EP1421272B1 - Fuel-injection device for internal combustion engines - Google Patents

Fuel-injection device for internal combustion engines Download PDF

Info

Publication number
EP1421272B1
EP1421272B1 EP02760079A EP02760079A EP1421272B1 EP 1421272 B1 EP1421272 B1 EP 1421272B1 EP 02760079 A EP02760079 A EP 02760079A EP 02760079 A EP02760079 A EP 02760079A EP 1421272 B1 EP1421272 B1 EP 1421272B1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
fuel
injection
injection device
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP02760079A
Other languages
German (de)
French (fr)
Other versions
EP1421272A1 (en
Inventor
Friedrich Boecking
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 EP1421272A1 publication Critical patent/EP1421272A1/en
Application granted granted Critical
Publication of EP1421272B1 publication Critical patent/EP1421272B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
    • F02M63/0042—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing combined with valve seats of the lift valve type
    • 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • 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
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
    • F02M57/025—Injectors structurally combined with fuel-injection pumps characterised by the pump drive hydraulic, e.g. with pressure amplification
    • 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/105—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive hydraulic drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0049—Combined valve units, e.g. for controlling pumping chamber and injection valve

Definitions

  • the invention is based on a fuel injection device according to the preamble of claim 1.
  • the valve is for controlling the in the control room prevailing pressure as a slide valve and the valve to Switching the injection pressure formed as a seat valve.
  • the fuel injection device shown in FIG. 1 1 for internal combustion engines comprises a high-pressure accumulator 2 (common rail), is mounted in the fuel at a fuel pressure P1. From the high-pressure accumulator 2, the fuel is discharged respectively via pressure lines 3 and injection lines 4 to the individual, projecting into the combustion chamber of the internal combustion engine to be supplied injectors (injectors) 5 , of which in Fig. 1, only one is shown.
  • injectors injectors
  • the valve sealing surface 8 facing away from the end face of the valve member 7 forms a second control surface 14, which limits a control chamber 15 and acts in the valve closing direction.
  • the control chamber 15 is connected via a Z-throttle 16 with the injection line 4 and via an A-throttle 17 and a slide valve 18 with a discharge line (oil leakage) 19 connectable.
  • the second control surface 14 is larger than the first control surface 13, so that when the slide valve 18 is closed, ie at the same pressure in the nozzle chamber 12 and the control chamber 15, the valve member 7, the injection ports 11 closes.
  • a local pressure booster unit 20 is provided with a against the action of a return spring 21 axially displaceable translation piston 22 , which primary side a primary chamber 23 , the secondary side, a secondary chamber 24 and the pressure side, a pressure chamber 25 limited.
  • the primary chamber 23 is connected directly, the secondary chamber 24 via a throttle 26 and the pressure chamber 25 via a check valve 27 to the pressure line 3, wherein the injection line 4 goes off from the pressure chamber 25.
  • the secondary chamber 24 is connected to the discharge line 19. With closed switching valve 28 prevails in all three chambers 23, 24, 25 of the fuel pressure P1 of the pressure accumulator 2, so that the transmission piston 22 is pressed by the return spring 21 in its initial position.
  • the slide valve 18 and the seat valve 28 are combined to form a 4/3 control valve 29 with a common valve body 30 .
  • the valve body 30 is slidably mounted in an axial guide bore 31 of the valve housing and axially adjustable by means of a piezoelectric actuator 32 .
  • the slide valve 18 has on the input side a provided in the wall of the guide bore 29, lower annular space 33 , in which the outgoing from the control chamber 15 line opens.
  • the slide valve 18 On the output side, the slide valve 18 has a provided on the valve body 30, lower annular space 34 , which opens to the annular space 33 through. Via a transverse bore 35 and a longitudinal bore 36 of the valve body 30, the lower annular space 34 of the valve body 30 is connected to the front side of the guide bore 29 outgoing discharge line 19.
  • the slide valve 18 closes when at a stroke H 2 of the valve body 30, the control edge 37 of the annular space 34, the upper sealing edge 38 of the annular space 33 passes over.
  • Fig. 2 the timing of the injection process is plotted in a diagram.
  • the beginning of the injection process is initiated at time t0 by a stroke H 1 of the valve body 30, so that the seat valve 28 opens and the slide valve 18 remains open.
  • the secondary chamber 24 is depressurized, and in the pressure chamber 25 and thus also in the nozzle chamber 12, a higher fuel pressure builds up.
  • the valve member 7 opens under pressure control against the action of the closing spring 9 and is controlled to maximum stroke h max , so that the injection takes place with the pressure prevailing in the nozzle chamber 12 fuel pressure.
  • the maximum injection pressure P max results from the piston cross-sectional ratio in the primary and pressure chambers 23, 25.
  • the slide valve 18 is closed by a stroke H 2 of the valve body 30.
  • the control chamber 15 is no longer depressurized, and the pressure in the control chamber 15 increases, so that the valve member 7 closes the injection openings 11 in a stroke-controlled manner.
  • the slide valve 18 is opened and the seat valve 28 is closed.
  • the control chamber 15 is depressurized again, and the valve member 7 opens hubsammlung, so that a post-injection with the prevailing in the injection chamber 12 fuel pressure, for example, with P max occurs.
  • the injection process is terminated at time t4 when the fuel pressure prevailing in the nozzle chamber 12 becomes smaller than the opening pressure P S. Due to the no longer pressure-relieved secondary chamber 24, the transmission piston 22 is pressed by the return spring 21 in its initial position and the pressure chamber 25 filled with fuel from the pressure accumulator 2.

Abstract

The invention relates to a fuel-injection device (1) for internal combustion engines, comprising several fuel injectors (5), each mounted in a fuel-injection tubing (4). Each fuel injector (5) comprises a nozzle chamber (12) and a pilot chamber (15), which are both connected to the fuel-injection tubing (4), a valve member (7) for controlling the injection openings (11) of the nozzle chamber (12), said valve member being operable at a first control surface (13), which is situated in the nozzle chamber (12) and acts in the valve opening direction and at a second control surface (14), which is situated in the pilot chamber (15) and acts in the valve closing direction, a first valve (18) for controlling the pressure prevailing in the pilot chamber (15) and a second valve (28) for controlling the injection pressure. According to the invention, a common valve body (30) is provided for both valves (18, 28), whereby the stroke (H2) of the valve body (30), which is necessary for closing the first valve (18), is larger than the stroke (H1), which is necessary for opening the second valve (28).

Description

Stand der TechnikState of the art

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

Bei einer bekannten Kraftstoffeinspritzvorrichtung dieser Art (DE 199 10 970 A1) ist der Steuerraum über ein 2/2-Wegeventil mit einer Entlastungsleitung verbindbar. Ein anderes 2/2-Wegeventil dient zur Aktivierung eines Druckübersetzers, mit dem ein hoher Einspritzdruck erzeugt wird (Siehe auch DE 10008268 A1).In a known fuel injection device of this Art (DE 199 10 970 A1) is the control room via a 2/2-way valve connectable with a discharge line. Another 2/2-way valve is used to activate a pressure booster, with which generates a high injection pressure is (see also DE 10008268 A1).

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Kraftstoffeinspritzvorrichtung mit den kennzeichnenden Merkmalen des Patentanspruchs 1 hat demgegenüber den Vorteil, daß der gemeinsame Ventilkörper von einem einzigen Stellantrieb betätigbar ist und so ein Ventilkörper und ein Stellantrieb eingespart werden können.The fuel injection device according to the invention with has the characterizing features of claim 1 In contrast, the advantage that the common valve body can be actuated by a single actuator and so on Valve body and an actuator can be saved.

Vorzugsweise ist das Ventil zum Steuern des im Steuerraum herrschenden Drucks als Schieberventil und das Ventil zum Schalten des Einspritzdruckes als Sitzventil ausgebildet.Preferably, the valve is for controlling the in the control room prevailing pressure as a slide valve and the valve to Switching the injection pressure formed as a seat valve.

Weitere Vorteile und vorteilhafte Ausgestaltungen des Gegen stands der Erfindung sind der Beschreibung, der Zeichnung und den Ansprüchen entnehmbar.Further advantages and advantageous embodiments of the counter state of the invention are the description of the drawing and the claims.

Zeichnungdrawing

Ein Ausführungsbeispiel der erfindungsgemäßen Kraftstoffeinspritzvorrichtung ist in der Zeichnung dargestellt und wird in der nachfolgenden Beschreibung näher erläutert. Es zeigen:

Fig. 1
die wesentlichen Komponenten einer erfindungsgemäßen Kraftstoffeinspritzvorrichtung mit einem 4/3-Steuerventil zum Steuern des Einspritzvorgangs; und
Fig. 2
ein Diagramm, das für die in Fig. 1 dargestellte Kraftstoffeinspritzvorrichtung über die Zeitachse den Hub (H) des Ventilkörpers des 4/3-Steuerventils, den Einspritzdruck (P) und den Hub (h) des Ventilglieds des Einspritzventils angibt.
An embodiment of the fuel injection device according to the invention is shown in the drawing and will be explained in more detail in the following description. Show it:
Fig. 1
the essential components of a fuel injection device according to the invention with a 4/3-control valve for controlling the injection process; and
Fig. 2
a diagram indicating the stroke (H) of the valve body of the 4/3-control valve, the injection pressure (P) and the stroke (h) of the valve member of the injection valve over the time axis for the fuel injection device shown in FIG.

Beschreibung der AusführungsbeispieleDescription of the embodiments

Die in Fig. 1 gezeigte Kraftstoffeinspritzvorrichtung 1 für Brennkraftmaschinen umfaßt einen Hochdruckspeicher 2 (Common Rail), in dem Kraftstoff unter einem Kraftstoffdruck P1 gelagert ist. Vom Hochdruckspeicher 2 wird der Kraftstoff jeweils über Druckleitungen 3 und Einspritzleitungen 4 zu den einzelnen, in den Brennraum der zu versorgenden Brennkraftmaschine ragenden Einspritzventilen (Injektoren) 5 abgeführt, von denen in Fig. 1 nur eines gezeigt ist.The fuel injection device shown in FIG. 1 1 for internal combustion engines comprises a high-pressure accumulator 2 (common rail), is mounted in the fuel at a fuel pressure P1. From the high-pressure accumulator 2, the fuel is discharged respectively via pressure lines 3 and injection lines 4 to the individual, projecting into the combustion chamber of the internal combustion engine to be supplied injectors (injectors) 5 , of which in Fig. 1, only one is shown.

In einer axialen Führungsbohrung 6 des Einspritzventils 5 ist ein kolbenförmiges Ventilglied (Düsennadel) 7 mit einer konischen Ventildichtfläche 8 verschiebbar gelagert, welche durch eine Schließfeder 9 gegen eine konische Ventilsitzfläche 10 des Ventilgehäuses gedrückt wird und die dort vorgesehenen Einspritzöffnungen 11 verschließt. Die Einspritzleitung 4 mündet im Einspritzventil 5 in einen ringförmigen Düsenraum 12, von dem ein zwischen Führungsbohrung 6 und Ventilglied 7 verlaufender Ringspalt bis zur Ventilsitzfläche 10 führt. Das Ventilglied 7 hat im Bereich des Düsenraumes 12 eine als Druckschulter ausgebildete erste Steuerfläche 13, an welcher der über die Einspritzleitung 4 zugeführte Kraftstoff im Öffnungssinn (d.h. nach innen) am Ventilglied 7 angreift. Die der Ventildichtfläche 8 abgewandte Stirnseite des Ventilglieds 7 bildet eine zweite Steuerfläche 14, die einen Steuerraum 15 begrenzt und in Ventilschließrichtung wirkt. Der Steuerraum 15 ist über eine Z-Drossel 16 mit der Einspritzleitung 4 verbunden sowie über eine A-Drossel 17 und ein Schieberventil 18 mit einer Entlastungsleitung (Lecköl) 19 verbindbar. Die zweite Steuerfläche 14 ist größer als die erste Steuerfläche 13, so daß bei geschlossenem Schieberventil 18, d.h. bei gleichem Druck im Düsenraum 12 und im Steuerraum 15, das Ventilglied 7 die Einspritzöffnungen 11 verschließt. Die Z-Drossel 16 ist kleiner als die A-Drossel 17, so daß bei geöffnetem Schieberventil 18 der im Steuerraum 15 herrschende Druck über die Entlastungsleitung 19 abgebaut wird und oberhalb eines Öffnungsdruckes PS das Ventilglied 7 durch den im Düsenraum 12 herrschenden Druck gegen die Wirkung der Schließfeder 9 aufgesteuert wird.In an axial guide bore 6 of the injection valve 5, a piston-shaped valve member (nozzle needle) 7 is slidably mounted with a conical valve sealing surface 8 , which is pressed by a closing spring 9 against a conical valve seat surface 10 of the valve housing and the injection openings 11 provided there closes. In the injection valve 5, the injection line 4 opens into an annular nozzle chamber 12, from which an annular gap extending between guide bore 6 and valve member 7 leads to the valve seat surface 10. The valve member 7 has in the region of the nozzle chamber 12 designed as a pressure shoulder first control surface 13 to which the supplied via the injection line 4 fuel in the opening direction (ie, inwardly) engages the valve member 7. The valve sealing surface 8 facing away from the end face of the valve member 7 forms a second control surface 14, which limits a control chamber 15 and acts in the valve closing direction. The control chamber 15 is connected via a Z-throttle 16 with the injection line 4 and via an A-throttle 17 and a slide valve 18 with a discharge line (oil leakage) 19 connectable. The second control surface 14 is larger than the first control surface 13, so that when the slide valve 18 is closed, ie at the same pressure in the nozzle chamber 12 and the control chamber 15, the valve member 7, the injection ports 11 closes. The Z-throttle 16 is smaller than the A-throttle 17, so that when the slide valve 18 is open, the pressure prevailing in the control chamber 15 pressure on the discharge line 19 and above an opening pressure P S, the valve member 7 by the pressure prevailing in the nozzle chamber 12 against the pressure Effect of the closing spring 9 is turned on.

Für jedes Einspritzventil 5 ist eine lokale Druckübersetzungseinheit 20 mit einem gegen die Wirkung einer Rückstellfeder 21 axial verschiebbaren Übersetzungskolben 22 vorgesehen, welcher primärseitig eine Primärkammer 23, sekundärseitig eine Sekundärkammer 24 und druckseitig eine Druckkammer 25 begrenzt. Die Primärkammer 23 ist direkt, die Sekundärkammer 24 über eine Drossel 26 und die Druckkammer 25 über ein Rückschlagventil 27 mit der Druckleitung 3 verbunden, wobei die Einspritzleitung 4 von der Druckkammer 25 abgeht. Über ein Sitzventil 28 ist die Sekundärkammer 24 mit der Entlastungsleitung 19 verbindbar. Bei geschlossenem Schaltventil 28 herrscht in allen drei Kammern 23, 24, 25 der Kraftstoffdruck P1 des Druckspeichers 2, so daß der Übersetzungskolben 22 durch die Rückstellfeder 21 in seine Ausgangslage gedrückt ist. Wird durch Öffnen des Sitzventils 28 die Sekundärkammer 24 druckentlastet, wird der Übersetzungskolben 22 in Kompressionsrichtung verschoben und dadurch entsprechend dem Kolbenquerschnittsverhältnis in Primär- und Druckkammer 23, 25 der in der Druckkammer 25 befindliche Kraftstoff auf einen höheren Kraftstoffdruck komprimiert. Das Rückschlagventil 27 verhindert dabei den Rückfluß von komprimiertem Kraftstoff zurück in die Druckleitung 3.For each injection valve 5, a local pressure booster unit 20 is provided with a against the action of a return spring 21 axially displaceable translation piston 22 , which primary side a primary chamber 23 , the secondary side, a secondary chamber 24 and the pressure side, a pressure chamber 25 limited. The primary chamber 23 is connected directly, the secondary chamber 24 via a throttle 26 and the pressure chamber 25 via a check valve 27 to the pressure line 3, wherein the injection line 4 goes off from the pressure chamber 25. About a seat valve 28 , the secondary chamber 24 is connected to the discharge line 19. With closed switching valve 28 prevails in all three chambers 23, 24, 25 of the fuel pressure P1 of the pressure accumulator 2, so that the transmission piston 22 is pressed by the return spring 21 in its initial position. If the secondary chamber 24 is relieved of pressure by opening the poppet valve 28, the transmission piston 22 is displaced in the compression direction and compressed according to the piston cross-sectional ratio in the primary and pressure chambers 23, 25 of the fuel in the pressure chamber 25 to a higher fuel pressure. The check valve 27 prevents the return flow of compressed fuel back into the pressure line. 3

Das Schieberventil 18 und das Sitzventil 28 sind zu einem 4/3-Steuerventil 29 mit einem gemeinsamen Ventilkörper 30 zusammengefaßt. Der Ventilkörper 30 ist in einer axialen Führungsbohrung 31 des Ventilgehäuses verschiebbar gelagert und mittels eines piezoelektrischen Stellantriebs 32 axial verstellbar.The slide valve 18 and the seat valve 28 are combined to form a 4/3 control valve 29 with a common valve body 30 . The valve body 30 is slidably mounted in an axial guide bore 31 of the valve housing and axially adjustable by means of a piezoelectric actuator 32 .

Das Schieberventil 18 weist eingangsseitig einen in der Wand der Führungsbohrung 29 vorgesehenen, unteren Ringraum 33 auf, in den die vom Steuerraum 15 abgehende Leitung mündet. Ausgangsseitig weist das Schieberventil 18 einen am Ventilkörper 30 vorgesehenen, unteren Ringraum 34 auf, der sich zum Ringraum 33 hin öffnet. Über eine Querbohrung 35 und eine Längsbohrung 36 des Ventilkörpers 30 ist der untere Ringraum 34 des Ventilkörpers 30 mit der stirnseitig von der Führungsbohrung 29 abgehenden Entlastungsleitung 19 verbunden. Das Schieberventil 18 sperrt, wenn bei einem Hub H2 des Ventilkörpers 30 die Steuerkante 37 des Ringraums 34 die obere Dichtkante 38 des Ringraums 33 überfährt.The slide valve 18 has on the input side a provided in the wall of the guide bore 29, lower annular space 33 , in which the outgoing from the control chamber 15 line opens. On the output side, the slide valve 18 has a provided on the valve body 30, lower annular space 34 , which opens to the annular space 33 through. Via a transverse bore 35 and a longitudinal bore 36 of the valve body 30, the lower annular space 34 of the valve body 30 is connected to the front side of the guide bore 29 outgoing discharge line 19. The slide valve 18 closes when at a stroke H 2 of the valve body 30, the control edge 37 of the annular space 34, the upper sealing edge 38 of the annular space 33 passes over.

Das Sitzventil 28 weist eingangsseitig einen in der Wand der Führungsbohrung 29 vorgesehenen, oberen Ringraum 39 mit einer konischen Ventilsitzfläche 40 auf, in den die von der Sekundärkammer 24 abgehende Leitung mündet. Der Ventilkörper 30 hat eine mit der Ventilsitzfläche 40 zusammenwirkende konische Ventildichtfläche 41, die sich nach unten zu einem Ringraum 42 erweitert, von dem die Entlastungsleitung 19 abgeht.The seat valve 28 has on the input side provided in the wall of the guide bore 29, upper annular space 39 with a conical valve seat surface 40 into which the outgoing from the secondary chamber 24 line opens. The valve body 30 has a cooperating with the valve seat surface 40 conical valve sealing surface 41 , which widens down to an annular space 42 , from which the discharge line 19 goes off.

In der in Fig. 1 gezeigten Ausgangsstellung des 4/3-Steuerventils 29 ist das Schieberventil 18 geöffnet, so daß der Steuerraum 15 druckentlastet ist, und das Sitzventil 28 geschlossen, so daß die Sekundärkammer 24 nicht druckentlastet ist. Der zum Öffnen des Sitzventils 28 erforderliche Hub H1 des Ventilkörpers 30 ist kleiner als der zum Schließen des Schieberventils 18 erforderliche Hub H2.In the initial position of the 4/3-control valve 29 shown in Fig. 1, the slide valve 18 is opened, so that the control chamber 15 is depressurized, and the seat valve 28 is closed, so that the secondary chamber 24 is not depressurized. The required to open the poppet valve 28 stroke H 1 of the valve body 30 is smaller than the required to close the spool valve 18 Hub H 2 .

In Fig. 2 ist in einem Diagramm der zeitliche Ablauf des Einspritzvorgangs aufgetragen.
Der Beginn des Einspritzvorgangs wird zum Zeitpunkt t0 durch einen Hub H1 des Ventilkörpers 30 eingeleitet, so daß das Sitzventil 28 öffnet und das Schieberventil 18 geöffnet bleibt. Die Sekundärkammer 24 wird druckentlastet, und in der Druckkammer 25 und damit auch im Düsenraum 12 baut sich ein höherer Kraftstoffdruck auf.
Wenn zum Zeitpunkt t1 im Düsenraum 12 der Öffnungsdruck PS erreicht wird, öffnet das Ventilglied 7 gegen die Wirkung der Schließfeder 9 druckgesteuert und wird auf maximalen Hub hmax aufgesteuert, so daß die Einspritzung mit dem im Düsenraum 12 herrschenden Kraftstoffdruck erfolgt. Der maximale Einspritzdruck Pmax ergibt sich aus dem Kolbenquerschnittsverhältnis in Primär- und Druckkammer 23, 25.
Zum Zeitpunkt t2, zu dem der im Düsenraum 12 herrschende Druck noch höher als der Öffnungsdruck PS ist, wird durch einen Hub H2 des Ventilkörpers 30 das Schieberventil 18 geschlossen. Der Steuerraum 15 ist nicht mehr druckentlastet, und der Druck im Steuerraum 15 steigt an, so daß das Ventilglied 7 die Einspritzöffnungen 11 hubgesteuert verschließt.
Zum Zeitpunkt t3 werden durch Zurückstellen des Ventilkörpers 30 in seine Ausgangsstellung das Schieberventil 18 geöffnet und das Sitzventil 28 geschlossen. Der Steuerraum 15 ist wieder druckentlastet, und das Ventilglied 7 öffnet hubgesteuert, so daß eine Nacheinspritzung mit dem in der Einspritzkammer 12 herrschenden Kraftstoffdruck, z.B. mit Pmax, erfolgt.
Der Einspritzvorgang ist zum Zeitpunkt t4 beendet, wenn der im Düsenraum 12 herrschende Kraftstoffdruck kleiner als der Öffnungsdruck PS wird. Aufgrund der nicht mehr druckentlasteten Sekundärkammer 24 wird der Übersetzungskolben 22 durch die Rückstellfeder 21 in seine Ausgangslage gedrückt und die Druckkammer 25 mit Kraftstoff aus dem Druckspeicher 2 gefüllt.In Fig. 2 , the timing of the injection process is plotted in a diagram.
The beginning of the injection process is initiated at time t0 by a stroke H 1 of the valve body 30, so that the seat valve 28 opens and the slide valve 18 remains open. The secondary chamber 24 is depressurized, and in the pressure chamber 25 and thus also in the nozzle chamber 12, a higher fuel pressure builds up.
If the opening pressure P S is reached at the time t1 in the nozzle chamber 12, the valve member 7 opens under pressure control against the action of the closing spring 9 and is controlled to maximum stroke h max , so that the injection takes place with the pressure prevailing in the nozzle chamber 12 fuel pressure. The maximum injection pressure P max results from the piston cross-sectional ratio in the primary and pressure chambers 23, 25.
At the time t2, at which the pressure prevailing in the nozzle chamber 12 is still higher than the opening pressure P S , the slide valve 18 is closed by a stroke H 2 of the valve body 30. The control chamber 15 is no longer depressurized, and the pressure in the control chamber 15 increases, so that the valve member 7 closes the injection openings 11 in a stroke-controlled manner.
At time t3 , by returning the valve body 30 to its initial position, the slide valve 18 is opened and the seat valve 28 is closed. The control chamber 15 is depressurized again, and the valve member 7 opens hubgesteuert, so that a post-injection with the prevailing in the injection chamber 12 fuel pressure, for example, with P max occurs.
The injection process is terminated at time t4 when the fuel pressure prevailing in the nozzle chamber 12 becomes smaller than the opening pressure P S. Due to the no longer pressure-relieved secondary chamber 24, the transmission piston 22 is pressed by the return spring 21 in its initial position and the pressure chamber 25 filled with fuel from the pressure accumulator 2.

Claims (6)

  1. Fuel injection device (1) for internal combustion engines, with a plurality of injection valves (5) provided in each case in a fuel injection line (4), each injection valve (5) having a nozzle space (12) and a control space (15), which are both connected to the injection line (4), a valve member (7) which controls the injection orifices (11) of the nozzle space (12) and which can be actuated via a first control face (13) located in the nozzle space (12) and acting in the valve-opening direction and via a second control face (14) located in the control space (15) and acting in the valve-closing direction, a first valve (18) for controlling the pressure prevailing in the control space (15), and a second valve (28) for switching the injection pressure, characterized in that a common valve body (30) is provided for both valves (18, 28), and in that the stroke (H2) of the valve body (30) which is required for closing the first valve (18) is greater than the stroke (H1) required for opening the second valve (28).
  2. Fuel injection device according to Claim 1, characterized in that the first valve (18) is designed as a slide valve.
  3. Fuel injection device according to Claim 1 or 2, characterized in that the second valve (28) is designed as a seat valve.
  4. Fuel injection device according to one of the preceding claims, characterized in that the actuating drive provided for the valve body (30) is designed as a piezoelectric actuating drive (32).
  5. Fuel injection device according to one of the preceding claims, characterized in that at least one lower fuel pressure (P1) is stored in a central pressure accumulator (2).
  6. Fuel injection device according to one of the preceding claims, characterized in that the injection line (4) is connected both to a lower fuel pressure (P1) via a non-return valve (27) and to the pressure chamber (25) of a pressure intensification piston (22) activatable by means of the second valve (28).
EP02760079A 2001-08-22 2002-07-05 Fuel-injection device for internal combustion engines Expired - Lifetime EP1421272B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10141110 2001-08-22
DE10141110A DE10141110A1 (en) 2001-08-22 2001-08-22 Fuel injection device for internal combustion engines
PCT/DE2002/002463 WO2003018995A1 (en) 2001-08-22 2002-07-05 Fuel-injection device for internal combustion engines

Publications (2)

Publication Number Publication Date
EP1421272A1 EP1421272A1 (en) 2004-05-26
EP1421272B1 true EP1421272B1 (en) 2005-06-29

Family

ID=7696228

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02760079A Expired - Lifetime EP1421272B1 (en) 2001-08-22 2002-07-05 Fuel-injection device for internal combustion engines

Country Status (6)

Country Link
US (1) US6871636B2 (en)
EP (1) EP1421272B1 (en)
JP (1) JP4204467B2 (en)
DE (2) DE10141110A1 (en)
ES (1) ES2244798T3 (en)
WO (1) WO2003018995A1 (en)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10251932B4 (en) * 2002-11-08 2007-07-12 Robert Bosch Gmbh Fuel injection device with integrated pressure booster
DE10315016A1 (en) * 2003-04-02 2004-10-28 Robert Bosch Gmbh Fuel injector with a leak-free servo valve
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
JP4695453B2 (en) * 2005-07-29 2011-06-08 株式会社豊田中央研究所 Directional control valve
DE102005059437A1 (en) * 2005-12-13 2007-06-14 Robert Bosch Gmbh fuel injector
DE102006026381A1 (en) * 2006-06-07 2007-12-13 Robert Bosch Gmbh Fuel injector with pressure booster and piezo actuator arranged on the low pressure side
US10982635B2 (en) * 2012-05-29 2021-04-20 Delphi Technologies Ip Limited Fuel injector and method for controlling the same
DE102019218432A1 (en) * 2019-11-28 2021-06-02 Robert Bosch Gmbh Single-substance injector and injection system for injecting a medium

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CS188353B1 (en) * 1975-02-14 1979-03-30 Jaromir Indra Displacement valve for the injection pump of the combustion engines
GB9616521D0 (en) * 1996-08-06 1996-09-25 Lucas Ind Plc Injector
DE19910970A1 (en) 1999-03-12 2000-09-28 Bosch Gmbh Robert Fuel injector
DE19939448A1 (en) * 1999-08-20 2001-03-01 Bosch Gmbh Robert Injector
DE19956598A1 (en) * 1999-11-25 2001-06-13 Bosch Gmbh Robert Valve for controlling liquids
DE10008268A1 (en) * 2000-01-20 2001-08-02 Bosch Gmbh Robert Fuel injection device for internal combustion engine, with at least two valves operable by actuator
WO2001053696A2 (en) * 2000-01-20 2001-07-26 Robert Bosch Gmbh Injection device and method for injecting a fluid
DE10002702A1 (en) * 2000-01-22 2001-08-02 Bosch Gmbh Robert Valve for controlling liquids
JP2001323858A (en) * 2000-05-17 2001-11-22 Bosch Automotive Systems Corp Fuel injection device
DE10031278A1 (en) * 2000-06-27 2002-01-17 Bosch Gmbh Robert Fuel injection device for internal combustion engines

Also Published As

Publication number Publication date
US20040055573A1 (en) 2004-03-25
DE10141110A1 (en) 2003-03-20
US6871636B2 (en) 2005-03-29
DE50203522D1 (en) 2005-08-04
EP1421272A1 (en) 2004-05-26
WO2003018995A1 (en) 2003-03-06
ES2244798T3 (en) 2005-12-16
JP4204467B2 (en) 2009-01-07
JP2005500472A (en) 2005-01-06

Similar Documents

Publication Publication Date Title
EP1593839B1 (en) Fuel injector for combustion engines with a multi-stage control valve
EP1651862B1 (en) Control valve for a fuel injector comprising a pressure exchanger
DE102006062216A1 (en) fuel injector
EP1421272B1 (en) Fuel-injection device for internal combustion engines
WO2005015000A1 (en) Control valve with pressure compensation for a fuel injector comprising a pressure intensifier
DE102005032464A1 (en) Fuel injecting device for use in e.g. high pressure accumulator injecting system, has pre-controlling space and damping space hydraulically connected by connecting channel that has reactive unit serving as discharging reactor
EP1397593B1 (en) Fuel injection device with a pressure booster
DE10031574B4 (en) Pressure-controlled double-acting high-pressure injector
EP1939441A2 (en) Fuel injector
EP1354133B1 (en) Fuel-injection device
EP1719904A1 (en) Fuel injector
DE10301194A1 (en) Fuel injection device for an internal combustion engine (ICE) has a high-pressure fuel pump linked to a fuel injection valve for each cylinder in the ICE
EP2511514B1 (en) Fuel injector valve
EP1483499B1 (en) Installation for the pressure-modulated formation of the injection behavior
EP1310667B1 (en) Fuel injection system for a combustion engine
EP1310668B1 (en) Fuel injection system for a combustion engine
DE10307002A1 (en) Fuel injection nozzle has outer nozzle needle and control element in form of inner nozzle needle with first and second lower and higher fuel outlet cross-section positions
DE10141111B4 (en) Fuel injection device for internal combustion engines
EP1491757B1 (en) Fuel injection system for internal combustion engine
EP1434939B1 (en) Fuel injection device for internal combustion engines
DE10164395A1 (en) Fuel injection device for IC engine has leakage channel connecting control pressure space for valve piston to discharge bore
DE10148995A1 (en) Fuel injection system, for direct fuel injection at an IC motor, has a pressure unit for each injection valve with a piston return spring within the primary zone so that the piston is unaffected by hydraulic oscillations
DE10205750A1 (en) Fuel injection device for an internal combustion engine
EP1370766A1 (en) Fuel-injection valve for internal combustion engines
DE102009000281A1 (en) Fuel injector, particularly common rail injector for injecting fuel in combustion chamber of internal combustion engine, comprises injection valve element which is adjusted between closed position and open position

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20040322

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR IE IT LI LU MC NL PT SE SK TR

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE ES FR GB IT

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REF Corresponds to:

Ref document number: 50203522

Country of ref document: DE

Date of ref document: 20050804

Kind code of ref document: P

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20050928

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2244798

Country of ref document: ES

Kind code of ref document: T3

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20060330

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: ES

Payment date: 20080723

Year of fee payment: 7

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20080718

Year of fee payment: 7

Ref country code: IT

Payment date: 20080726

Year of fee payment: 7

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20080723

Year of fee payment: 7

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20080925

Year of fee payment: 7

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20090705

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20100331

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090731

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090705

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100202

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20090706

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090706

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090705