WO2001014717A1 - Fuel injection device for internal combustion engines - Google Patents

Fuel injection device for internal combustion engines Download PDF

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Publication number
WO2001014717A1
WO2001014717A1 PCT/DE2000/002678 DE0002678W WO0114717A1 WO 2001014717 A1 WO2001014717 A1 WO 2001014717A1 DE 0002678 W DE0002678 W DE 0002678W WO 0114717 A1 WO0114717 A1 WO 0114717A1
Authority
WO
WIPO (PCT)
Prior art keywords
fuel injection
injection device
valve member
fuel
piezo
Prior art date
Application number
PCT/DE2000/002678
Other languages
German (de)
French (fr)
Inventor
Patrick Mattes
Original Assignee
Robert Bosch Gmbh
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Priority to EP00956130A priority Critical patent/EP1210511A1/en
Priority to JP2001518566A priority patent/JP2003507642A/en
Publication of WO2001014717A1 publication Critical patent/WO2001014717A1/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
    • 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
    • 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
    • F02M63/0059—Arrangements of valve actuators
    • F02M63/0063—Two or more actuators acting on a single valve body
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • 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

Definitions

  • the invention relates to a fuel injection device for internal combustion engines according to the preamble of claim 1, as is known from DE 196 24 001 AI.
  • the opening stroke required to open the valve member that relieves a control chamber is generated by means of a piezo actuator. So that the useful stroke of the valve member is constant at all temperatures, one is required
  • Valve member is arranged.
  • the hydraulic coupler has the additional advantage of translating a piezo actuator into a stroke, which leads to a significant increase in the valve speed.
  • the amount of fuel can be controlled very precisely and the stroke-to-stroke scatter of a fuel injector decreases.
  • the problem with the use of a hydraulic coupler is that, due to the system, in the hydraulic coupler very high pressures must be generated so that the valve member lifts off its valve seat and opens. It is therefore necessary, on the one hand, to design the piston gap dimensions to be very small in order to limit the leakage from the hydraulic coupler, and on the other hand the piezo actuator must be significantly oversized in order to compensate for the stroke losses due to the leakage.
  • the fuel injection device for internal combustion engines according to the invention with the characterizing features of claim 1 has the advantage that the piezo device requires a reduced volume overall. This can be explained by the fact that, due to the lower pressure required in the hydraulic coupler, this has less leakage and thus less stroke losses. This in turn results in a correspondingly smaller-sized piezo actuator that interacts with the hydraulic coupler.
  • the smaller-sized piezo actuator also requires lower currents to control the piezo actuator and a smaller and simpler control device for the piezo actuator.
  • the reduced pressure prevailing in the hydraulic coupler it is possible to provide for an increase in the tolerance of the piston gap dimensions, so that production is simplified.
  • FIG. 1 shows a schematic illustration of a fuel injection device and FIG. 2 shows part of a fuel injection valve together
  • FIG. 1 shows a fuel injection valve 10 m in a simplified representation, which has an injection valve housing 12 with a stepped bore 13, in which a valve needle is guided as an injection valve member 15. This has at one end a conical sealing surface 16 which cooperates with a conical valve seat 17 at the end of the stepped bore 13. Fuel injection openings 18 are arranged downstream of the valve seat 17 and are separated from a pressure chamber 19 when the sealing surface 16 is placed on the valve seat 17. The pressure chamber 19 extends over an annular space 22 which is formed around the part 21 of the injection valve member 15 which adjoins the sealing surface 16 upstream and has a smaller diameter as far as the valve seat 17.
  • the pressure chamber 19 is connected via a pressure line 23 to a high-pressure fuel source in the form of a high-pressure fuel reservoir 24, which is supplied, for example, by a high-pressure pump 25, which delivers a variable delivery rate, from a reservoir 27 with fuel which is brought to the injection pressure.
  • the high-pressure fuel accumulator 24 supplies several of the fuel injection valves 10 shown Fuel injection system is referred to as a “common rail system”.
  • the part 21 of the injection valve member 15 with a smaller diameter goes with a pressure shoulder 28 m pointing towards the valve seat 17 and a part 29 of the larger diameter
  • Injector valve member 15 over. This is tightly guided in the stepped bore 13 and continues on the side facing away from the pressure shoulder 28 in an intermediate part 30 to hm to a piston-shaped end 31 of the injection valve member 15. In the area of the intermediate part 30, the latter has a spring plate 32, between which and the injection valve housing 12 a compression spring 33 is clamped, which acts on the injection valve member 15 in the closed position.
  • the piston-shaped end 31 of the injection valve member 15 delimits an end face 34, the area of which is larger than that of the pressure shoulder 28 in the injection valve housing 12, a control chamber 35.
  • the control chamber 35 is connected via a supply throttle 36 m to the
  • control chamber 35 is connected to a relief chamber 39, which can also be the reservoir 27, for example, via an outlet channel 38 and an outlet throttle 37.
  • the passage of the drain channel 38 is controlled by a control valve 40, which is designed as a 2/2 way valve.
  • control valve 40 The structure of the control valve 40 is shown in more detail in FIG.
  • the cylindrical control valve 40 is connected to the
  • the control valve 40 has an essentially sleeve-shaped outer housing 42, the end 43 facing away from the injection valve housing 12 is closed by a flanging process or the like.
  • Inside the outer case 42 is on the Injection valve housing 12 facing away from a first, simplified piezo actuator 45 integrated, which is axially delimited by two fixed bearing plates 46, 47.
  • the lower fixed bearing plate 47 is coupled to a first plunger 48, which is sealed on its circumference by means of a sealing element 49 to the outer housing 42.
  • a section 51, enlarged in diameter, of the first plunger 48 projects into a first bore 52 of a hydraulic translator 55 or hydraulic coupler having a cylindrical housing 53.
  • a second bore 56 of smaller diameter is formed in the housing 53, in which a second plunger 57 is immersed from the side facing the injection valve housing 12.
  • the underside 58 of the housing 53 facing the injection valve housing 12 lies flat on the upper end face 59 of the injection valve housing 12.
  • the injection valve housing 12 has a threefold stepped through hole 61 opening into the control chamber 35.
  • the section 62 of the through hole 61 facing the housing 53 has the largest diameter, the section 63 opening into the control chamber 35 has the smallest diameter.
  • the drain channel 38 also branches off from the section 63 to the relief chamber 39.
  • a second piezo actuator 65 likewise shown in simplified form, is arranged in section 62.
  • the second piezo actuator 65 which is significantly smaller than the first piezo actuator 45, has a centrally arranged through hole 66 which is penetrated by the second plunger 57 with radial play. With regard to its axial movement path, the second piezo actuator 65 is arranged in a form-fitting manner between the underside 58 of the housing 53 and a collar 67 of the second plunger 57 which is enlarged in diameter. The collar 67 is slidably guided in the central section 64 of the through hole 61. The reason 68 of the middle section 64 serves as an axial stroke limiter for the second plunger 57.
  • a plunger section 69 adjoins the collar 67, which is guided in section 63 with radial play and which interacts with a valve member 70 designed as a ball.
  • a seat edge 72 is formed which, together with the valve member 70, forms a sealing seat, so that no fuel can flow out of the control chamber 35 via the section 63 and the drain channel 38 to the relief chamber 39.
  • the control of the fuel injection valve 10 takes place via the control valve 40 or the two piezo actuators 45, 65 via a control device 73, which controls the control valves 40 of the individual fuel injection valves 10 as a function of operating parameters, and the pressure in the high-pressure fuel accumulator with a pressure sensor 74 24 detects and controls the variable delivery high pressure pump 25 in accordance with the deviation from a desired setpoint.
  • a pressure limiting valve 75 can be provided, which can also be controlled as a pressure control valve depending on operating parameters, depending on the design of the high-pressure fuel supply.
  • the high-pressure pump 25 can also continuously deliver in the same quantity and the pressure in the high-pressure fuel accumulator 24 can be regulated via the pressure limiting valve 75, which is to be regarded here explicitly as a pressure control valve.
  • the fuel injection device described above which is in particular a component of a diesel internal combustion engine, works as follows: When the control valve 40 is closed, ie the piezoactuators 45, 65 are not actuated, the valve member 70 bears against the seat edge 72 and seals the control chamber 35 to the relief chamber 39.
  • the sealing seat is due to the constant connection of the control room 35 with the
  • High-pressure fuel accumulator 24 is formed because the pressure prevailing in the control chamber 35 is at a high level. Because the area of the end face 34 is larger than the area of the pressure shoulder 28 and the pressure acting on both areas is the same at the moment, a resultant force results which holds the injection valve member 15 in the closed position with respect to the injection openings 18.
  • first only the second piezo actuator 65 is controlled by the control unit 73. The second piezo actuator 65 is therefore only for lifting the
  • Valve member 70 responsible from the seat edge 72 i.e. that it has a relatively small stroke.
  • the relatively small stroke of the second piezo actuator 65 is sufficient to overcome an increase in the opening force of the valve member 70 due to the seat angle difference.
  • the second piezo actuator 65 expands, it is supported against the underside 58 of the housing 53 and presses it via the collar 67 of the second plunger 57 in the direction of the relief chamber 35
  • Actual opening of the valve member 70 by means of the first piezo actuator 45 which has a greater stroke than the second piezo actuator 65.
  • a relatively low lifting force of the first piezo actuator 45 is sufficient to move the second plunger 57 further.
  • the stroke of the first piezo actuator 45 is increased by the hydraulic translator 55.
  • the maximum stroke of the second plunger 57 is determined by the bottom 68 of the through bore 61 acting as a stroke stop is limited.
  • the lifting of the valve member 70 or the opening stroke by the first piezo actuator 45 causes fuel to flow out of the control chamber 35 to the relief chamber 39, so that, decoupled from

Abstract

The invention relates to a fuel injection device for internal combustion engines. Said fuel injection device comprises a plurality of fuel injection valves (10) that are supplied with fuel by a high-pressure fuel accumulator (24). Every fuel injection valve (10) has a needle-shaped injection valve member (15) whose movement is controlled via the fuel pressure that prevails in a control chamber (35). According to the invention, the movement of the valve member (70) that relieves the control chamber (35) to a relief chamber (39) and that is coupled to a tappet (57) is controlled by means of two piezo actuators (45, 65). The piezo actuators (45, 65) are mounted in series so that their travel has the same effective direction.

Description

Kraftstoffeinspritzvorrichtung für BrennkraftmaschinenFuel injection device for internal combustion engines
Stand der TechnikState of the art
Die Erfindung betrifft eine Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen nach dem Oberbegriff des Anspruchs 1, wie sie aus der DE 196 24 001 AI bekannt ist. Bei der bekannten Kraftstoffeinspritzvorrichtung wird der zum Öffnen des einen Steuerraum entlastenden Ventilgliedes erforderliche Öffnungshub mittels eines Piezoaktors erzeugt. Damit der Nutzhub des Ventilgliedes bei allen Temperaturen konstant ist, ist es erforderlich, eineThe invention relates to a fuel injection device for internal combustion engines according to the preamble of claim 1, as is known from DE 196 24 001 AI. In the known fuel injection device, the opening stroke required to open the valve member that relieves a control chamber is generated by means of a piezo actuator. So that the useful stroke of the valve member is constant at all temperatures, one is required
Temperaturkompensation vorzusehen. Dies erfolgt bei der bekannten Kraftstoffeinspritzvorrichtung mittels eines hydraulischen Kopplers, der zwischen dem Piezoaktor und demTo provide temperature compensation. In the known fuel injection device, this is done by means of a hydraulic coupler, which is located between the piezo actuator and the
Ventilglied angeordnet ist. Der hydraulische Koppler hat im Gegensatz zu der ebenfalls im Stand der Technik bekannten Temperaturkompensation mittels speziellen Materialpaarungen den zusätzlichen Vorteil einer Wegübersetzung von Piezoaktor- in Weghub, der zu einer deutlichen Steigerung der Ventilgeschwindigkeit führt . Dadurch kann sehr präzise die Kraftstoffmenge gesteuert werden und die Hub-zu-Hub- Streuungen eines Kraftstoffeinspritzventiles nehmen ab. Problematisch bei der Verwendung eines hydraulischen Kopplers ist, daß systembedingt im hydraulischen Koppler sehr hohe Drücke erzeugt werden müssen, damit das Ventilglied von seinem Ventilsitz abhebt und öffnet. Daher ist es zum einen erforderlich, zur Begrenzung der Leckage aus dem hydraulischen Koppler die Kolbenspaltmaße sehr gering auszubilden, andererseits muß der Piezoaktor deutlich überdimensioniert werden, um die Hubverluste aufgrund der Leckage zu kompensieren.Valve member is arranged. In contrast to the temperature compensation by means of special material pairings, which is also known in the prior art, the hydraulic coupler has the additional advantage of translating a piezo actuator into a stroke, which leads to a significant increase in the valve speed. As a result, the amount of fuel can be controlled very precisely and the stroke-to-stroke scatter of a fuel injector decreases. The problem with the use of a hydraulic coupler is that, due to the system, in the hydraulic coupler very high pressures must be generated so that the valve member lifts off its valve seat and opens. It is therefore necessary, on the one hand, to design the piston gap dimensions to be very small in order to limit the leakage from the hydraulic coupler, and on the other hand the piezo actuator must be significantly oversized in order to compensate for the stroke losses due to the leakage.
Vorteile der ErfindungAdvantages of the invention
Die erfindungsgemäße Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen mit den kennzeichnenden Merkmalen des Anspruchs 1 hat demgegenüber den Vorteil, daß die Piezoemrichtung insgesamt ein verringertes Volumen beansprucht. Dies erklärt sich daraus, daß aufgrund des geringeren erforderlichen Drucks im hydraulischen Koppler dieser eine geringere Leckage und somit geringere Hubverluste aufweist. Dies wiederum hat einen entsprechend kleiner bauenden, mit dem hydraulischen Koppler zusammenwirkenden Piezoaktor zur Folge. Durch den kleiner bauenden Piezoaktor sind auch geringere Strome zur Ansteuerung des Piezoaktors sowie ein kleiner und einfacher bauendes Steuergerat für den Piezoaktor erforderlich. Weiterhin ist es aufgrund des im hydraulischen Koppler herrschenden reduzierten Drucks möglich, eine Toleranzaufweitung der Kolbenspaltmaße vorzusehen, so daß die Fertigung vereinfacht wird.The fuel injection device for internal combustion engines according to the invention with the characterizing features of claim 1 has the advantage that the piezo device requires a reduced volume overall. This can be explained by the fact that, due to the lower pressure required in the hydraulic coupler, this has less leakage and thus less stroke losses. This in turn results in a correspondingly smaller-sized piezo actuator that interacts with the hydraulic coupler. The smaller-sized piezo actuator also requires lower currents to control the piezo actuator and a smaller and simpler control device for the piezo actuator. Furthermore, because of the reduced pressure prevailing in the hydraulic coupler, it is possible to provide for an increase in the tolerance of the piston gap dimensions, so that production is simplified.
Weitere vorteilhafte Weiterbildungen der erfindungsgemäßenFurther advantageous developments of the invention
Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen sind m den Unteransprüchen angegeben. ZeichnungFuel injection device for internal combustion engines are specified in the subclaims. drawing
Ein Ausführungsbeispiel der Erfindung ist m der Zeichnung dargestellt und wird nachfolgend näher erläutert. Es zeigen:An embodiment of the invention is shown in the drawing and is explained in more detail below. Show it:
Figur 1 e ne schematische Darstellung einer Kraftstoff- einspritzvorrichtung und Figur 2 einen Teil eines Kraftstoffemspritzventils samt1 shows a schematic illustration of a fuel injection device and FIG. 2 shows part of a fuel injection valve together
Steuerventil nach Figur 1 im Längsschnitt.Control valve according to Figure 1 in longitudinal section.
Beschreibung des Ausführungsbeisp elsDescription of the execution example
Figur 1 zeigt ein Kraftstoffemspritzventil 10 m vereinfachter Darstellung, das ein Emspritzventilgehause 12 mit einer gestuften Bohrung 13 aufweist, in der eine Ventilnadel als Emspritzventilglied 15 geführt ist. Dieses weist an seinem einen Ende eine kegelförmige Dichtfläche 16 auf, die mit einem kegelförmigen Ventilsitz 17 am Ende der gestuften Bohrung 13 zusammenwirkt. Stromabwärts des Ventilsitzes 17 sind Kraftstoffemspritzöffnungen 18 angeordnet, die beim Aufsetzen der Dichtfläche 16 auf dem Ventilsitz 17 von einem Druckraum 19 getrennt werden. Der Druckraum 19 erstreckt sich über einen um den sich an die Dichtfläche 16 stromaufwärts anschließenden, mit kleinerem Durchmesser versehenen Teil 21 des Emspritzventilglieds 15 herum gebildeten Ringraum 22 bis zum Ventilsitz 17 hin. Der Druckraum 19 ist über eine Druckleitung 23 mit einer Kraftstoffhochdruckquelle m Form eines Kraftstoffhochdruckspeichers 24 verbunden, der zum Beispiel von einer mit variabler Förderrate fördernden Hochdruckpumpe 25 aus einem Vorratsbehälter 27 mit Kraftstoff, der auf Einspritzdruck gebracht ist, versorgt wird. Der Kraftstoffhochdruckspeicher 24 versorgt dabei mehrere der gezeigten Kraftstoffemspritzventile 10. Es derartiges Kraftstoffemspritzsystem wird als „Common-Rail-System" bezeichnet. Im Bereich des Druckraums 19 geht der im Durchmesser kleinere Teil 21 des E spritzventilglieds 15 mit einer zum Ventilsitz 17 weisenden Druckschulter 28 m einen im Durchmesser größeren Teil 29 desFIG. 1 shows a fuel injection valve 10 m in a simplified representation, which has an injection valve housing 12 with a stepped bore 13, in which a valve needle is guided as an injection valve member 15. This has at one end a conical sealing surface 16 which cooperates with a conical valve seat 17 at the end of the stepped bore 13. Fuel injection openings 18 are arranged downstream of the valve seat 17 and are separated from a pressure chamber 19 when the sealing surface 16 is placed on the valve seat 17. The pressure chamber 19 extends over an annular space 22 which is formed around the part 21 of the injection valve member 15 which adjoins the sealing surface 16 upstream and has a smaller diameter as far as the valve seat 17. The pressure chamber 19 is connected via a pressure line 23 to a high-pressure fuel source in the form of a high-pressure fuel reservoir 24, which is supplied, for example, by a high-pressure pump 25, which delivers a variable delivery rate, from a reservoir 27 with fuel which is brought to the injection pressure. The high-pressure fuel accumulator 24 supplies several of the fuel injection valves 10 shown Fuel injection system is referred to as a “common rail system”. In the area of the pressure chamber 19, the part 21 of the injection valve member 15 with a smaller diameter goes with a pressure shoulder 28 m pointing towards the valve seat 17 and a part 29 of the larger diameter
Emspritzventilglieds 15 über. Dieser ist m der gestuften Bohrung 13 dicht gefuhrt und setzt sich auf der der Druckschulter 28 abgewandten Seite m einem Zwischenteil 30 bis hm zu einem kolbenförmigen Ende 31 des Emspritzventilglieds 15 fort. Im Bereich des Zwischenteils 30 hat dieses einen Federteller 32, zwischen dem und dem Emspritzventilgehause 12 eine Druckfeder 33 eingespannt ist, die das Emspπtzventilglied 15 m Schließstellung beaufschlagt .Injector valve member 15 over. This is tightly guided in the stepped bore 13 and continues on the side facing away from the pressure shoulder 28 in an intermediate part 30 to hm to a piston-shaped end 31 of the injection valve member 15. In the area of the intermediate part 30, the latter has a spring plate 32, between which and the injection valve housing 12 a compression spring 33 is clamped, which acts on the injection valve member 15 in the closed position.
Das kolbenförmige Ende 31 des Emspritzventilglieds 15 begrenzt mit einer Stirnseite 34, deren Fläche großer ist als die der Druckschulter 28 im Emspritzventilgehause 12 einen Steuerraum 35. Der Steuerraum 35 ist über eine Zulaufdrossel 36 m standiger Verbindung mit demThe piston-shaped end 31 of the injection valve member 15 delimits an end face 34, the area of which is larger than that of the pressure shoulder 28 in the injection valve housing 12, a control chamber 35. The control chamber 35 is connected via a supply throttle 36 m to the
Kraftstoffhochdruckspeicher 24. Gleichzeitig ist der Steuerraum 35 über einen Abflußkanal 38 und eine Ablaufdrossel 37 mit einem Entlastungsraum 39 verbunden, der zum Beispiel auch der Vorratsbehälter 27 sein kann. Der Durchgang des Abflußkanals 38 wird durch ein Steuerventil 40, das als 2/2 -Wegeventil ausgebildet ist, gesteuert.High-pressure fuel reservoir 24. At the same time, the control chamber 35 is connected to a relief chamber 39, which can also be the reservoir 27, for example, via an outlet channel 38 and an outlet throttle 37. The passage of the drain channel 38 is controlled by a control valve 40, which is designed as a 2/2 way valve.
In der Figur 2 ist der Aufbau des Steuerventils 40 genauer dargestellt. Das zylindrisch ausgebildete Steuerventil 40 ist mittels einer Überwurfmutter 41 mit demThe structure of the control valve 40 is shown in more detail in FIG. The cylindrical control valve 40 is connected to the
Emspritzventilgehause 12 lösbar verbunden. Das Steuerventil 40 weist ein im wesentlichen hulsenformiges Außengehause 42 auf, dessen dem Emspritzventilgehause 12 abgewandtes Ende 43 durch einen Bordelvorgang oder ähnliches verschlossen ist. Im Inneren des Außengehäuses 42 ist auf der dem Einspritzventilgehäuse 12 abgewandten Seite ein erster, vereinfacht dargestellter Piezoaktor 45 integriert, welcher axial von zwei Festlagerplatten 46, 47 begrenzt ist. Die untere Festlagerplatte 47 ist mit einem ersten Stößel 48 gekoppelt, der an seinem Umfang mittels eines Dichtelements 49 zum Außengehäuse 42 hin abgedichtet ist. Ein im Durchmesser vergrößerter Abschnitt 51 des ersten Stößels 48 ragt in eine erste Bohrung 52 eines ein zylindrisches Gehäuse 53 aufweisenden hydraulischen Übersetzers 55 bzw. hydraulischen Kopplers ein. Koaxial zur ersten Bohrung 52 ist eine zweite Bohrung 56 geringeren Durchmessers im Gehäuse 53 ausgebildet, in der ein zweiter Stößel 57 von der dem Einspritzventilgehäuse 12 zugewandten Seite eintaucht. Die dem Einspritzventilgehäuse 12 zugewandte Unterseite 58 des Gehäuses 53 liegt plan auf der oberen Stirnfläche 59 des Einspritzventilgehäuses 12 auf.Injector valve housing 12 releasably connected. The control valve 40 has an essentially sleeve-shaped outer housing 42, the end 43 facing away from the injection valve housing 12 is closed by a flanging process or the like. Inside the outer case 42 is on the Injection valve housing 12 facing away from a first, simplified piezo actuator 45 integrated, which is axially delimited by two fixed bearing plates 46, 47. The lower fixed bearing plate 47 is coupled to a first plunger 48, which is sealed on its circumference by means of a sealing element 49 to the outer housing 42. A section 51, enlarged in diameter, of the first plunger 48 projects into a first bore 52 of a hydraulic translator 55 or hydraulic coupler having a cylindrical housing 53. Coaxial to the first bore 52, a second bore 56 of smaller diameter is formed in the housing 53, in which a second plunger 57 is immersed from the side facing the injection valve housing 12. The underside 58 of the housing 53 facing the injection valve housing 12 lies flat on the upper end face 59 of the injection valve housing 12.
Das Einspritzventilgehäuse 12 hat eine dreifach abgestufte, in den Steuerraum 35 mündende Durchgangsbohrung 61. Der dem Gehäuse 53 zugewandte Abschnitt 62 der Durchgangsbohrung 61 hat dabei den größten, der in den Steuerraum 35 mündende Abschnitt 63 den geringsten Durchmesser. Vom Abschnitt 63 zweigt auch der Abflußkanal 38 zum Entlastungsraum 39 ab. Im Abschnitt 62 ist ein zweiter, ebenfalls vereinfacht dargestellter Piezoaktor 65 angeordnet.The injection valve housing 12 has a threefold stepped through hole 61 opening into the control chamber 35. The section 62 of the through hole 61 facing the housing 53 has the largest diameter, the section 63 opening into the control chamber 35 has the smallest diameter. The drain channel 38 also branches off from the section 63 to the relief chamber 39. A second piezo actuator 65, likewise shown in simplified form, is arranged in section 62.
Der bedeutend kleiner als der erste Piezoaktor 45 bauende zweite Piezoaktor 65 weist ein mittig angeordnetes Durchgangsloch 66 auf, das vom zweiten Stößel 57 mit radialem Spiel durchdrungen ist. Der zweite Piezoaktor 65 ist in Bezug auf seinen axialen Bewegungsweg formschlüssig zwischen der Unterseite 58 des Gehäuses 53 und einem im Durchmesser vergrößerten Bund 67 des zweiten Stößels 57 angeordnet. Der Bund 67 ist im mittleren Abschnitt 64 der Durchgangsbohrung 61 gleitend geführt. Der Grund 68 des mittleren Abschnitts 64 dient dabei als axiale Hubbegrenzung für den zweiten Stößel 57. An den Bund 67 schließt sich ein Stößelabschnitt 69 an, der mit radialem Spiel im Abschnitt 63 geführt ist, und der mit einem als Kugel ausgebildeten Ventilglied 70 zusammenwirkt. Im Übergangsbereich zwischen dem Steuerraum 35 zum Abschnitt 63 der Durchgangsbohrung 61 ist eine Sitzkante 72 ausgebildet, die zusammen mit dem Ventilglied 70 einen Dichtsitz ausbildet, so daß kein Kraftstoff vom Steuerraum 35 über den Abschnitt 63 und den Abflußkanal 38 zum Entlastungsraum 39 hin abströmen kann.The second piezo actuator 65, which is significantly smaller than the first piezo actuator 45, has a centrally arranged through hole 66 which is penetrated by the second plunger 57 with radial play. With regard to its axial movement path, the second piezo actuator 65 is arranged in a form-fitting manner between the underside 58 of the housing 53 and a collar 67 of the second plunger 57 which is enlarged in diameter. The collar 67 is slidably guided in the central section 64 of the through hole 61. The reason 68 of the middle section 64 serves as an axial stroke limiter for the second plunger 57. A plunger section 69 adjoins the collar 67, which is guided in section 63 with radial play and which interacts with a valve member 70 designed as a ball. In the transition region between the control chamber 35 and the section 63 of the through-bore 61, a seat edge 72 is formed which, together with the valve member 70, forms a sealing seat, so that no fuel can flow out of the control chamber 35 via the section 63 and the drain channel 38 to the relief chamber 39.
Entsprechend der Figur 1 erfolgt die Ansteuerung des Kraftstoffeinspritzventils 10 über das Steuerventil 40 bzw. die beiden Piezoaktoren 45, 65 über ein Steuergerät 73, das in Abhängigkeit von Betriebsparametern die Steuerventile 40 der einzelnen Kraftstoffeinspritzventile 10 ansteuert, ferner mit einem Drucksensor 74 den Druck im Kraftstoffhochdruckspeicher 24 erfaßt und entsprechend der Abweichung von einem gewünschten Sollwert die variabel fördernde Hochdruckpumpe 25 steuert. Parallel zu dieser kann ein Druckbegrenzungsventil 75 vorgesehen sein, das auch als Drucksteuerventil in Abhängigkeit von Betriebsparametern steuerbar ist, je nach Konzeption der Krafstoffhochdruckmengenversorgung .According to FIG. 1, the control of the fuel injection valve 10 takes place via the control valve 40 or the two piezo actuators 45, 65 via a control device 73, which controls the control valves 40 of the individual fuel injection valves 10 as a function of operating parameters, and the pressure in the high-pressure fuel accumulator with a pressure sensor 74 24 detects and controls the variable delivery high pressure pump 25 in accordance with the deviation from a desired setpoint. In parallel with this, a pressure limiting valve 75 can be provided, which can also be controlled as a pressure control valve depending on operating parameters, depending on the design of the high-pressure fuel supply.
Auch kann die Hochdruckpumpe 25 ständig in gleicher Menge fördern und über das Druckbegrenzungsventil 75, das hier explizit als Drucksteuerventil anzusehen ist, der Druck im Krafstoffhochdruckspeicher 24 eingeregelt werden.The high-pressure pump 25 can also continuously deliver in the same quantity and the pressure in the high-pressure fuel accumulator 24 can be regulated via the pressure limiting valve 75, which is to be regarded here explicitly as a pressure control valve.
Die oben beschriebene Krafstoffeinspritzvorrichtung, die insbesondere Bestandteil einer Dieselbrennkraftmaschine ist, arbeitet wie folgt: Bei geschlossenem Steuerventil 40, d.h. nicht betätigten Piezoaktoren 45, 65, liegt das Ventilglied 70 gegen die Sitzkante 72 an und dichtet den Steuerraum 35 zum Entlastungsraum 39 hin ab. Der Dichtsitz wird aufgrund der ständigen Verbindung des Steuerraums 35 mit demThe fuel injection device described above, which is in particular a component of a diesel internal combustion engine, works as follows: When the control valve 40 is closed, ie the piezoactuators 45, 65 are not actuated, the valve member 70 bears against the seat edge 72 and seals the control chamber 35 to the relief chamber 39. The sealing seat is due to the constant connection of the control room 35 with the
Kraftstoffhochdruckspeicher 24 gebildet, da der im Steuerraum 35 herrschende Druck auf hohem Niveau ist. Weil die Fläche der Stirnseite 34 größer ist als die Fläche der Druckschulter 28 und der auf beide Flächen wirkende Druck in dem Moment gleich groß ist, ergibt sich eine resultierende Kraft, die das Einspritzventilglied 15 in geschlossener Stellung in Bezug auf die Einspritzöffnungen 18 hält. Zur Auslösung einer Einspritzung wird zuerst nur der zweite Piezoaktor 65 vom Steuergerät 73 angesteuert. Der zweite Piezoaktor 65 ist somit allein für das Abheben desHigh-pressure fuel accumulator 24 is formed because the pressure prevailing in the control chamber 35 is at a high level. Because the area of the end face 34 is larger than the area of the pressure shoulder 28 and the pressure acting on both areas is the same at the moment, a resultant force results which holds the injection valve member 15 in the closed position with respect to the injection openings 18. To trigger an injection, first only the second piezo actuator 65 is controlled by the control unit 73. The second piezo actuator 65 is therefore only for lifting the
Ventilgliedes 70 von der Sitzkante 72 verantwortlich, d.h., daß dieser einen relativ geringen Hub aufweist. Dabei genügt der relativ geringe Hub des zweiten Piezoaktors 65, um einen Öffnungskraftanstieg des Ventilgliedes 70 aufgrund der Sitzwinkeldifferenz zu überwinden. Bei der Ausdehnung des zweiten Piezoaktors 65 stützt sich dieser dabei gegen die Unterseite 58 des Gehäuses 53 ab und drückt über den Bund 67 des zweiten Stößels 57 diesen in Richtung des Entlastungsraums 35. Sobald das Ventilglied 70 von der Sitzkante 72 etwas abgehoben ist, erfolgt das eigentliche Öffnen des Ventilgliedes 70 mittels des ersten Piezoaktors 45, der einen größeren Hub aufweist als der zweite Piezoaktor 65. Dabei genügt, nachdem die Sitzkräfte überwunden sind, eine relativ geringe Hubkraft des ersten Piezoaktors 45, um den zweiten Stößel 57 weiterzubewegen.Valve member 70 responsible from the seat edge 72, i.e. that it has a relatively small stroke. The relatively small stroke of the second piezo actuator 65 is sufficient to overcome an increase in the opening force of the valve member 70 due to the seat angle difference. When the second piezo actuator 65 expands, it is supported against the underside 58 of the housing 53 and presses it via the collar 67 of the second plunger 57 in the direction of the relief chamber 35 Actual opening of the valve member 70 by means of the first piezo actuator 45, which has a greater stroke than the second piezo actuator 65. After the seat forces have been overcome, a relatively low lifting force of the first piezo actuator 45 is sufficient to move the second plunger 57 further.
Aufgrund des hydraulischen Übersetzers 55 und der gewählten Durchmesserverhältnisse der Stößel 48 und 57 bzw. der Bohrungen 52 und 56 im Gehäuse 53 wird dabei der Hub des ersten Piezoaktors 45 durch den hydraulischen Übersetzer 55 vergrößert. Der Maximalhub des zweiten Stößels 57 wird durch den als Hubanschlag wirkenden Grund 68 der Durchgangsbohrung 61 begrenzt. Das Abheben des Ventilgliedes 70 bzw. der Öffnungshub durch den ersten Piezoaktor 45 bewirkt, daß Kraftstoff vom Steuerraum 35 zum Entlastungsraum 39 hin abströmen kann, so daß, abgekoppelt vomBecause of the hydraulic translator 55 and the selected diameter ratios of the plungers 48 and 57 or the bores 52 and 56 in the housing 53, the stroke of the first piezo actuator 45 is increased by the hydraulic translator 55. The maximum stroke of the second plunger 57 is determined by the bottom 68 of the through bore 61 acting as a stroke stop is limited. The lifting of the valve member 70 or the opening stroke by the first piezo actuator 45 causes fuel to flow out of the control chamber 35 to the relief chamber 39, so that, decoupled from
Kraftstoffhochdruckspeicher 24 durch die Zulaufdrossel 36, sich im Steuerraum 35 ein Druck niedrigeren Niveaus einstellt. In diesem Fall überwiegen die auf die Druckschulter 28 in Öffnungsrichtung wirkenden Druckkräfte und das Kraftstoffeinspritzventil 10 wird zur Einspritzung geöffnet .High-pressure fuel reservoir 24 through the inlet throttle 36, a pressure of lower levels is established in the control chamber 35. In this case, the pressure forces acting on the pressure shoulder 28 in the opening direction predominate and the fuel injection valve 10 is opened for injection.
Durch Wiederschließen des Steuerventils 40 bzw. Nichtbestromen der Piezoaktoren 45, 65 stellt sich, nachdem das Ventilglied 70 wieder in Wirkverbindung mit der Sitzkante 72 ist, im Steuerraum 35 sehr schnell der ursprüngliche hohe Kraftstoffdruck wieder ein, da der Kraftstoff über die Zulaufdrossel 36 weiterhin zufließen kann. Dadurch gelangt das Einspritzventilglied 15 wieder in seine Ausgangsstellung bzw. Schließstellung zur Beendigung der Hochdruckeinspritzung zurück. By reclosing the control valve 40 or not energizing the piezo actuators 45, 65, after the valve member 70 is again in operative connection with the seat edge 72, the original high fuel pressure in the control chamber 35 is very quickly restored, since the fuel continues to flow via the inlet throttle 36 can. As a result, the injection valve member 15 returns to its initial position or closed position to end the high-pressure injection.

Claims

Ansprüche Expectations
1. Kraf stoffeinspritzvorrichtung für Brennkraftmaschinen mit einer Kraftstoffhochdruckquelle (24), aus der ein1. Kraf fuel injection device for internal combustion engines with a high-pressure fuel source (24), from the one
Kraftstoffeinspritzventil (10) mit Kraftstoff versorgt wird, das ein Einspritzventilglied (15) zur Steuerung von wenigstens einer Einspritzöffnung (18) und einen Steuerraum (35) aufweist, der von einer beweglichen Wand (34), die mit dem Einspritzventilglied (15) wenigstens mittelbar verbunden ist, begrenzt wird, und der einen mittels einer Zulaufdrossel (36) dimensionerten, von einer Hochdruckquelle (25) , vorzugsweise von der Kraftstoffhochdruckquelle kommenden Zuflußkanal (23) aufweist, wobei der Steuerraum (35) mittels eines eine Piezoeinrichtung und einem damit zumindest mittelbar verbundenen Ventilglied (70) aufweisenden Steuerventils (40) entlastbar ist, dadurch gekennzeichnet, daß die Piezoeinrichtung wenigstens zwei, in gleicher Richtung wirkende, hintereinandergeschaltete Piezoaktoren (45, 65) aufweist.Fuel injection valve (10) is supplied with fuel, which has an injection valve member (15) for controlling at least one injection opening (18) and a control chamber (35) which is at least indirectly connected to a movable wall (34) which is connected to the injection valve member (15) is connected, is limited, and has an inflow channel (23), which is dimensioned by means of an inlet throttle (36) and comes from a high-pressure source (25), preferably from the high-pressure fuel source, the control chamber (35) using a piezo device and thus at least indirectly connected valve member (70) having control valve (40) can be relieved, characterized in that the piezo device has at least two piezo actuators (45, 65) connected in series in the same direction.
2. Kraftstoffeinspritzvorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß die Piezoaktoren (45, 65) unterschiedlich große Hubewege aufweisen.2. Fuel injection device according to claim 1, characterized in that the piezo actuators (45, 65) have differently large lifting paths.
3. Kraftstoffeinspritzvorrichtung nach Anspruch 2, dadurch gekennzeichnet, daß der einen kleineren Hub aufweisende eine Piezoaktor (65) zwischen dem Ventilglied (70) und dem einen größeren Hub aufweisenden anderen Piezoaktor (45) angeordnet ist .3. Fuel injection device according to claim 2, characterized in that the having a smaller stroke a piezo actuator (65) between the valve member (70) and the one larger stroke having another piezo actuator (45) is arranged.
4. Kraftstoffeinspritzvorrichtung nach Anspruch 3, dadurch gekennzeichnet, daß der andere Piezoaktor (65) ein4. Fuel injection device according to claim 3, characterized in that the other piezo actuator (65)
Durchgangsloch (66) für einen mit dem Ventilglied (70) zusammenwirkenden Stößel (57) aufweist und daß der Stößel (57) eine Stützfläche (67) für den anderen Piezoaktor (65) aufweist, zwischen der und einem ortsfesten ersten Anschlag (58) der andere Piezoaktor (65) angeordnet ist.Through hole (66) for a with the valve member (70) cooperating plunger (57) and that the plunger (57) has a support surface (67) for the other piezo actuator (65), between the and a stationary first stop (58) another piezo actuator (65) is arranged.
5. Kraftstoffeinspritzvorrichtung nach Anspruch 4, dadurch gekennzeichnet, daß auf der dem ersten Anschlag (58) gegenüberliegenden Seite des ersten Anschlags (58) ein als Hubbegrenzung für den Stößel (57) und das Ventilglied (70) wirkender zweiter Anschlag (68) angeordnet ist.5. Fuel injection device according to claim 4, characterized in that on the first stop (58) opposite side of the first stop (58) as a stroke limitation for the plunger (57) and the valve member (70) acting second stop (68) is arranged ,
6. Kraftstoffeinspritzvorrichtung nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß zwischen den beiden Piezoaktoren (45, 65) ein hydraulischer Übersetzer (55) angeordnet ist.6. Fuel injection device according to one of claims 1 to 5, characterized in that a hydraulic translator (55) is arranged between the two piezo actuators (45, 65).
7. Kraftstoffeinspritzvorrichtung nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, daß die beiden Piezoaktoren (45, 65) innerhalb eines gemeinsamen Gehäuses (42) angeordnet sind.7. Fuel injection device according to one of claims 1 to 6, characterized in that the two piezo actuators (45, 65) are arranged within a common housing (42).
8. Kraftstoffeinspritzvorrichtung nach Anspruch 7, dadurch gekennzeichnet, daß das Gehäuse (42) zumindest in dem Bereich der beiden Piezoaktoren (45, 65) hülsenförmig ausgebildet ist. 8. Fuel injection device according to claim 7, characterized in that the housing (42) is sleeve-shaped at least in the region of the two piezo actuators (45, 65).
PCT/DE2000/002678 1999-08-20 2000-08-10 Fuel injection device for internal combustion engines WO2001014717A1 (en)

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JP2001518566A JP2003507642A (en) 1999-08-20 2000-08-10 Fuel injection device for internal combustion engines

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DE19939446.6 1999-08-20

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DE10129375B4 (en) * 2001-06-20 2005-10-06 Mtu Friedrichshafen Gmbh Injector with piezo actuator
JP4167230B2 (en) 2004-01-13 2008-10-15 デルファイ・テクノロジーズ・インコーポレイテッド Fuel injection device
DE102009026554A1 (en) * 2009-05-28 2010-12-02 Robert Bosch Gmbh Throttling valve for liquid and / or gaseous substances
DE102011103262A1 (en) 2011-06-01 2012-12-06 Golle Motor Gmbh Injector for diesel and gasoline direct injection systems of combustion engines, comprises control piston, which is directly connected with nozzle needle, where nozzle needle is arranged in control sleeve in longitudinally movable manner

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JPH01147143A (en) * 1987-12-01 1989-06-08 Toyota Motor Corp Fuel injection system for internal combustion engine
EP0789142A1 (en) * 1995-08-29 1997-08-13 Isuzu Motors Limited Storage type fuel injection device
DE19624001A1 (en) 1996-06-15 1997-12-18 Bosch Gmbh Robert Fuel injection device for internal combustion engines
DE19654782C1 (en) * 1996-12-31 1998-05-20 Dualon International S A Injector for diesel engine
DE19732802A1 (en) * 1997-07-30 1999-02-04 Bosch Gmbh Robert Fuel injection device for internal combustion engines

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Publication number Priority date Publication date Assignee Title
JPH01147143A (en) * 1987-12-01 1989-06-08 Toyota Motor Corp Fuel injection system for internal combustion engine
EP0789142A1 (en) * 1995-08-29 1997-08-13 Isuzu Motors Limited Storage type fuel injection device
DE19624001A1 (en) 1996-06-15 1997-12-18 Bosch Gmbh Robert Fuel injection device for internal combustion engines
DE19654782C1 (en) * 1996-12-31 1998-05-20 Dualon International S A Injector for diesel engine
DE19732802A1 (en) * 1997-07-30 1999-02-04 Bosch Gmbh Robert Fuel injection device for internal combustion engines

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PATENT ABSTRACTS OF JAPAN vol. 013, no. 405 (M - 868) 7 September 1989 (1989-09-07) *

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JP2003507642A (en) 2003-02-25

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