EP1373717A1 - Fuel injection device for internal combustion engines - Google Patents

Fuel injection device for internal combustion engines

Info

Publication number
EP1373717A1
EP1373717A1 EP02732356A EP02732356A EP1373717A1 EP 1373717 A1 EP1373717 A1 EP 1373717A1 EP 02732356 A EP02732356 A EP 02732356A EP 02732356 A EP02732356 A EP 02732356A EP 1373717 A1 EP1373717 A1 EP 1373717A1
Authority
EP
European Patent Office
Prior art keywords
valve
control
injection device
pressure
fuel injection
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.)
Withdrawn
Application number
EP02732356A
Other languages
German (de)
French (fr)
Inventor
Achim Brenk
Wolfgang Klenk
Roland Bleher
Uwe Gordon
Manfred Mack
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
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
Publication of EP1373717A1 publication Critical patent/EP1373717A1/en
Withdrawn legal-status Critical Current

Links

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
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/08—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series the valves opening in direction of fuel flow
    • 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
    • F02M63/0003—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure
    • F02M63/0007—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure using electrically actuated valves

Definitions

  • the invention is based on a fuel injection device according to the preamble of claim 1.
  • the injection valve has a two-stage hydraulic stroke stop which limits the opening stroke of the valve member and is designed as a hydraulic damping space with controllable relief.
  • the fuel in the damping chamber is pressed into a low-pressure chamber by two cuts on the valve member and via relief lines assigned to the cuts.
  • the sealing edge of the first bevel is formed closer to the combustion chamber than that of the second bevel, so that the sealing edge of the first bevel plunges into the bore as soon as a row of injection openings has emerged from the bore of the valve member.
  • the fuel in the damping chamber is routed exclusively via the second bevel and its relief line.
  • a hydraulically controlled relief valve is arranged in the relief line of the second bevel, which only opens when the pressure prevailing in the damping chamber exceeds the closing force of the closing spring acting on the valve member of the relief valve.
  • the closing spring is supported on one end face of an axially displaceable piston, the other end of which faces away from a hydraulic working space.
  • the piston and thus the closing force of the closing spring can be adjusted as a function of the operating characteristics of the internal combustion engine.
  • the Control pressure can thus be used to control how far the valve member emerges from the bore during the opening stroke movement and whether only one or both rows of injection openings are released.
  • the fuel injection device for internal combustion engines according to the invention with the characterizing features of claim 1 has the advantage that the hydraulic actuation of the Hubêtv ⁇ ntile takes place with low pressure and with the help of a single further control valve which can be switched via an actuator and can influence the pressure in the control line to the stroke control valve ,
  • the use of low pressure as a control variable has great advantages and reduces the control losses of the overall system or leads to an improvement in system efficiency. If the low pressure is taken from the discharge / quantity of the metering valves controlling the fuel metering of the injection valves, there is a further improvement in the overall efficiency.
  • control (pressure relief) of the injection valves The entire control quantity requirement can be covered by the control (pressure relief) of the injection valves.
  • FIG. 1 shows a first exemplary embodiment of a fuel injection device in a schematic overall illustration
  • FIG. 2 shows a second exemplary embodiment of a fuel injection device analogous to the representation in FIG. 1.
  • the first exemplary embodiment of a fuel injection device for internal combustion engines has a high-pressure fuel pump 2, which is connected on the suction side to a fuel tank 3 and on the pressure side to a high-pressure accumulator (common mail) 4. From this high-pressure accumulator 4, the high-pressure fuel is supplied via feed lines 5 to the individual pressure-controlled injection valves projecting into the combustion chamber of the internal combustion engine to be supplied
  • injectors 6 discharged, of which only one is shown in Fig. 1.
  • the injector 6 each have an electrically actuated metering valve 7 in the form of, for example, a 3/2-way valve.
  • the pressure in the high-pressure accumulator 4 is controlled by means of a 2/2-way solenoid valve 8, via which the high-pressure accumulator 4 is connected to the fuel 3, that is to say can be connected to the leak oil side.
  • the injection valve 6, which is designed as an A nozzle, comprises a piston-shaped valve member 11, which protrudes outward from the guide bore 10 of the valve housing against the action of a closing spring 9.
  • Two axially superimposed rows of spray holes 12, 13 are provided on the valve member 11 externally directed opening stroke of the valve member 11 can be opened in succession.
  • the spray holes 12, 13 are connected via longitudinal channels 14 in the valve member 11 to an annular pressure chamber 15, into which the supply line 5 opens into the injection valve 6.
  • the valve member 11 has a pressure shoulder 16, on which the fuel supplied via the supply line 5 in the opening direction (i.e. to the outside) on
  • Valve member 11 attacks.
  • the valve member 11 is provided at one end of a shaft 17, which at its other end carries a spring plate 18, on which the closing spring 9, which is supported at the other end on the valve housing, engages.
  • the stroke performed by the valve member 11 when opening is controlled by a hydraulic stroke stop 19.
  • the piston 20 provided for this purpose on the shaft 17 delimits with its one end a damping space 21 with two axially offset relief channels 22, 23, which are closed in succession during the opening stroke of the valve member 11.
  • the damping chamber 21 with the fuel tank 3, ie with the leakage, is connected via the first relief channel 22.
  • a hydraulically controllable, spring-loaded stroke control valve 24 (3/2-way valve) which, depending on the pressure prevailing in its control line 25, connects the damping chamber 21 with the fuel tank 3, ie with the Leakage oil side, or connects to a pressure accumulator 26.
  • the control lines 25 of the stroke control valves 24 are connected via a 3/2-way control valve 27 either to the pressure accumulator 26 or to the fuel tank 3, that is to say to the leakage oil side.
  • the control valve 27 can be actuated by an actuator in order to switch over the stroke control valves 24 of all the injection valves 6 at the same time.
  • the pressure accumulator 26 Via the metering valve 7 and a spring-loaded constant pressure or pressure regulating valve 28 provided therebetween (for example set to 60 bar), the pressure accumulator 26 can also be used
  • the fuel injection ie the opening stroke of the valve member 11, is initiated by energizing the metering valve 7.
  • the control pressure of the pressure accumulator 26 prevails in the control line 25, so that the stroke control valve 24 is switched against the spring force with the aid of this control pressure and, as shown in FIG. 1, the damping chamber 21 with the fuel tank 3 connects.
  • the valve member 11 opens, the fuel displaced by the piston 20 from the damping chamber 21 flows out via the second relief channel 23, so that a stroke limitation does not take place.
  • the 3/2-way control valve 27 when the 3/2-way control valve 27 is open, ie energized, the control line 25 is connected to the fuel tank 3 and is thus relieved, so that the stroke control valve 24 now connects the damping chamber 21 to the pressure accumulator 26.
  • the pressure accumulator 26 has a very small volume to ensure a precise stroke stop, but is so large that the valve member 11 does not vibrate. If, when the valve member 11 opens, the piston 20 closes the first relief channel 22 with its control edge 30, the fuel located in the damping chamber 21 is compressed by the piston 20. As a result, the opening stroke of the valve member 11 is hydraulically limited to a partial stroke of, for example, 50%, in which only the lower spray holes 12 are released for injection. In the fuel injection device shown in Fig. 2
  • control line 25 of the stroke control valves 24 can be connected to the fuel ank 3 via a 2/2-way control valve 32 and is connected to the pressure accumulator 26 via a throttle 33.

Abstract

The invention relates to a fuel injection device (1) for internal combustion engines, comprising an injection valve (6), for each cylinder of the internal combustion engine, provided in a fuel supply line (5) and a hydraulic stroke stop (9), limiting the opening stroke of the valve member (11) of the injection valve (6), embodied as a hydraulic damping chamber (21). Said device further comprises a hydraulically operated stroke control valve (24), which closes the connection of the damping chamber (21) to the oil drain side (3), depending upon the pressure in the control line (25) thereof, whereby the control lines (25) of the individual stroke control valves (24) may be connected either to a low pressure reservoir (26) or an oil drain side (3), by means of a control valve unit.

Description

Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen Fuel injection device for internal combustion engines
Beschreibungdescription
Stand der TechnikState of the art
Die Erfindung geht von einer Kraftstoffeinspritzvorr:ich- tung nach der Gattung des Patentanspruchs 1 aus. Eine solche aus der DE 197 39 905 AI bekannte Kraftstoffeinspritzvorrichtung umfaßt ein Einspritzventil mit einem nach au- ßen aus einer Bohrung des Ventilkörpers austauchenden Ventilglied. An dem Ventilglied sind zwei axial übereinander liegende Reihen von Spritzlöchern vorgesehen, die beim nach außen gerichteten Öffnungshub des Ventilglieds nach- einander aufsteuerbar sind. Das Einspritzventil weist einen den Öffnungshub des Ventilglieds begrenzenden zweistufigen hydraulischen Hubanschlag auf, der als hydraulischer Dämpfungsraum mit zusteuerbarer Entlastung ausgebildet ist. Bei der Öffnungshubbewegung wird der Kraftstoff im Dämpfungsraum durch zwei Anschliffe am Ventilglied und über' jeweils den Anschliffen zugeordnete Entlastungslei- tungen in einen Niederdruckraum gepreßt. Die Dichtkante des ersten Anschliffs ist dabei brennraumnäher als die des zweiten Anschliffs ausgebildet, so daß die Dichtkante des ersten Anschliffs in die Bohrung eintaucht, sobald eine Einspritzöffnungsreihe aus der Bohrung des Ventilglieds ausgetaucht ist. In der weiteren Huböffnungsphase wird der Kraftstoff im Dämpfungsraum ausschließlich über den zweiten Anschliff und dessen Entlastungsleitung geleitet. In der Entlastungsleitung des zweiten Anschliffs ist ein hydraulisch gesteuertes Entlastungsventil angeordnet, das erst dann öffnet, wenn der im Dämpfungsraum herrschende Druck die Schließkraft der auf das Ventilglied des Entlastungsventils wirkenden Schließfeder überschreitet. Die Schließfeder ist an der einen Stirnfläche eines axial verschiebbaren Kolbens abgestützt, dessen andere abgewandte Stirnseite einen hydraulischen Arbeitsraum begrenzt . Indem der Arbeitsraum über eine Steuerleitung mit einer unter Druck stehenden Hydraulikflüssigkeit aus einem Hydraulik- system beaufschlagt wird, läßt sich der Kolben und damit die Schließkraft der Schließfeder in Abhängigkeit vom Betriebskennfeld der Brennkraftmaschine verstellen. Über den Steuerdruck läßt sich somit steuern, wie weit das Ventil - glied bei der Öffnungshubbewegung aus der Bohrung aus- taucht und ob nur eine oder beide Einspritzöffnungsreihen freigegeben werden.The invention is based on a fuel injection device according to the preamble of claim 1. Such a fuel injection device known from DE 197 39 905 AI comprises an injection valve with a ß from a bore of the valve body emerging valve member. Provided on the valve member are two rows of spray holes lying axially one above the other, which can be opened in succession during the outward opening stroke of the valve member. The injection valve has a two-stage hydraulic stroke stop which limits the opening stroke of the valve member and is designed as a hydraulic damping space with controllable relief. During the opening stroke movement, the fuel in the damping chamber is pressed into a low-pressure chamber by two cuts on the valve member and via relief lines assigned to the cuts. The sealing edge of the first bevel is formed closer to the combustion chamber than that of the second bevel, so that the sealing edge of the first bevel plunges into the bore as soon as a row of injection openings has emerged from the bore of the valve member. In the further stroke opening phase, the fuel in the damping chamber is routed exclusively via the second bevel and its relief line. A hydraulically controlled relief valve is arranged in the relief line of the second bevel, which only opens when the pressure prevailing in the damping chamber exceeds the closing force of the closing spring acting on the valve member of the relief valve. The closing spring is supported on one end face of an axially displaceable piston, the other end of which faces away from a hydraulic working space. By applying a pressurized hydraulic fluid from a hydraulic system to the working area via a control line, the piston and thus the closing force of the closing spring can be adjusted as a function of the operating characteristics of the internal combustion engine. On the Control pressure can thus be used to control how far the valve member emerges from the bore during the opening stroke movement and whether only one or both rows of injection openings are released.
Vorteile der ErfindungAdvantages of the invention
Die erfindungsgemäße Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen mit den kennzeichnenden Merkmalen des Patentanspruchs 1 hat demgegenüber den Vorteil, daß die hydraulische Betätigung der Hubsteuervεntile mit Niederdruck und mit Hilfe eines einzigen weiteren Steuerventils erfolgt, das über einen Aktor schaltbar ist und den Druck in der Steuerleitung zum Hubsteuerventil beeinflussen kann. Die Verwendung von Niederdruck als Steuergröße hat große Vorteile und reduziert die Absteuerverluste des Gesamtsystems bzw. führt zu einer Verbesserung des Systemwirkungsgrads. Wird der Niederdruck aus der Absteuer/menge der die Kraftstoffzumessung der Einspritzventile steuernden Zumeßventile entnommen, so ergibt sich eine weitere Verbesserung des Gesamtwirkungsgrads.The fuel injection device for internal combustion engines according to the invention with the characterizing features of claim 1 has the advantage that the hydraulic actuation of the Hubsteuervεntile takes place with low pressure and with the help of a single further control valve which can be switched via an actuator and can influence the pressure in the control line to the stroke control valve , The use of low pressure as a control variable has great advantages and reduces the control losses of the overall system or leads to an improvement in system efficiency. If the low pressure is taken from the discharge / quantity of the metering valves controlling the fuel metering of the injection valves, there is a further improvement in the overall efficiency.
Der gesamte Steuermengenbedarf kann aus der Absteueirung (Druckentlastung) der Einspritzventile gedeckt werden.The entire control quantity requirement can be covered by the control (pressure relief) of the injection valves.
Dies ist aus energetischer Sicht wesentlich günstiger als die Verwendung eines Vorförderdruckniveaus zur Betätigung der Hubsteuerventile. Auf eine separate druckgeregelte Vorförderpumpe kann verzichtet werden.From an energy point of view, this is much cheaper than using a pre-delivery pressure level to actuate the lift control valves. There is no need for a separate pressure-controlled feed pump.
Weitere Vorteile und vorteilhafte Ausgestaltungen des Gegenstands der Erfindung sind der Beschreibung, der Zeich- nung und den Ansprüchen entnehmbar.Further advantages and advantageous configurations of the object of the invention are the description, the drawing tion and the claims.
Zeichnungdrawing
Zwei Ausführungsbeispiele der erfindungsgemäßen Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen sind in der Zeichnung dargestellt und werden in der nachfolgenden Beschreibung näher erläutert. Es zeigen:Two exemplary embodiments of the fuel injection device according to the invention for internal combustion engines are shown in the drawing and are explained in more detail in the description below. Show it:
Fig. 1 ein erstes Ausführungsbeispiel einer Kraftstoff- einspriczvorrichtung in einer schematischen Gesamtdarstellung; und1 shows a first exemplary embodiment of a fuel injection device in a schematic overall illustration; and
Fig. 2 ein zweites Ausführungsbeispiel einer Kraftstoffeinspritzvorrichtung analog zur Darstellung in Fig. 1.FIG. 2 shows a second exemplary embodiment of a fuel injection device analogous to the representation in FIG. 1.
Beschreibung der AusführungsbeispieleDescription of the embodiments
Das in Fig. 1 insgesamt mit 1 bezeichnete erste Ausführungsbeispiel einer Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen weist eine Kraftstoffhochdruckpumpe 2 auf, die saugseitig mit einem Kraftstofftank 3 und druckseitig mit einem Hochdruckspeicher (Common ail) 4 verbunden ist . Von diesem Hochdruckspeicher 4 wird der unter Hochdruck stehende Kraftstoff über Zufuhrleitungen 5 zu den einzelnen, in den Brennraum der zu versorgenden Brenn- kraftmaschine ragenden druckgesteuerten Einspritzventile1, the first exemplary embodiment of a fuel injection device for internal combustion engines has a high-pressure fuel pump 2, which is connected on the suction side to a fuel tank 3 and on the pressure side to a high-pressure accumulator (common mail) 4. From this high-pressure accumulator 4, the high-pressure fuel is supplied via feed lines 5 to the individual pressure-controlled injection valves projecting into the combustion chamber of the internal combustion engine to be supplied
(Injektoren) 6 abgeführt, von denen in Fig. 1 nur eines gezeigt ist. Zur Steuerung des Einspritzvorganges ist je- dem Einspritzventil 6 jeweils ein elektrisch betätigbares Zumeßventil 7 in Form z.B. eines 3/2-Wege-Ventils zugeordnet. Der Druck im Hochdruckspeicher 4 wird mittels eines 2/2-Wege-Magnetventils 8 gesteuert, über das der Hoch- druckspeicher 4 mit dem Kraftstoff ank 3, d.h. mit der Leckölseite verbindbar ist.(Injectors) 6 discharged, of which only one is shown in Fig. 1. To control the injection process, the injector 6 each have an electrically actuated metering valve 7 in the form of, for example, a 3/2-way valve. The pressure in the high-pressure accumulator 4 is controlled by means of a 2/2-way solenoid valve 8, via which the high-pressure accumulator 4 is connected to the fuel 3, that is to say can be connected to the leak oil side.
Das als A-Düse ausgebildete Einspritzventil 6 umfaßt ein gegen die Wirkung einer Schließfeder 9 nach außen aus ei- ner Führungsbohrung 10 des Ventilgehäuses austauchendes kolbenförmiges Ventilglied 11. Am Ventilglied 11 sind zwei axial übereinander liegende Reihen von Spritzlöchern 12, 13 vorgesehen, die beim nach außen gerichteten Öffmαngshub des Ventilglieds 11 nacheinander aufsteuerbar sind. Über Längskanäle 14 im Ventilglied 11 sind die Spritzlöcher 12, 13 mit einem ringförmigen Druckraum 15 verbunden, in den die Zufuhrleitung 5 im Einspritzventil 6 mündet. Im Bereich des Druckraums 15 hat das Ventilglied 11 eine Druckschulter 16, an welcher der über die Zufuhrleitung 5 zuge- führte Kraftstoff im Öffnungssinn (d.h. nach außen) amThe injection valve 6, which is designed as an A nozzle, comprises a piston-shaped valve member 11, which protrudes outward from the guide bore 10 of the valve housing against the action of a closing spring 9. Two axially superimposed rows of spray holes 12, 13 are provided on the valve member 11 externally directed opening stroke of the valve member 11 can be opened in succession. The spray holes 12, 13 are connected via longitudinal channels 14 in the valve member 11 to an annular pressure chamber 15, into which the supply line 5 opens into the injection valve 6. In the area of the pressure chamber 15, the valve member 11 has a pressure shoulder 16, on which the fuel supplied via the supply line 5 in the opening direction (i.e. to the outside) on
Ventilglied 11 angreift. Das Ventilglied 11 ist am einen Ende eines Schafts 17 vorgesehen, der an seinem anderen Ende einen Federteller 18 trägt, an welchem die anderen- ends am Ventilgehäuse abgestützte Schließfeder 9 angreift. Der vom Ventilglied 11 beim Öffnen durchgeführte Hub wird durch einen hydraulischen Hubanschlag 19 gesteuert . Der dazu am Schaft 17 vorgesehene Kolben 20 begrenzt mit seiner einen Stirnseite einen Dä pfungsraum 21 mit zwei axial zueinander versetzten Entlastungskanälen 22, 23, die beim Öffnungshub des Ventilglieds 11 nacheinander verschlossen werden. Über den ersten Entlastungskanal 22 ist der Dämpfungsraum 21 mit dem Kraftstofftank 3, d.h. mit der Leck- ölseite, und über den zweiten Entlastungskanal 23 mit einem hydraulisch steuerbaren, federbelasteten Hubsteυerven- til 24 (3/2-Wege-Ventil) verbunden, welches in Abhängigkeit des in seiner Steuerleitung 25 herrschenden Drucks den Dämpfungsraum 21 mit dem Kraftstofftank 3, d.h. mit der Leckölseite, oder mit einem Druckspeicher 26 verbindet. Die Steuerleitungen 25 der Hubsteuervenuile 24 sind über ein 3/2 -Wege-Steuerventil 27 entweder mit dem Druckspeicher 26 oder mit dem Kraf stofftank 3, d.h. mit der Leckölseite verbindbar. Das Steuerventil 27 kann über einen Aktor betätigt werden, um die Hubsteuerventile 24 aller Einspritzventile 6 gleichzeitig umzuschalten. Über das Zumeßventil 7 und ein dazwischen vorgesehenes federbelastetes Gleichdruck- bzw. Druckregelventil 28 (z.B. auf 60 bar eingestellt) läßt sich der Druckspeicher 26 mitValve member 11 attacks. The valve member 11 is provided at one end of a shaft 17, which at its other end carries a spring plate 18, on which the closing spring 9, which is supported at the other end on the valve housing, engages. The stroke performed by the valve member 11 when opening is controlled by a hydraulic stroke stop 19. The piston 20 provided for this purpose on the shaft 17 delimits with its one end a damping space 21 with two axially offset relief channels 22, 23, which are closed in succession during the opening stroke of the valve member 11. The damping chamber 21 with the fuel tank 3, ie with the leakage, is connected via the first relief channel 22. oil side, and connected via the second relief channel 23 to a hydraulically controllable, spring-loaded stroke control valve 24 (3/2-way valve) which, depending on the pressure prevailing in its control line 25, connects the damping chamber 21 with the fuel tank 3, ie with the Leakage oil side, or connects to a pressure accumulator 26. The control lines 25 of the stroke control valves 24 are connected via a 3/2-way control valve 27 either to the pressure accumulator 26 or to the fuel tank 3, that is to say to the leakage oil side. The control valve 27 can be actuated by an actuator in order to switch over the stroke control valves 24 of all the injection valves 6 at the same time. Via the metering valve 7 and a spring-loaded constant pressure or pressure regulating valve 28 provided therebetween (for example set to 60 bar), the pressure accumulator 26 can also be used
Kraftstoff aus dem Druckraum 15 füllen, wobei der Druc - Speicher 26 über ein weiteres federbelastetes Gleichdruck- bzw. Druckregelventil 29 (auf z.B. 10 bar eingestellt) mit dem Kraftstofftank 3, d.h. mit der Leckölseite verbunden ist. Mit Hilfe des Druckregelventils 28 wird im Lecköl- rücklauf des Zumeßventils 7 ein Standdruck von 60 bar und anschließend durch das Druckregelventil 29 im Druckspeicher 26 ein zweites tieferes Druckniveau von 10 bar erzeugt, welches für die Niederdrucksteuerung der Hubsteuer- ventile 24 herangezogen wird. Der gesamte Steuermengenbedarf kann aus der Absteuerung (Druckentlastung) der Einspritzventile 6 gedeckt werden.Fill fuel from the pressure chamber 15, the pressure accumulator 26 via a further spring-loaded constant pressure or pressure control valve 29 (set to e.g. 10 bar) with the fuel tank 3, i.e. is connected to the leak oil side. With the help of the pressure control valve 28, a standing pressure of 60 bar is generated in the leak oil return of the metering valve 7 and then a second lower pressure level of 10 bar is generated by the pressure control valve 29 in the pressure accumulator 26, which pressure level is used for the low pressure control of the stroke control valves 24. The entire control quantity requirement can be covered by the control (pressure relief) of the injection valves 6.
Die Kraftstoffeinspritzung, d.h. der Öffnungshub des Ven- tilglieds 11, wird durch Bestromen des Zumeßventils 7 eingeleitet . Bei unbestromtem 3/2-Wege-Steuerventil 27 herrscht in der Steuerleitung 25 der Steuerdruck des Druckspeichers 26, so daß das Hubsteuerventil 24 mit Hilfe dieses Steuerdruckes entgegen der Federkraft geschaltet wird und, wie in Fig. 1 gezeigt, den Dämpfungsraum 21 mit dem Kraftstofftank 3 verbindet. Dann strömt beim Öffnen des Ventilglieds 11 der durch den Kolben 20 aus dem Dämpfungsraum 21 verdrängte Kraftstoff über den zweiten Entlastungskanal 23 ab, so daß eine Hubbegrenzung nicht stattfindet. Erst wenn der Kolben 20 bei seiner Hubbewegung den zweiten Entlastungskanal 23 mit seiner Steuerkante 30 verschließt, wird der im Dämpfungsraum 21 befindliche Kraftstoff durch den Kolben 20 komprimiert und dadurch der Öffnungshub des Ventilglieds 11 hydraulisch begrenzt. Bei diesem Maximalhub des Ventil - glieds 11 von 100% sind beide Spritzlochreihen 12, 13 freigegeben.The fuel injection, ie the opening stroke of the valve member 11, is initiated by energizing the metering valve 7. When the 3/2-way control valve 27 is de-energized, the control pressure of the pressure accumulator 26 prevails in the control line 25, so that the stroke control valve 24 is switched against the spring force with the aid of this control pressure and, as shown in FIG. 1, the damping chamber 21 with the fuel tank 3 connects. Then, when the valve member 11 opens, the fuel displaced by the piston 20 from the damping chamber 21 flows out via the second relief channel 23, so that a stroke limitation does not take place. Only when the piston 20 closes the second relief channel 23 with its control edge 30 during its stroke movement is the fuel in the damping chamber 21 compressed by the piston 20 and the opening stroke of the valve member 11 is thereby hydraulically limited. With this maximum stroke of the valve member 11 of 100%, both rows of spray holes 12, 13 are released.
Hingegen ist bei geöffnetem, d.h. bestromtem 3/2 -Wege- Steuerventil 27 die Steuerleitung 25 mit dem Kraftstoff- tank 3 verbunden und damit entlastet, so daß das Hubsteuerventil 24 nunmehr den Dämpfungsraum 21 mit dem Druckspeicher 26 verbindet. Der Druckspeicher 26 hat ein sehr geringes Volumen, um einen präzisen Hubanschlag zu gewährleisten, ist aber so groß, daß es nicht zu Schwingungen des Ventilglieds 11 kommt. Wenn beim Öffnen des Ventilglieds 11 der Kolben 20 mit seiner Steuerkante 30 den ersten Entlastungskanal 22 verschließt, wird der im Dämpfungsraum 21 befindliche Kraftstoff durch den Kolben 20 komprimiert. Dadurch wird der Öffnungshub des Ventilglieds 11 hydraulisch auf einen Teilhub von z.B. 50% begrenzt, bei dem nur die unteren Spritzlöcher 12 für eine Einspritzung freigegeben werden. Bei der in Fig..2 gezeigten Kraf tstof feinspritzvorrichtungIn contrast, when the 3/2-way control valve 27 is open, ie energized, the control line 25 is connected to the fuel tank 3 and is thus relieved, so that the stroke control valve 24 now connects the damping chamber 21 to the pressure accumulator 26. The pressure accumulator 26 has a very small volume to ensure a precise stroke stop, but is so large that the valve member 11 does not vibrate. If, when the valve member 11 opens, the piston 20 closes the first relief channel 22 with its control edge 30, the fuel located in the damping chamber 21 is compressed by the piston 20. As a result, the opening stroke of the valve member 11 is hydraulically limited to a partial stroke of, for example, 50%, in which only the lower spray holes 12 are released for injection. In the fuel injection device shown in Fig. 2
31 ist die Steuerleitung 25 der Hubsteuerventile 24 über ein 2/2-Wege-Steuerventil 32 mit dem Kraftstoff ank 3 verbindbar und über eine Drossel 33 mit dem Druckspeicher 26 verbunden.31, the control line 25 of the stroke control valves 24 can be connected to the fuel ank 3 via a 2/2-way control valve 32 and is connected to the pressure accumulator 26 via a throttle 33.
Bei geschlossenem, d.h. unbestromtem 2/2-Wege-SteuerventilWhen closed, i.e. deenergized 2/2-way control valve
32 herrscht in der Steuerleitung 25 der Steuerdruck des Druckspeichers 26, so daß das Hubsteuerventil 24 entgegen der Federkraft geschaltet wird, wie in Fig. 2 gezeigt ist.32, the control pressure of the pressure accumulator 26 prevails in the control line 25, so that the stroke control valve 24 is switched against the spring force, as shown in FIG. 2.
Hingegen wird bei geöffnetem, d.h. bestromtem 2/2-Wege- Steuerventil 32 permanent Kraftstoff aus dem Druckspeicher 26 über die Drossel 33 in den Kraftstofftank 3 gefördert, so daß die Steuerleitung 25 entlastet ist und das Hubsteu- erventil 24 durch die Federkraft in seine andere Stellung geschaltet wird. On the other hand, when the energized 2/2-way control valve 32 permanently fuel from the pressure accumulator 26 via the throttle 33 into the fuel tank 3, so that the control line 25 is relieved and the stroke control valve 24 is switched to its other position by the spring force.

Claims

Patentansprüche claims
1. Kraftstoffeinspritzvorrichtung (1; 31) für Brenn- kraft aschinen, mit jeweils einem in einer Zufuhrleitung (5) des Kraftstoffs vorgesehenen Einspritzventil (6) für jeden Zylinder der Brennkraftmaschine und mit einem den Öffnungshub des Ventilglieds (11) des Einspritzventils (6) begrenzenden hydraulischen Huban- schlag (19), der als hydraulischer Dämpfungsraum (21) ausgebildet ist und ein hydraulisch steuerbares Hubsteuerventil (24) aufweist, welches in Abhängigkeit des in seiner Steuerleitung (25) herrschenden Drucks die Verbindung des Dämpfungsraums (21) zur Leckölsei- te (3) sperrt, dadurch gekennzeichnet, daß die Steuerleitungen (25) der einzelnen Hubsteuerventile (24) über eine Steuerventileinheit entweder mit einem Niederdruckspeicher (26) oder mit dex Leck- ölseite (3) verbindbar sind.1. Fuel injection device (1; 31) for internal combustion engines, each with an injection valve (6) for each cylinder of the internal combustion engine provided in a supply line (5) of the fuel and with an opening stroke of the valve member (11) of the injection valve (6) delimiting hydraulic stroke stop (19), which is designed as a hydraulic damping chamber (21) and has a hydraulically controllable stroke control valve (24) which, depending on the pressure prevailing in its control line (25), connects the damping chamber (21) to the leakage oil line. te (3) blocks, characterized in that the control lines (25) of the individual stroke control valves (24) can be connected via a control valve unit either to a low-pressure accumulator (26) or to the dex leakage oil side (3).
2. Kraftstoffeinspritzvorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß die Steuerventileinheit durch ein 3/2-Wege-Steuerventil (27) gebildet ist, das die Steuerleitungen (25) der einzelnen Hubsteuer- ventile (24) entweder mit dem Niederdruckspeicher (26) oder der Leckölseite (3) verbindet.2. Fuel injection device according to claim 1, characterized in that the control valve unit is formed by a 3/2-way control valve (27) which the control lines (25) of the individual stroke control valves (24) either with the low pressure accumulator (26) or the leak oil side (3) connects.
3. Kraftstoffeinspritzvorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß die Steuerventileinheit durch ein 2/2-Wege-Steuerventil (32) , mittels dem die Steuerleitungen (25) der einzelnen Hubsteuerventile (24) mit der Leckölseite (3) verbindbar sind, und durch eine Drosssel (33) , mittels der die Steuerleitungen (25) der einzelnen Hubsteuerventile (24) mit dem Niederdruckspeicher (26) verbunden sind, gebildet ist .3. Fuel injection device according to claim 1, characterized in that the control valve unit by a 2/2-way control valve (32) by means of which the Control lines (25) of the individual stroke control valves (24) can be connected to the leakage oil side (3), and are formed by a throttle (33) by means of which the control lines (25) of the individual stroke control valves (24) are connected to the low-pressure accumulator (26) is.
4. Kraftstoffeinspritzvorrichcung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß der Niederdruckspeicher (26) mit dem Druckraum (15) der einzelnen Einspritzventile (6) jeweils über eine Ventileinheit verbunden ist.4. Fuel injection device according to one of the preceding claims, characterized in that the low-pressure accumulator (26) is connected to the pressure chamber (15) of the individual injection valves (6) in each case via a valve unit.
5. Kraftstoffeinspritzvorrichtung nach Anspruch 4, da- durch gekennzeichnet, daß die Ventileinheit durch das die Kraftstoffzumessung eines Einspritzventils (6) steuernde Zumeßventils (7) gebildet ist, das den Druckraum (15) des Einspritzventils (6) entweder mit dem einzuspritzenden Kraftstoff und oder mit dem Nie- derdruckspeicher (26) verbindet.5. Fuel injection device according to claim 4, characterized in that the valve unit is formed by the metering valve (7) which controls the fuel metering of an injection valve (6) and which forms the pressure chamber (15) of the injection valve (6) either with the fuel to be injected and or connects to the low pressure accumulator (26).
6. Kraftstoffeinspritzvorrichtung nach Anspruch 4 oder 5, dadurch gekennzeichnet, daß der Niederdruckspeicher (26) über ein erstes Druckregelventil (28) mit der Ventileinheit verbunden ist.6. Fuel injection device according to claim 4 or 5, characterized in that the low pressure accumulator (26) via a first pressure control valve (28) is connected to the valve unit.
7. Kraftstoffeinspritzvorrichtung nach einem der Ansprüche 4 bis 6, dadurch gekennzeichnet, daß der Druckspeicher (26) über ein zweites Druckregelventil (29) mit der Leckölseite (3) verbunden ist.7. Fuel injection device according to one of claims 4 to 6, characterized in that the pressure accumulator (26) via a second pressure control valve (29) with the leak oil side (3) is connected.
8. Kraftstoffeinspritzvorrichtung nach einem der vorher- gehenden Ansprüche, dadurch gekennzeichnet, daß die Steuerventileinheit elektrisch betätigbar ist.8. Fuel injection device according to one of the previously outgoing claims, characterized in that the control valve unit is electrically actuated.
9. Kraftstoffeinspritzvorrichtung nach einem der vorher- gehenden Ansprüche, dadurch gekennzeichnet, daß die hydraulisch gesteuerten Hubsteuerventile (24) der einzelnen Einspritzventile (6) jeweils durch ein 3/2- Wege-Ventil gebildet sind, das den Dämpfungsraum (21) des jeweiligen Einspritzventils (6) entweder mit der Leckölseite (3) oder mit einem Druckbehälter, insbesondere mit dem Niederdruckspeicher (26) verbindet. 9. Fuel injection device according to one of the preceding claims, characterized in that the hydraulically controlled stroke control valves (24) of the individual injection valves (6) are each formed by a 3/2-way valve which forms the damping chamber (21) of the respective injection valve (6) either with the leak oil side (3) or with a pressure vessel, in particular with the low pressure accumulator (26).
EP02732356A 2001-03-29 2002-03-27 Fuel injection device for internal combustion engines Withdrawn EP1373717A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10115396 2001-03-29
DE2001115396 DE10115396A1 (en) 2001-03-29 2001-03-29 Fuel injection device for internal combustion engines
PCT/DE2002/001109 WO2002079638A1 (en) 2001-03-29 2002-03-27 Fuel injection device for internal combustion engines

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EP1373717A1 true EP1373717A1 (en) 2004-01-02

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EP (1) EP1373717A1 (en)
JP (1) JP2004518897A (en)
BR (1) BR0204505A (en)
DE (1) DE10115396A1 (en)
WO (1) WO2002079638A1 (en)

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DE102008053873B4 (en) * 2008-10-30 2012-08-30 Vialle Alternative Fuel Systems B.V. Internal combustion engine and method for operating an internal combustion engine

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DE2260565B2 (en) * 1972-12-11 1975-11-13 Hermann Berstorff Maschinenbau Gmbh, 3000 Hannover Method and device for mixing plastic or rubber in a two-roller mixing mill
DE19618698A1 (en) * 1996-05-09 1997-11-13 Bosch Gmbh Robert Fuel injection valve for internal combustion engines
DE19739905A1 (en) * 1997-09-11 1999-03-18 Bosch Gmbh Robert Fuel injector
AT2960U3 (en) * 1998-07-02 1999-11-25 Avl List Gmbh INTERNAL COMBUSTION ENGINE WITH DIRECT INJECTION
DE19900037A1 (en) * 1999-01-02 2000-07-06 Bosch Gmbh Robert Fuel injector
DE19939421A1 (en) * 1999-08-20 2001-03-01 Bosch Gmbh Robert Combined stroke / pressure controlled fuel injection method and system for an internal combustion engine
DE10100512A1 (en) * 2000-02-07 2001-08-09 Bosch Gmbh Robert Injector

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Title
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DE10115396A1 (en) 2002-10-10
BR0204505A (en) 2003-04-08

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