EP1421272A1 - Fuel-injection device for internal combustion engines - Google Patents

Fuel-injection device for internal combustion engines

Info

Publication number
EP1421272A1
EP1421272A1 EP02760079A EP02760079A EP1421272A1 EP 1421272 A1 EP1421272 A1 EP 1421272A1 EP 02760079 A EP02760079 A EP 02760079A EP 02760079 A EP02760079 A EP 02760079A EP 1421272 A1 EP1421272 A1 EP 1421272A1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
fuel
injection
chamber
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.)
Granted
Application number
EP02760079A
Other languages
German (de)
French (fr)
Other versions
EP1421272B1 (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

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 relates to a fuel injection device according to the preamble of claim 1.
  • control chamber is connected via a 2/2-way valve can be connected to a relief line.
  • Another 2/2-way valve is used to activate a pressure intensifier, which generates a high injection pressure.
  • the fuel injection device according to the invention with the characterizing features of claim 1 has the advantage that the common valve body can be actuated by a single actuator and thus a valve body and an actuator can be saved.
  • the valve for controlling the pressure prevailing in the control chamber is preferably designed as a slide valve and the valve for switching the injection pressure as a seat valve.
  • FIG. 1 shows the essential components of an inventive moderate fuel injection device with a 4/3 control valve for controlling the injection process
  • Fig. 2 is a diagram for that shown in Fig. 1
  • Fuel injector on the time axis indicates 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.
  • the fuel injection device 1 for internal combustion engines shown in FIG. 1 comprises a high-pressure accumulator 2 (common rail) in which fuel is stored at a fuel pressure Pl.
  • the fuel is discharged from the high-pressure accumulator 2 via pressure lines 3 and injection lines 4 to the individual injection valves (injectors) 5 projecting into the combustion chamber of the internal combustion engine to be supplied, only one of which is shown in FIG. 1.
  • a piston-shaped valve member (nozzle needle) 7 with a conical valve sealing surface 8 is displaceably mounted in an axial guide bore 6 of the injection valve 5, which is pressed by a closing spring 9 against a conical valve seat surface 10 of the valve housing and closes the injection openings 11 provided there.
  • the injection line 4 opens in the injection valve 5 into an annular nozzle chamber 12, from which an annular gap extending between the guide bore 6 and the valve member 7 extends up to Valve seat surface 10 leads.
  • the valve member 7 has a first control surface 13 designed as a pressure shoulder, on which the fuel supplied via the injection line 4 acts on the valve member 7 in the opening direction (ie inwards).
  • control chamber 15 is connected to the injection line 4 via a Z throttle 16 and via an A throttle 17 and a
  • Slider valve 18 can be connected to a relief line (leak oil) 19.
  • 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 in the control chamber 15, the valve member 7 closes the injection openings 11.
  • the inlet throttle 16 is smaller than the A-throttle '17 so that degrades opened slide valve 18 of 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 pressure against the effect of the closing spring 9 is turned on.
  • a local pressure transmission unit 20 is provided with a transmission piston 22 which is axially displaceable against the action of a return spring 21 and which delimits a primary chamber 23 on the primary side, a secondary chamber 24 on the secondary side and a pressure chamber 25 on the pressure side.
  • 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, the injection line 4 from the Pressure chamber 25 goes off.
  • the secondary chamber 24 can be connected to the relief line 19 via a seat valve 28.
  • the transmission piston 22 is displaced in the compression direction and the fuel in the pressure chamber 25 is compressed to a higher fuel pressure in accordance with the piston cross-sectional ratio in the primary and pressure chambers 23, 25.
  • the check valve 27 prevents the backflow of compressed fuel back into the pressure line 3.
  • 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 lower annular space 33, which is provided in the wall of the guide bore 29 and into which the line leading from the control space 15 opens.
  • the slide valve 18 On the output side, the slide valve 18 has a lower annular space 34, which is provided on the valve body 30 and opens towards the annular space 33.
  • the lower annular space 34 of the valve body 30 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 relief line 19 leading from the guide bore 29 on the end face.
  • the slide valve 18 blocks when at a stroke H 2 of the valve body 30, the control edge 37 of the annular space 34 passes over the upper sealing edge 38 of the annular space 33.
  • the seat valve 28 On the inlet side, the seat valve 28 has an upper annular space 39 provided in the wall of the guide bore 29 with a conical valve seat surface 40, into which the line leading from the secondary chamber 24 opens.
  • the valve body 30 has a conical valve sealing surface 41 which interacts with the valve seat surface 40 and widens downward to form an annular space 42 from which the relief line 19 branches off.
  • Fig. 2 is the timing of the
  • the start of the injection process is initiated at time t0 by a stroke H x of the valve body 30, so that the seat valve 28 opens and the slide valve 18 remains open.
  • the secondary chamber 24 is relieved of pressure, and a higher fuel pressure builds up in the pressure chamber 25 and thus also in the nozzle chamber 12. If the opening pressure P s is reached in the nozzle chamber 12 at the time t1, the valve member 7 opens against the action of the closing spring 9 and is controlled to maximum Stroke h max controlled so that the injection takes place with the fuel pressure prevailing in the nozzle chamber 12.
  • the maximum injection pressure P ma ⁇ results from the piston cross-sectional ratio in the primary and pressure chamber 23, 25.
  • the valve body 30 is opened and the seat valve 28 is closed by returning the valve body 30 to its starting position.
  • the control chamber 15 is again relieved of pressure and the valve member 7 opens in a stroke-controlled manner so that post-injection takes place with the fuel pressure prevailing in the injection chamber 12, for example with Pm a /.
  • the injection process ends at time t4 when the fuel pressure prevailing in the nozzle chamber 12 becomes lower than the opening pressure P s . Because the secondary chamber 24 is no longer relieved of pressure, the transmission piston 22 is pressed into its starting position by the return spring 21 and the pressure chamber 25 is 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

Kraftstoffeinspritzvorrichtung- für Brennkraftmaschinen Fuel injection device for internal combustion engines
Beschreibungdescription
Stand der TechnikState of the art
Die Erfindung geht aus von einer Kraftstoffeinspritzvorrichtung nach der Gattung des Patentanspruchs 1.The invention relates to a fuel injection device according to the preamble of claim 1.
Bei einer bekannten Kraftstoffeinspritzvorrichtung dieser Art (DE 199 10 970 AI) ist der Steuerraum über ein 2/2-We- geventil mit einer Entlastungsleitung verbindbar. Ein anderes 2/2-Wegeventil dient zur Aktivierung eines Druckübersetzers, mit dem ein hoher Einspritzdruck erzeugt wird.In a known fuel injection device of this type (DE 199 10 970 AI) the control chamber is connected via a 2/2-way valve can be connected to a relief line. Another 2/2-way valve is used to activate a pressure intensifier, which generates a high injection pressure.
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 the characterizing features of claim 1 has the advantage that the common valve body can be actuated by a single actuator and thus a 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.The valve for controlling the pressure prevailing in the control chamber is preferably designed as a slide valve and the valve for switching the injection pressure as a seat valve.
Weitere Vorteile und vorteilhafte Ausgestaltungen des Gegenstands der Erfindung sind der Beschreibung, der Zeichnung und den Ansprüchen entnehmbar.Further advantages and advantageous configurations of the subject matter of the invention can be found in the description, 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:An embodiment of the fuel injection device according to the invention is shown in the drawing and is explained in more detail in the following description. Show it:
Fig. 1 die wesentlichen Komponenten einer erfindungsge- mäßen Kraftstoffeinspritzvorrichtung mit einem 4/3-Steuerventil zum Steuern des Einspritzvorgangs ; und1 shows the essential components of an inventive moderate fuel injection device with a 4/3 control valve for controlling the injection process; and
Fig. 2 ein Diagramm, das für die in Fig. 1 dargestellteFig. 2 is a diagram for that shown in Fig. 1
Kraftstoffeinspritzvorrichtung über die Zeitachse den Hub (H) des Ventilkδrpers des 4/3-Steuerventils, den Einspritzdruck (P) und den Hub (h) des Ventilglieds des Einspritzventils angibt.Fuel injector on the time axis indicates 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.
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 Pl gelagert ist. Vom Hochdruckspeicher 2 wird der Kraftstoff jeweils über Druckleitungen 3 und Einspritzleitungen 4 zu den einzelnen, in den Brennraum der zu versor- genden Brennkraftmaschine ragenden Einspritzventilen (Injektoren) 5 abgeführt, von denen in Fig. 1 nur eines gezeigt ist .The fuel injection device 1 for internal combustion engines shown in FIG. 1 comprises a high-pressure accumulator 2 (common rail) in which fuel is stored at a fuel pressure Pl. The fuel is discharged from the high-pressure accumulator 2 via pressure lines 3 and injection lines 4 to the individual injection valves (injectors) 5 projecting into the combustion chamber of the internal combustion engine to be supplied, only one of which is shown in FIG. 1.
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 Führungs- bohrung 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 Einspritzlei- tung 4 verbunden sowie über eine A-Drossel 17 und einA piston-shaped valve member (nozzle needle) 7 with a conical valve sealing surface 8 is displaceably mounted in an axial guide bore 6 of the injection valve 5, which is pressed by a closing spring 9 against a conical valve seat surface 10 of the valve housing and closes the injection openings 11 provided there. The injection line 4 opens in the injection valve 5 into an annular nozzle chamber 12, from which an annular gap extending between the guide bore 6 and the valve member 7 extends up to Valve seat surface 10 leads. In the region of the nozzle chamber 12, the valve member 7 has a first control surface 13 designed as a pressure shoulder, on which the fuel supplied via the injection line 4 acts on the valve member 7 in the opening direction (ie inwards). The end face of the valve member 7 facing away from the valve sealing surface 8 forms a second control surface 14 which delimits a control chamber 15 and acts in the valve closing direction. The control chamber 15 is connected to the injection line 4 via a Z throttle 16 and via an A throttle 17 and a
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.Slider valve 18 can be connected to a relief line (leak oil) 19. 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 in the control chamber 15, the valve member 7 closes the injection openings 11. The inlet throttle 16 is smaller than the A-throttle '17 so that degrades opened slide valve 18 of 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 pressure against the effect of the closing spring 9 is turned on.
Für jedes Einspritzventil 5 ist eine lokale Drucküberset- zungseinheit 20 mit einem gegen die Wirkung einer Rückstellfeder 21 axial verschiebbaren Übersetzungskolben 22 vorgesehen, welcher primärseitig eine Primärkammer 23, se- kundärseitig 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 Pl des Druckspei- chers 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 Kol- benquerschnittsverhältnis 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 transmission unit 20 is provided with a transmission piston 22 which is axially displaceable against the action of a return spring 21 and which delimits a primary chamber 23 on the primary side, a secondary chamber 24 on the secondary side and a pressure chamber 25 on the pressure side. 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, the injection line 4 from the Pressure chamber 25 goes off. The secondary chamber 24 can be connected to the relief line 19 via a seat valve 28. When the switching valve 28 is closed, the fuel pressure P 1 of the pressure accumulator 2 prevails in all three chambers 23, 24, 25, so that the translation piston 22 is pressed into its starting position by the return spring 21. If the secondary chamber 24 is relieved of pressure by opening the seat valve 28, the transmission piston 22 is displaced in the compression direction and the fuel in the pressure chamber 25 is compressed to a higher fuel pressure in accordance with the piston cross-sectional ratio in the primary and pressure chambers 23, 25. The check valve 27 prevents the backflow 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 gela- gert 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 lower annular space 33, which is provided in the wall of the guide bore 29 and into which the line leading from the control space 15 opens. On the output side, the slide valve 18 has a lower annular space 34, which is provided on the valve body 30 and opens towards the annular space 33. 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 relief line 19 leading from the guide bore 29 on the end face. The slide valve 18 blocks when at a stroke H 2 of the valve body 30, the control edge 37 of the annular space 34 passes over the upper sealing edge 38 of the annular space 33.
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 zu- sammenwirkende konische Ventildichtfläche 41, die sich nach unten zu einem Ringraum 42 erweitert, von dem die Entlastungsleitung 19 abgeht.On the inlet side, the seat valve 28 has an upper annular space 39 provided in the wall of the guide bore 29 with a conical valve seat surface 40, into which the line leading from the secondary chamber 24 opens. The valve body 30 has a conical valve sealing surface 41 which interacts with the valve seat surface 40 and widens downward to form an annular space 42 from which the relief line 19 branches off.
In der in Fig. 1 gezeigten Ausgangsstellung des 4/3-Steu- erventils 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 Hj. 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 open, so that the control chamber 15 is relieved of pressure, and the seat valve 28 is closed, so that the secondary chamber 24 is not relieved of pressure. The stroke Hj required to open the seat valve 28 . of the valve body 30 is smaller than the stroke H 2 required to close the slide valve 18.
In Fig. 2 ist in einem Diagramm der zeitliche Ablauf desIn Fig. 2 is the timing of the
Einspritzvorgangs aufgetragen.Injection process applied.
Der Beginn des Einspritzvorgangs wird zum Zeitpunkt tO durch einen Hub Hx 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 tl 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 Pmaχ 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 .The start of the injection process is initiated at time t0 by a stroke H x of the valve body 30, so that the seat valve 28 opens and the slide valve 18 remains open. The secondary chamber 24 is relieved of pressure, and a higher fuel pressure builds up in the pressure chamber 25 and thus also in the nozzle chamber 12. If the opening pressure P s is reached in the nozzle chamber 12 at the time t1, the valve member 7 opens against the action of the closing spring 9 and is controlled to maximum Stroke h max controlled so that the injection takes place with the fuel pressure prevailing in the nozzle chamber 12. The maximum injection pressure P ma χ results from the piston cross-sectional ratio in the primary and pressure chamber 23, 25. At time t2, at which the pressure prevailing in the nozzle chamber 12 is still higher than the opening pressure P s , a stroke H 2 of the valve body 30 the slide valve 18 closed. 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.
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 Pma / 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. At time t3, the valve body 30 is opened and the seat valve 28 is closed by returning the valve body 30 to its starting position. The control chamber 15 is again relieved of pressure and the valve member 7 opens in a stroke-controlled manner so that post-injection takes place with the fuel pressure prevailing in the injection chamber 12, for example with Pm a /. The injection process ends at time t4 when the fuel pressure prevailing in the nozzle chamber 12 becomes lower than the opening pressure P s . Because the secondary chamber 24 is no longer relieved of pressure, the transmission piston 22 is pressed into its starting position by the return spring 21 and the pressure chamber 25 is filled with fuel from the pressure accumulator 2.

Claims

Patentansprüche claims
1. Kraftstoffeinspritzvorrichtung (1) für Brennkraftma- schinen, mit mehreren jeweils in einer Einspritzleitung (4) des Kraftstoffs vorgesehenen Einspritzventilen (5), wobei jedes Einspritzventil (5) einen Düsenraum (12) und einen Steuerraum (15), die beide mit der Einspritzleitung (4) verbunden sind, ein die Einspritzöffnungen (11) des Düsenraums (12) steuerndes Ventilglied (7) , das über eine im Düsenraum (12) befindliche, in Ventilöffnungsrichtung wirkende erste Steuerfläche (13) und über eine im Steuerraum (15) befindliche, in Ventilschließrichtung wirkende zweite Steuerfläche (14) betätigbar ist, ein erstes1. Fuel injection device (1) for internal combustion engines, with a plurality of injection valves (5) each provided in an injection line (4) of the fuel, each injection valve (5) having a nozzle chamber (12) and a control chamber (15), both with the Injection line (4) are connected, a valve member (7) controlling the injection openings (11) of the nozzle chamber (12), which has a first control surface (13) located in the nozzle chamber (12) and acting in the valve opening direction and via a in the control chamber (15) located in the valve closing direction acting second control surface (14) can be actuated, a first
Ventil (18) zum Steuern des im Steuerraum (15) herrschenden Drucks und ein zweites Ventil (28) zum Schalten des Einspritzdruckes aufweist, dadurch gekennzeichnet, daß für beide Ventile (18, 28) ein gemeinsamer Ventilkörper (30) vorgesehen ist und daß der zum Schließen des ersten Ventils (18) erforderliche Hub (H2) des Ventilkörpers (30) größer als der zum Öffnen des zweiten Ventils (18) erforderliche Hub (Hx) ist.Has valve (18) for controlling the pressure prevailing in the control chamber (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 that stroke (H 2 ) of the valve body (30) required to close the first valve (18) is greater than the stroke (H x ) required to open the second valve (18).
2. Kraftstoffeinspritzvorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß das erste Ventil (18) als Schieberventil ausgebildet ist.2. Fuel injection device according to claim 1, characterized in that the first valve (18) is designed as a slide valve.
3. Kraftstoffeinspritzvorrichtung nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß das zweite Ventil (28) als Sitzventil ausgebildet ist.3. Fuel injection device according to claim 1 or 2, characterized in that the second valve (28) is designed as a seat valve.
4. Kraftstoffeinspritzvorrichtung nach einem der vor- hergehenden Ansprüche, dadurch gekennzeichnet, daß der für den Ventilkörper (30) vorgesehene Stellantrieb als piezoelektrischer Stellantrieb (32) ausgebildet ist .4. Fuel injection device according to one of the preceding claims, characterized in that the actuator provided for the valve body (30) is designed as a piezoelectric actuator (32).
5. Kraftstoffeinspritzvorrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß zumindest ein tieferer Kraftstoffdruck (Pl) in einem zentralen Druckspeicher (2) gespeichert ist.5. Fuel injection device according to one of the preceding claims, characterized in that at least a lower fuel pressure (Pl) is stored in a central pressure accumulator (2).
6. Kraftstoffeinspritzvorrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Einspritzleitung (4) sowohl über ein Rückschlagventil (27) mit einem tieferen Kraftstoffdruck (Pl) als auch mit der Druckkammer (25) eines durch das zweite Ventil (28) aktivierbaren Druckübersetzungs- kolbens (22) verbunden ist.- 6. Fuel injection device according to one of the preceding claims, characterized in that the injection line (4) both via a check valve (27) with a lower fuel pressure (Pl) and with the pressure chamber (25) of a pressure transmission which can be activated by the second valve (28) - piston (22) is connected.
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

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

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EP (1) EP1421272B1 (en)
JP (1) JP4204467B2 (en)
DE (2) DE10141110A1 (en)
ES (1) ES2244798T3 (en)
WO (1) WO2003018995A1 (en)

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DE10315016A1 (en) * 2003-04-02 2004-10-28 Robert Bosch Gmbh Fuel injector with a leak-free servo valve
DE602005002758T2 (en) 2004-01-13 2008-07-24 Delphi Technologies, Inc., Troy Fuel injection valve
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

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JP2005500472A (en) 2005-01-06
US6871636B2 (en) 2005-03-29
EP1421272B1 (en) 2005-06-29
JP4204467B2 (en) 2009-01-07
DE50203522D1 (en) 2005-08-04
DE10141110A1 (en) 2003-03-20
WO2003018995A1 (en) 2003-03-06
ES2244798T3 (en) 2005-12-16
US20040055573A1 (en) 2004-03-25

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