff vom Hochdruckraum 60 und vom Druckraum 44 in den Koppelraum 78 gelangt ist, stößt der Steuerkolben 38 am Ende seiner Schließbewegung auf ein "Kraftstoffpolster", was zu einer dynamischen Druckerhöhung im Koppelraum 78 auf einen Druck führt, der größer ist als der Druck im Hochdruckraum 60. In der Folge öffnet das Rückschlagventil 82, so dass der in den Koppelraum 78 eingedrungene Kraftstoff in den Hochdruckraum 60 entweichen kann. Am Ende seiner Schließbewegung gelangt daher der Steuerkolben 38 wieder in Anlage an die Düsennadel 40.To end an injection, the switching valve 64 is returned to its closed position, in which the connection of the hydraulic control chamber 56 is locked to the low pressure port 24. Via the inlet throttle 58, the pressure in the hydraulic control chamber 56 increases. As a result, the control piston 38 is again moved in the closing direction, since the pressure in the coupling chamber 78 is initially lower than in the hydraulic control chamber 56. As a result, the pressure in the coupling chamber 78 increases due to the reduction in volume again, which ultimately leads to a total in the closing direction of the nozzle needle 40 leads to this acting force. The movement of the nozzle needle 40 is at an end when this with its in FIG. 2 bottom end rests again on the housing-side valve seat and thus no fuel can escape through the fuel outlet openings 46. Since, as already mentioned above, in the meantime fuel has passed from the high-pressure chamber 60 and the pressure chamber 44 into the coupling chamber 78, the control piston 38 encounters a "fuel cushion" at the end of its closing movement, which leads to a dynamic pressure increase in the coupling chamber 78 to a pressure , which is greater than the pressure in the high-pressure chamber 60. As a result, the check valve 82 opens, so that the fuel which has penetrated into the coupling chamber 78 can escape into the high-pressure chamber 60. At the end of its closing movement, therefore, the control piston 38 again comes into abutment against the nozzle needle 40.

Soll von der Kraftstoff-Einspritzvorrichtung 20 Kraftstoff durch mehrere kurz hintereinander liegende Einspritzungen eingespritzt werden, muss das Ventilelement 36 wieder öffnen können, unmittelbar nachdem es in seiner Schließstellung angelangt war. Voraussetzung hierfür ist, dass der Koppelraum 78, nachdem im Koppelraum 78 vorhandener "überschüssiger" Kraftstoff über das Rückschlagventil 82 in den Hochdruckraum 60 abgeführt wurde, möglichst schnell wieder ein abgeschlossenes Volumen bildet, welches die Düsennadel 40 an die Öffnungsbewegung des Steuerkolbens 38 koppelt. Dies wird erreicht, indem der Hub des Ventilelements 84 des Rückschlagventils 82 auf einen sehr geringen maximalen Hub begrenzt wird. Fällt der Druck im Koppelraum 78 also aufgrund einer Öffnungsbewegung des Steuerkolbens 38 wieder ab, muss das Ventilelement 84 nur einen geringen Hub zurücklegen, bis es wieder in seiner geschlossen Stellung ist und somit der Koppelraum 78 ein abgeschlossenes Volumen bilden kann.If fuel is to be injected by the fuel injection device 20 through a plurality of injections arranged in quick succession, the valve element 36 must be able to open again immediately after it has reached its closed position. The prerequisite for this is that the coupling space 78, after the "excess" fuel present in the coupling space 78 has been removed via the check valve 82 into the high-pressure chamber 60, again forms a closed volume as quickly as possible, which couples the nozzle needle 40 to the opening movement of the control piston 38. This is achieved by limiting the stroke of the valve member 84 of the check valve 82 to a very small maximum lift. If the pressure in the coupling chamber 78 thus drops again due to an opening movement of the control piston 38, the valve element 84 has to travel only a small stroke until it is in its closed position again and thus the coupling space 78 can form a closed volume.

Die Ausgestaltung des Mündungsbereichs 90 des Verbindungskanals 66 in Form eines sich zum Hochdruckraum 60 hin erweiternden Trichters hat folgende Wirkung: Aufgrund des Öffnens und Schließens des Ventilelements 36 kommt es im Hochdruckraum 60 zu Druckschwingungen, welche jedoch aufgrund der Größe des Hochdruckraums 60 dort kaum spürbar sind. Der Verbindungskanal 66 und der Druckraum 44 haben jedoch ein deutlich kleineres Volumen als der Hochdruckraum 60, so dass sich Druckschwankungen dort verstärkt auswirken und somit die Einspritzgenauigkeit reduzieren würden. Hier greift der trichterförmig ausgestaltete Mündungsbereich 90 an: Durch diesen werden auf den Mündungsbereich 90 auftreffende Druckwellen "zerstreut" beziehungsweise reduziert, so dass die Druckschwankungen nur vermindert in den Verbindungskanal 66 hinein übertragen werden. Daher kann der Kraftstoff mit der hier vorgestellten Kraftstoff-Einspritzvorrichtung 20 mit besonders hoher Genauigkeit zugemessen werden.The configuration of the mouth region 90 of the connecting channel 66 in the form of a funnel which widens towards the high-pressure chamber 60 has the following effect: Due to the opening and closing of the valve element 36, pressure oscillations occur in the high-pressure chamber 60, which, however, are hardly noticeable there due to the size of the high-pressure chamber 60 , However, the connecting channel 66 and the pressure chamber 44 have a significantly smaller volume than the high-pressure chamber 60, so that pressure fluctuations would have an increased effect there and thus would reduce the injection accuracy. Here, the funnel-shaped configured mouth region 90 attacks: Through this impact waves striking the mouth region 90 are "dispersed" or reduced, so that the pressure fluctuations are transmitted only reduced in the connecting channel 66 into it. Therefore, the fuel can be metered with the fuel injection device 20 presented here with particularly high accuracy.

Claims (6)

  1. Fuel injection device (20) for an internal combustion engine (10), having a housing (26) and having a valve element (36) which is arranged in the housing (26) and which interacts with a valve seat situated in the region of at least one fuel outlet opening (46), wherein at least one control piston (38) and a nozzle needle (40) of the valve element (36) are coupled to one another by means of a hydraulic coupler (80), wherein an annular chamber is formed between an end peg (74) and an end region (72) of the control piston (38), the nozzle needle (40) and a guide element (68), which annular chamber forms a coupler chamber (78) of the hydraulic coupler (80), wherein the control piston (38) has a hydraulic control surface (54) which acts in the closing direction of the valve element (36) and which, together with an end body (32) of the housing (26), delimits a hydraulic control chamber (56), wherein the control chamber (56) is connected via an inflow throttle (58) in the end body (32) to a high-pressure chamber (60) which is connected to a high-pressure port (18), and said control chamber is connected by means of an outflow throttle (62) in the end body (32) to a solenoid-actuated 2/2 directional control switching valve (64) which, depending on the switching position, connects the outflow throttle (62) to or blocks the outflow throttle (62) in the direction of a low-pressure port (24), and wherein a connecting duct (66) is provided which leads from the high-pressure chamber (60) to the valve seat situated in the region of the fuel outlet opening (42), wherein the coupler chamber (78) comprises a check valve (82) which is connected thereto and which, in the open state, connects the coupler chamber (78) to the high-pressure chamber (60) in that the check valve (82) opens away from the coupler chamber (78) in the direction of the high-pressure chamber (60).
  2. Fuel injection device according to Claim 1, characterized in that a valve element (84) of the check valve (82) is loaded into its closed position by a spring (86).
  3. Fuel injection device according to Claim 2, characterized in that the valve element (84) of the check valve (82) has a maximum stroke which is such that a predefined time interval between a closing and a subsequent opening of the valve element (36) of the fuel injection device (20) can be maintained.
  4. Fuel injection device according to one of the preceding claims, characterized in that a gap (70) between the control piston (38) and a housing portion (70) which delimits the coupler chamber (78) with respect to a high-pressure chamber (60) is designed such that an opening of the nozzle needle (40) takes place in a delayed fashion.
  5. Fuel injection device according to Claim 1, characterized in that an opening-out region (90) of the connecting duct (66) into the high-pressure chamber (60) is designed such that pressure waves are reduced.
  6. Fuel injection device according to Claim 5, characterized in that the opening-out region (90) is funnel-shaped.
EP07728518A 2006-06-09 2007-04-25 Fuel injection device for an internal combustion engine Not-in-force EP2032834B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006026877A DE102006026877A1 (en) 2006-06-09 2006-06-09 Fuel injection device for an internal combustion engine
PCT/EP2007/054063 WO2007141094A1 (en) 2006-06-09 2007-04-25 Fuel injection device for an internal combustion engine

Publications (2)

Publication Number Publication Date
EP2032834A1 EP2032834A1 (en) 2009-03-11
EP2032834B1 true EP2032834B1 (en) 2011-09-21

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Application Number Title Priority Date Filing Date
EP07728518A Not-in-force EP2032834B1 (en) 2006-06-09 2007-04-25 Fuel injection device for an internal combustion engine

Country Status (7)

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US (1) US20090184183A1 (en)
EP (1) EP2032834B1 (en)
CN (1) CN101466944B (en)
AT (1) ATE525565T1 (en)
DE (1) DE102006026877A1 (en)
ES (1) ES2370855T3 (en)
WO (1) WO2007141094A1 (en)

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Also Published As

Publication number Publication date
US20090184183A1 (en) 2009-07-23
EP2032834A1 (en) 2009-03-11
CN101466944A (en) 2009-06-24
CN101466944B (en) 2012-07-04
ES2370855T3 (en) 2011-12-23
WO2007141094A1 (en) 2007-12-13
ATE525565T1 (en) 2011-10-15
DE102006026877A1 (en) 2007-12-13

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