EP1576276A1 - Fuel injection device comprising a 3/3-way control valve for forming the injection process - Google Patents

Fuel injection device comprising a 3/3-way control valve for forming the injection process

Info

Publication number
EP1576276A1
EP1576276A1 EP03812121A EP03812121A EP1576276A1 EP 1576276 A1 EP1576276 A1 EP 1576276A1 EP 03812121 A EP03812121 A EP 03812121A EP 03812121 A EP03812121 A EP 03812121A EP 1576276 A1 EP1576276 A1 EP 1576276A1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure side
low
fuel injection
connection
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Withdrawn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
EP03812121A
Other languages
German (de)
French (fr)
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 EP1576276A1 publication Critical patent/EP1576276A1/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Withdrawn legal-status Critical Current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
    • 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
    • F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
    • F02M63/0036—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat with spherical or partly spherical shaped valve member ends
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—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
    • F02M63/0045—Three-way valves

Definitions

  • the invention is based on a fuel injection device according to the preamble of claim 1.
  • a fuel injection device for example, known from DE 100 39 215 A1
  • the nozzle needle of a fuel injection valve is opened or dependent on the pressure prevailing in a control chamber closed.
  • the control chamber which is permanently connected to the high-pressure side, can be connected to the low-pressure side by means of a 2/2-way control valve designed as a double-seat valve and can thus be relieved of pressure.
  • injection course shaping is not possible with this fuel injection device.
  • the fuel injection device according to the invention with the characterizing features of claim dem has the advantage that the pressure prevailing in the control chamber in the two open valve positions of the control valve is reduced at different speeds and therefore an injection curve can be carried out.
  • FIG. 1 shows the fuel injection device according to the invention with a double seat valve controlling the pressure in a control chamber in its lower valve position
  • FIG. 2 shows the double seat valve of FIG. 1 in its middle valve position
  • Fig. 3 shows the double seat valve of Figure 1 in its upper valve position.
  • Fig. 4 shows another embodiment of the invention
  • Fuel injection device with a differently designed double seat valve in a representation analogous to FIG. 1.
  • the fuel injection device 1 according to the invention shown in FIG. 1 is usually used in an internal combustion engine with a plurality of cylinders, with each of these cylinders being assigned a fuel injection valve (injector).
  • This injector has, in a manner known per se, an injector nozzle, not shown here, which projects into a cylinder combustion chamber of the internal combustion engine, and an injector needle 3 which opens and closes the injector depending on the pressure in a control chamber 2 and is only indicated to a small extent here.
  • the control room 2 is permanently connected to a high-pressure inlet line (high-pressure side) 5 via an inlet throttle 4.
  • a 3/3-way control valve 6 in the form of a double-seat valve is provided, which opens or blocks the connection of the control chamber 2 with a low-pressure drain line (low-pressure side) 7.
  • the high-pressure inlet line 5 can be connected to a high-pressure reservoir (common rail), not shown, and the low-pressure outlet line 7 can be connected to leakage oil.
  • the control valve 6 has a high-pressure side valve connection 8, which is connected to the control chamber 2, and two low-pressure side valve connections 9, 10, which are each connected to the low-pressure discharge line 7 via an outlet throttle 11, 12.
  • the control valve 6 has a valve body 13 designed as a valve ball, which is axially adjustable in a valve chamber 14 between two coaxial annular valve seats 15, 16 by means of a piezoelectric actuator 17 against the action of a closing spring 18.
  • the valve chamber 14 is connected via the valve opening of the lower valve seat 15 in FIG. 1 to the high-pressure valve connection 8 and via the valve opening of the upper valve seat 16 to the first low-pressure valve connection 9.
  • the second low-pressure valve connection 10 is permanently connected to the valve chamber 14 connected.
  • the valve body 13 can be moved into an upper, middle or lower valve position by means of the actuator 17.
  • valve opening of the lower valve seat 15 is closed by the valve body 13 and the valve opening of the upper valve seat 16 is opened, so that the connection of the control chamber 2 to the low-pressure drain line 7 is blocked.
  • the high pressure prevailing in the control chamber 2 acts on a control surface 19 of the nozzle needle 3 acting in the closing direction of the nozzle needle 3, so that the nozzle needle 3 or the fuel injection valve are closed.
  • valve body 13 In the middle valve position shown in FIG. 2, the valve body 13 is located between the two valve seats 15, 16, so that the valve openings of the two valve seats 15, 16 are open.
  • the high-pressure valve connection 8 is now connected to both low-pressure valve connections 9, 10, so that the
  • Control room 2 is connected to the low-pressure discharge line 7 via both discharge throttles 11, 12. As a result, the pressure prevailing in the control chamber 2 is reduced and the nozzle needle 3 or the fuel injection valve open.
  • the pressure reduction rate is determined by the two parallel discharge throttle 11, 12. If the first outlet throttle 11 has a significantly smaller throttle resistance than the second outlet throttle 12, the pressure reduction rate is approximately determined by the first outlet throttle 11.
  • valve body 13 closes the valve opening of the upper valve seat 16.
  • the high-pressure side valve connection 8 is only connected to the second low-pressure side valve connection 10, so that the control chamber 2 is connected to the low-pressure valve only via the second outlet throttle 12. Drain line 7 is connected.
  • the pressure reduction rate is determined by the second outlet throttle 12.
  • valve body 113 of the control valve 106 is designed as a valve piston and is guided axially displaceably in a guide bore 120.
  • the valve body 113 has a lower and an upper conical valve sealing surface 121, 122 which cooperate with the two conical valve seats 115, 116.
  • the valve chamber 114 provided between the two valve seats 115, 116 is connected via the valve opening of the lower valve seat 115 in FIG. 4 to a lower annular space 123 of the guide bore 120 and via the valve opening of the upper valve seat 116 to an upper annular space 124 of the guide bore 120, the two annular spaces 123, 124 are formed by annular grooves of the valve body 113.
  • the high-pressure side valve connection 108 opens into the lower annular space 123, and the first low-pressure side valve connection 109 extends from the upper annular space 124.
  • the second low-pressure side valve connection 110 extends from the valve chamber 114.
  • the first low-pressure side valve connection 109 is connected to the low-pressure discharge line 107 via the first discharge throttle 111 and the second low-pressure side valve connection 110 is connected via the first discharge throttle 112.
  • Leakage oil line 125 in order to discharge the leakage oil present between valve body 113 and guide bore 120.
  • the first valve connection 108 is connected to both low-pressure side valve connections 109, 110, so that the pressure prevailing in the control chamber 102 is reduced via the two flow restrictors 111, 112 and that Open nozzle needle 103 or the fuel injection valve.
  • the high-pressure-side valve connection 108 is only connected to the second low-pressure-side valve connection 110, so that the pressure prevailing in the control chamber 102 is reduced only via the second outlet throttle 1 12 and the nozzle needle 3 or the fuel injection valve open.
  • a suitable injection course shaping by means of the control valve 106 can be set by a suitable combination of the two outlet throttles 11 1, 112 and the inlet throttle 104.

Abstract

Disclosed is a fuel injection device (1) for internal combustion engines, comprising a control chamber (2) that is connected to a high-pressure end (5), and a control valve (6) which is connected to said control chamber (2) by means of a valve connection (8) located at a low-pressure end while being connected to a low-pressure end (7) by means of a first valve connection (9) located at a low-pressure end via a first discharge throttle (11). A second valve connection (10) of the control valve (6), which is located at a low-pressure end, is connected to the low-pressure end (7) via a second discharge throttle (12). The connection between the valve connection (8) located at a high-pressure end and the low-pressure end (7) is blocked in a first valve position while said valve connection (8) located at a high-pressure end is connected to both valve connections (9, 10) located at a low-pressure end in a second valve position and is connected to one of the two valve connections (9, 10) located at a low-pressure end in a third valve position.

Description

Kraftstoffeinspritzvorrichtung mit einem 3/3-Weqe-Steuerventil zur EinspritzverlaufsformunqFuel injection device with a 3/3-way control valve for injection course shaping
Stand der TechnikState of the art
Die Erfindung geht aus von einer Kraftstoffeinspritzvorrichtung nach der Gattung des Patentanspruchs 1. Bei solch einer z.B. durch die DE 100 39 215 A1 bekannten Kraftstoffeinspritzvorrichtung wird die Düsennadel eines Kraftstoffeinspritzventils abhängig von dem in einem Steuerraum herrschenden Druck geöffnet oder geschlossen. Der permanent an die Hochdruckseite angeschlossene Steuerraum kann mittels eines als Doppelsitzventil ausgebildeten 2/2-Wege-Steuerventils mit der Niederdruckseite verbunden und dadurch druckentlastet werden. Bei dieser Kraftstoffeinspritzvorrichtung ist eine Einspritzverlaufsformung allerdings nicht möglich.The invention is based on a fuel injection device according to the preamble of claim 1. In such a fuel injection device, for example, known from DE 100 39 215 A1, the nozzle needle of a fuel injection valve is opened or dependent on the pressure prevailing in a control chamber closed. The control chamber, which is permanently connected to the high-pressure side, can be connected to the low-pressure side by means of a 2/2-way control valve designed as a double-seat valve and can thus be relieved of pressure. However, injection course shaping is not possible with this fuel injection device.
Vorteile der ErfindungAdvantages of the invention
Die erfindungsgemäße Kraftstoffeinspritzvorrichtung mit den kennzeichnenden Merkmalen des Patentanspruchs Λ hat demgegenüber den Vorteil, dass der im Steuerraum herrschende Druck in den beiden offenen Ventilpositionen des Steuerventils unterschiedlich schnell abgebaut wird und daher eine Einspritzverlaufsformung durchgeführt werden kann.The fuel injection device according to the invention with the characterizing features of claim dem has the advantage that the pressure prevailing in the control chamber in the two open valve positions of the control valve is reduced at different speeds and therefore an injection curve can be carried out.
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
Zwei bevorzugte Ausführungsbeispiele der erfindungsgemäßen Kraftstoffeinspritzvorrichtung mit einem als Doppelsitzventil ausgestalteten 3/3- Wege-Steuerventil sind in der Zeichnung schematisch dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen:Two preferred exemplary embodiments of the fuel injection device according to the invention with a 3/3-way control valve designed as a double seat valve are shown schematically in the drawing and explained in more detail in the description below. Show it:
Fig. 1 die erfindungsgemäße Kraftstoffeinspritzvorrichtung mit einem den Druck in einem Steuerraum steuernden Doppelsitzventil in seiner unteren Ventilposition;1 shows the fuel injection device according to the invention with a double seat valve controlling the pressure in a control chamber in its lower valve position;
Fig. 2 das Doppelsitzventil der Fig. 1 in seiner mittleren Ventilposition;FIG. 2 shows the double seat valve of FIG. 1 in its middle valve position;
Fig. 3 das Doppelsitzventil der Fig. 1 in seiner oberen Ventilposition; Fig. 4 eine weitere Ausführungsform der erfindungsgemäßenFig. 3 shows the double seat valve of Figure 1 in its upper valve position. Fig. 4 shows another embodiment of the invention
Kraftstoffeinspritzvorrichtung mit einem anders ausgebildeten Doppelsitzventil in einer Darstellung analog zu Fig. 1.Fuel injection device with a differently designed double seat valve in a representation analogous to FIG. 1.
Beschreibung der AusführungsbeispieleDescription of the embodiments
Die in Fig. 1 gezeigte erfindungsgemäße Kraftstoffeinspritzvorrichtung 1 wird üblicherweise bei einer Brennkraftmaschine mit mehreren Zylindern verwendet, wobei jedem dieser Zylinder ein Kraftstoffeinspritzventil (Injektor) zugeordnet ist.The fuel injection device 1 according to the invention shown in FIG. 1 is usually used in an internal combustion engine with a plurality of cylinders, with each of these cylinders being assigned a fuel injection valve (injector).
Dieser Injektor weist in an sich bekannter Weise eine in einen Zylinderbrennraum der Brennkraftmaschine ragende, hier nicht näher dargestellte Einspritzdüse sowie eine die Einspritzdüse abhängig vom Druck in einem Steuerraum 2 öffnende und schließende, hier nur zu einem kleinen Teil angedeutete Düsennadel 3 auf.This injector has, in a manner known per se, an injector nozzle, not shown here, which projects into a cylinder combustion chamber of the internal combustion engine, and an injector needle 3 which opens and closes the injector depending on the pressure in a control chamber 2 and is only indicated to a small extent here.
Der Steuerraum 2 ist über eine Zulaufdrossel 4 dauerhaft an eine Hochdruck- Zulaufleitung (Hochdruckseite) 5 angeschlossen. Zum Steuern des Einspritzvorgangs ist ein 3/3-Wege-Steuerventil 6 in Form eines Doppelsitzventils vorgesehen, das die Verbindung des Steuerraums 2 mit einer Niederdruck- Ablaufleitung (Niederdruckseite) 7 öffnet oder sperrt. Die Hochdruck-Zulaufleitung 5 kann mit einem nicht gezeigten Hochdruckspeicher (Common Rail) und die Niederdruck-Ablaufleitung 7 mit Lecköl verbunden sein.The control room 2 is permanently connected to a high-pressure inlet line (high-pressure side) 5 via an inlet throttle 4. To control the injection process, a 3/3-way control valve 6 in the form of a double-seat valve is provided, which opens or blocks the connection of the control chamber 2 with a low-pressure drain line (low-pressure side) 7. The high-pressure inlet line 5 can be connected to a high-pressure reservoir (common rail), not shown, and the low-pressure outlet line 7 can be connected to leakage oil.
Das Steuerventil 6 hat einen hochdruckseitigen Ventilanschluss 8, der mit dem Steuerraum 2 verbunden ist, und zwei niederdruckseitige Ventilanschlüsse 9, 10, die mit der Niederdruck-Ablaufleitung 7 jeweils über eine Ablaufdrossel 11 , 12 verbunden sind. Das Steuerventil 6 hat einen als Ventilkugel ausgebildeten Ventilkörper 13, der in einer Ventilkammer 14 zwischen zwei koaxialen ringförmigen Ventilsitzen 15, 16 mittels eines piezoelektrischen Stellantriebs 17 gegen die Wirkung einer Schließfeder 18 axial verstellbar ist. Die Ventilkammer 14 ist über die Ventilöffnung des in Fig. 1 unteren Ventilsitzes 15 mit dem hochdruckseitigen Ventilanschluss 8 und über die Ventilöffnung des oberen Ventilsitzes 16 mit dem ersten niederdruckseitigen Ventilanschluss 9 verbunden. Der zweite niederdruckseitige Ventilanschluss 10 ist dauerhaft an die Ventilkammer 14 angeschlossen. Mittels des Stellantriebs 17 kann der Ventilkörper 13 in eine obere, mittlere oder untere Ventilposition verschoben werden.The control valve 6 has a high-pressure side valve connection 8, which is connected to the control chamber 2, and two low-pressure side valve connections 9, 10, which are each connected to the low-pressure discharge line 7 via an outlet throttle 11, 12. The control valve 6 has a valve body 13 designed as a valve ball, which is axially adjustable in a valve chamber 14 between two coaxial annular valve seats 15, 16 by means of a piezoelectric actuator 17 against the action of a closing spring 18. The valve chamber 14 is connected via the valve opening of the lower valve seat 15 in FIG. 1 to the high-pressure valve connection 8 and via the valve opening of the upper valve seat 16 to the first low-pressure valve connection 9. The second low-pressure valve connection 10 is permanently connected to the valve chamber 14 connected. The valve body 13 can be moved into an upper, middle or lower valve position by means of the actuator 17.
In der in Fig. 1 gezeigten unteren Ventilposition des Ventilkörpers 13 ist die Ventilöffnung des unteren Ventilsitzes 15 durch den Ventilkörper 13 verschlossen und die Ventilöffnung des oberen Ventilsitzes 16 geöffnet, so dass die Verbindung des Steuerraums 2 zur Niederdruck-Ablaufleitung 7 gesperrt ist. Der im Steuerraum 2 herrschende Hochdruck greift an einer in Schließrichtung der Düsennadel 3 wirkenden Steuerfläche 19 der Düsennadel 3 an, so dass die Düsennadel 3 bzw. das Kraftstoffeinspritzventil geschlossen sind.In the lower valve position of the valve body 13 shown in FIG. 1, the valve opening of the lower valve seat 15 is closed by the valve body 13 and the valve opening of the upper valve seat 16 is opened, so that the connection of the control chamber 2 to the low-pressure drain line 7 is blocked. The high pressure prevailing in the control chamber 2 acts on a control surface 19 of the nozzle needle 3 acting in the closing direction of the nozzle needle 3, so that the nozzle needle 3 or the fuel injection valve are closed.
In der in Fig. 2 gezeigten mittleren Ventilposition befindet sich der Ventilkörper 13 zwischen beiden Ventilsitzen 15, 16, so dass die Ventilöffnungen der beiden Ventilsitze 15, 16 geöffnet sind. Der hochdruckseitige Ventilanschluss 8 ist nunmehr mit beiden niederdruckseitigen Ventilanschlüssen 9, 10 verbunden, so dass derIn the middle valve position shown in FIG. 2, the valve body 13 is located between the two valve seats 15, 16, so that the valve openings of the two valve seats 15, 16 are open. The high-pressure valve connection 8 is now connected to both low-pressure valve connections 9, 10, so that the
Steuerraum 2 über beide Ablaufdrosseln 11 , 12 mit der Niederdruck-Ablaufleitung 7 verbunden ist. Dadurch wird der im Steuerraum 2 herrschende Druck abgesenkt, und die Düsennadel 3 bzw. das Kraftstoffeinspritzventil öffnen. Die Druckabbaugeschwindigkeit ist durch die beiden parallelen Ablaufdrossel 11 , 12 bestimmt. Wenn die erste Ablaufdrossel 11 einen deutlich kleineren Drosselwiderstand als die zweite Ablaufdrossel 12 aufweist, ist die Druckabbaugeschwindigkeit näherungsweise durch die erste Ablaufdrossel 11 bestimmt.Control room 2 is connected to the low-pressure discharge line 7 via both discharge throttles 11, 12. As a result, the pressure prevailing in the control chamber 2 is reduced and the nozzle needle 3 or the fuel injection valve open. The pressure reduction rate is determined by the two parallel discharge throttle 11, 12. If the first outlet throttle 11 has a significantly smaller throttle resistance than the second outlet throttle 12, the pressure reduction rate is approximately determined by the first outlet throttle 11.
In seiner in Fig. 3 gezeigten oberen Ventilposition verschließt der Ventilkörpers 13 die Ventilöffnung des oberen Ventilsitzes 16. Der hochdruckseitige Ventilanschluss 8 ist nur noch mit dem zweiten niederdruckseitigen Ventilanschluss 10 verbunden, so dass der Steuerraum 2 nur über die zweite Ablaufdrossel 12 mit der Niederdruck- Ablaufleitung 7 verbunden ist. Dadurch wird der im Steuerraum 2 herrschende Druck abgesenkt, und die Düsennadel 3 bzw. das Kraftstoffeinspritzventil öffnen. Die Druckabbaugeschwindigkeit ist durch die zweite Ablaufdrossel 12 bestimmt.In its upper valve position shown in FIG. 3, the valve body 13 closes the valve opening of the upper valve seat 16. The high-pressure side valve connection 8 is only connected to the second low-pressure side valve connection 10, so that the control chamber 2 is connected to the low-pressure valve only via the second outlet throttle 12. Drain line 7 is connected. As a result, the pressure prevailing in the control chamber 2 is reduced and the nozzle needle 3 or the fuel injection valve open. The pressure reduction rate is determined by the second outlet throttle 12.
Da der im Steuerraum 2 herrschende Druck in der mittleren und der oberen Ventilposition des Ventilkörpers 13 unterschiedlich schnell abgebaut wird, kann durch geeignete Kombination der beiden Ablaufdrosseln 11 , 12 und der Zulaufdrossel 4 eine gewünschte Einspritzverlaufsformung mittels des Steuerventils 6 eingestellt werden.Since the pressure prevailing in the control chamber 2 in the middle and the upper valve position of the valve body 13 is reduced at different speeds, can by suitable combination of the two outlet throttles 11, 12 and the inlet throttle 4, a desired injection curve shaping can be set by means of the control valve 6.
Bei der in Fig. 4 gezeigten Kraftstoffeinspritzvorrichtung 101 ist der Ventilkörper 113 des Steuerventils 106 als Ventilkolben ausgebildet und in einer Führungsbohrung 120 axial verschiebbar geführt. Der Ventilkörper 113 hat eine untere und eine obere konische Ventildichtfläche 121 , 122, die mit den beiden konischen Ventilsitzen 115, 116 zusammenwirken. Die zwischen beiden Ventilsitzen 115, 116 vorgesehene Ventiikammer 114 ist über die Ventilöffnung des in Fig. 4 unteren Ventilsitzes 115 mit einem unteren Ringraum 123 der Führungsbohrung 120 und über die Ventilöffnung des oberen Ventilsitzes 116 mit einem oberen Ringraum 124 der Führungsbohrung 120 verbunden, wobei die beiden Ringräume 123, 124 durch Ringnuten des Ventilkörpers 113 gebildet sind. Der hochdruckseitige Ventilanschluss 108 mündet in den unteren Ringraum 123, und der erste niederdruckseitige Ventilanschluss 109 geht vom oberen Ringraum 124 ab. Der zweite niederdruckseitige Ventilanschluss 110 geht von der Ventilkammer 114 ab. Mit der Niederdruck-Ablaufleitung 107 ist der erste niederdruckseitige Ventilanschluss 109 über die erste Ablaufdrossel 111 und der zweite niederdruckseitige Ventilanschluss 110 über die erste Ablaufdrossel 112 verbunden. Am unteren Ende der Führungsbohrung 120 geht noch eineIn the fuel injection device 101 shown in FIG. 4, the valve body 113 of the control valve 106 is designed as a valve piston and is guided axially displaceably in a guide bore 120. The valve body 113 has a lower and an upper conical valve sealing surface 121, 122 which cooperate with the two conical valve seats 115, 116. The valve chamber 114 provided between the two valve seats 115, 116 is connected via the valve opening of the lower valve seat 115 in FIG. 4 to a lower annular space 123 of the guide bore 120 and via the valve opening of the upper valve seat 116 to an upper annular space 124 of the guide bore 120, the two annular spaces 123, 124 are formed by annular grooves of the valve body 113. The high-pressure side valve connection 108 opens into the lower annular space 123, and the first low-pressure side valve connection 109 extends from the upper annular space 124. The second low-pressure side valve connection 110 extends from the valve chamber 114. The first low-pressure side valve connection 109 is connected to the low-pressure discharge line 107 via the first discharge throttle 111 and the second low-pressure side valve connection 110 is connected via the first discharge throttle 112. At the lower end of the guide bore 120 there is another
Leckölleitung 125 ab, um das zwischen Ventilkörper 113 und Führungsbohrung 120 vorhandene Lecköl abzuführen.Leakage oil line 125 in order to discharge the leakage oil present between valve body 113 and guide bore 120.
In der in Fig. 4 gezeigten unteren Ventilposition des Ventilkörpers 113 ist die Verbindung des über die Zulaufdrossel 104 an die Hochdruck-Zulaufleitung 105 angeschlossenen Steuerraums 102 zur Niederdruck-Ablaufleitung 107 gesperrt. Der im Steuerraum 102 herrschende Hochdruck greift an der in Schließrichtung der Düsennadel 103 wirkenden Steuerfläche 119 der Düsennadel 103 an, so dass die Düsennadel 103 bzw. das Kraftstoffeinspritzventil geschlossen sind. In der mittleren Ventilposition (nicht gezeigt) des Ventiikörpers 113 zwischen beiden Ventilsitzen 115, 116 ist der erste Ventilanschluss 108 mit beiden niederdruckseitigen Ventilanschlüssen 109, 110 verbunden, so dass der im Steuerraum 102 herrschende Druck über die beiden Ablaufdrosseln 111 , 112 abgesenkt wird und die Düsennadel 103 bzw. das Kraftstoffeinspritzventil öffnen. In der oberen Ventilposition (nicht gezeigt) des Ventilkörpers 13 ist der hochdruckseitige Ventilanschluss 108 nur mit dem zweiten niederdruckseitigen Ventilanschluss 110 verbunden, so dass der im Steuerraum 102 herrschende Druck nur über die zweite Ablaufdrossel 1 12 abgesenkt wird und die Düsennadel 3 bzw. das Kraftstoffeinspritzventil öffnen.In the lower valve position of the valve body 113 shown in FIG. 4, the connection of the control chamber 102 connected to the high-pressure inlet line 105 via the inlet throttle 104 to the low-pressure outlet line 107 is blocked. The high pressure prevailing in the control chamber 102 acts on the control surface 119 of the nozzle needle 103 acting in the closing direction of the nozzle needle 103, so that the nozzle needle 103 and the fuel injection valve are closed. In the central valve position (not shown) of the valve body 113 between the two valve seats 115, 116, the first valve connection 108 is connected to both low-pressure side valve connections 109, 110, so that the pressure prevailing in the control chamber 102 is reduced via the two flow restrictors 111, 112 and that Open nozzle needle 103 or the fuel injection valve. In the upper valve position (not shown) of the valve body 13, the high-pressure-side valve connection 108 is only connected to the second low-pressure-side valve connection 110, so that the pressure prevailing in the control chamber 102 is reduced only via the second outlet throttle 1 12 and the nozzle needle 3 or the fuel injection valve open.
Da der im Steuerraum 102 herrschende Druck in der mittleren und der oberen Ventilposition des Ventilkörpers 113 unterschiedlich schnell abgebaut wird, kann durch geeignete Kombination der beiden Ablaufdrosseln 11 1 , 112 und der Zulaufdrossel 104 eine gewünschte Einspritzverlaufsformung mittels des Steuerventils 106 eingestellt werden. Since the pressure prevailing in the control chamber 102 is reduced at different speeds in the middle and the upper valve position of the valve body 113, a suitable injection course shaping by means of the control valve 106 can be set by a suitable combination of the two outlet throttles 11 1, 112 and the inlet throttle 104.

Claims

Patentansprüche claims
1. Kraftstoffeinspritzvorrichtung (1 ; 101) für Brennkraftmaschinen, mit einem an eine Hochdruckseite (5; 105) angeschlossenen Steuerraum (2; 102) und mit einem Steuerventil (6; 106), das mit einem hochdruckseitigen1. Fuel injection device (1; 101) for internal combustion engines, with a control chamber (2; 102) connected to a high-pressure side (5; 105) and with a control valve (6; 106) connected to a high-pressure side
Ventilanschluss (8; 108) mit dem Steuerraum (2; 102) und mit einem ersten niederdruckseitigen Ventilanschluss (9; 109) über eine erste Ablaufdrossel (11 ; 111 ) mit einer Niederdruckseite (7; 107) verbunden ist, dadurch gekennzeichnet, dass ein zweiter niederdruckseitiger Ventilanschluss (10; 110) desValve connection (8; 108) with the control chamber (2; 102) and with a first low-pressure valve connection (9; 109) via a first outlet throttle (11; 111) with a low-pressure side (7; 107), characterized in that a second low pressure side valve connection (10; 110) of the
Steuerventils (6; 106) über eine zweite Ablaufdrossel (12; 112) mit der Niederdruckseite (7; 107) verbunden ist und dass in einer ersten Ventilposition die Verbindung des hochdruckseitigen Ventilanschlusses (8; 108) zur Niederdruckseite (7; 107) gesperrt ist, in einer zweiten Ventilposition der hochdruckseitige Ventilanschluss (8; 108) mit beiden niederdruckseitigen Ventilanschlüssen (9, 10; 109, 110) verbunden ist und in einer dritten Ventilposition der hochdruckseitige Ventilanschluss (8; 108) mit einem der beiden niederdruckseitigen Ventilanschlüsse (9, 10; 109, 110) verbunden ist.Control valve (6; 106) is connected to the low-pressure side (7; 107) via a second discharge throttle (12; 112) and that the connection of the high-pressure side valve connection (8; 108) to the low-pressure side (7; 107) is blocked in a first valve position , in a second valve position the high pressure side valve connection (8; 108) is connected to both low pressure side valve connections (9, 10; 109, 110) and in a third valve position the high pressure side valve connection (8; 108) is connected to one of the two low pressure side valve connections (9, 10; 109, 110) is connected.
2. Kraftstoffeinspritzvorrichtung nach Anspruch 1 , dadurch gekennzeichnet, dass die zweite Ablaufdrossel (12; 112) einen höherem Drosselwiderstand als die erste Ablaufdrossel (11 ; 111) aufweist.2. Fuel injection device according to claim 1, characterized in that the second discharge throttle (12; 112) has a higher throttle resistance than the first discharge throttle (11; 111).
3. Kraftstoffeinspritzvorrichtung nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass das Steuerventil (6; 106) als Doppelsitzventil mit einem in einer Ventilkammer (14; 114) zwischen zwei Ventilsitzen (15, 16; 1 15, 116) axial verstellbaren Ventilkörper (13; 113) ausgebildet ist, wobei der eine Ventilsitz (15; 115) mit dem hochdruckseitigen Ventilanschluss (8; 108), der andere Ventilsitz (16; 116) mit dem ersten niederdruckseitigen Ventilanschluss (9; 109) und die Ventilkammer (14; 114) mit dem zweiten niederdruckseitigen Ventilanschluss (10; 110) verbunden sind.3. Fuel injection device according to claim 1 or 2, characterized in that the control valve (6; 106) as a double seat valve with an in a valve chamber (14; 114) between two valve seats (15, 16; 1 15, 116) axially adjustable valve body (13 ; 113) is formed, the one valve seat (15; 115) with the valve port (8; 108), the other valve seat (16; 116) with the first low pressure side valve connection (9; 109) and the valve chamber (14; 114) with the second low pressure side valve connection (10; 110).
4. Kraftstoffeinspritzvorrichtung nach Anspruch 3, dadurch gekennzeichnet, dass der Ventilkörper (13) des Steuerventils (6) kugelförmig ausgebildet ist.4. Fuel injection device according to claim 3, characterized in that the valve body (13) of the control valve (6) is spherical.
5. Kraftstoffeinspritzvorrichtung nach Anspruch 3, dadurch gekennzeichnet, dass der Ventilkörper (1 13) des Steuerventils (106) kolbenförmig ausgebildet ist.5. Fuel injection device according to claim 3, characterized in that the valve body (1 13) of the control valve (106) is piston-shaped.
6. Kraftstoffeinspritzvorrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Steuerraum (2; 102) über eine Zulaufdrossel (4; 104) an die Hochdruckseite (5; 105) angeschlossen ist.6. Fuel injection device according to one of the preceding claims, characterized in that the control chamber (2; 102) via an inlet throttle (4; 104) is connected to the high pressure side (5; 105).
7. Kraftstoffeinspritzvorrichtung nach Anspruch 6, dadurch gekennzeichnet, dass die Zulaufdrossel (4; 104) einen kleineren Drosselwiderstand als jede der beiden Ablaufdrosseln (15, 16; 115, 116) aufweist.7. Fuel injection device according to claim 6, characterized in that the inlet throttle (4; 104) has a smaller throttle resistance than each of the two outlet throttles (15, 16; 115, 116).
Kraftstoffeinspritzvorrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Ventilkörper (13; 113) des Steuerventils (6; 106) mittels eines piezoelektrischen Stellantriebs (17) verstellbar ist. Fuel injection device according to one of the preceding claims, characterized in that the valve body (13; 113) of the control valve (6; 106) is adjustable by means of a piezoelectric actuator (17).
EP03812121A 2002-12-05 2003-07-10 Fuel injection device comprising a 3/3-way control valve for forming the injection process Withdrawn EP1576276A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10256748 2002-12-05
DE10256748 2002-12-05
PCT/DE2003/002316 WO2004051071A1 (en) 2002-12-05 2003-07-10 Fuel injection device comprising a 3/3-way control valve for forming the injection process

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EP1576276A1 true EP1576276A1 (en) 2005-09-21

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JP4325589B2 (en) * 2004-07-06 2009-09-02 株式会社デンソー Common rail injector
CN100432415C (en) * 2004-07-06 2008-11-12 株式会社电装 Common-rail injector
DE102006013702A1 (en) * 2006-03-24 2007-09-27 Robert Bosch Gmbh Fuel injector comprises a control valve body that is directly loaded by a control space pressure without series connection of a throttle device
DE102006056840A1 (en) * 2006-12-01 2008-06-05 Robert Bosch Gmbh fuel injector
DE102007001554A1 (en) * 2007-01-10 2008-07-17 Robert Bosch Gmbh fuel injector
GB201411162D0 (en) * 2014-06-24 2014-08-06 Delphi International Operations Luxembourg S.�.R.L. Control valve

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Publication number Priority date Publication date Assignee Title
EP1041272B1 (en) * 1999-04-01 2004-10-27 Delphi Technologies, Inc. Fuel injector
DE19946833C2 (en) * 1999-09-30 2002-02-21 Bosch Gmbh Robert Valve for controlling liquids
JP3551898B2 (en) * 2000-06-15 2004-08-11 トヨタ自動車株式会社 Fuel injection valve
DE10039215A1 (en) * 2000-08-11 2002-02-28 Bosch Gmbh Robert Seat valve arrangement, in particular for a fuel injection system of an internal combustion engine

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