EP1939440B1 - Fuel injector valve - Google Patents

Fuel injector valve Download PDF

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Publication number
EP1939440B1
EP1939440B1 EP20070122092 EP07122092A EP1939440B1 EP 1939440 B1 EP1939440 B1 EP 1939440B1 EP 20070122092 EP20070122092 EP 20070122092 EP 07122092 A EP07122092 A EP 07122092A EP 1939440 B1 EP1939440 B1 EP 1939440B1
Authority
EP
European Patent Office
Prior art keywords
valve
outlet
fuel injection
magnet coil
solenoid valve
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.)
Not-in-force
Application number
EP20070122092
Other languages
German (de)
French (fr)
Other versions
EP1939440A3 (en
EP1939440A2 (en
Inventor
Gert Wolf
Matthias Burger
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 EP1939440A2 publication Critical patent/EP1939440A2/en
Publication of EP1939440A3 publication Critical patent/EP1939440A3/en
Application granted granted Critical
Publication of EP1939440B1 publication Critical patent/EP1939440B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • 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
    • F02M45/04—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 with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/08—Injectors peculiar thereto
    • F02M45/086—Having more than one injection-valve controlling discharge orifices
    • 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
    • F02M63/0024—Valves characterised by the valve actuating means electrical, e.g. using solenoid in combination with permanent magnet
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0059—Arrangements of valve actuators
    • F02M63/0061—Single actuator acting on two or more valve bodies
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0059—Arrangements of valve actuators
    • F02M63/0063—Two or more actuators acting on a single valve body
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/46—Valves, e.g. injectors, with concentric valve bodies

Definitions

  • the invention relates to a fuel injection valve for fuel injection systems of internal combustion engines. Specifically, the invention relates to an injector for fuel injection systems of air-compressing, self-igniting internal combustion engines.
  • EP 1 724 462 discloses a valve according to the preamble of independent claim 1.
  • a fuel injector for direct injection of diesel fuel into an internal combustion engine has a valve housing consisting of several housing parts.
  • a fuel inlet nozzle is provided, wherein within the valve housing, a channel for the passage of fuel is formed, which opens into a pressure chamber, which is provided in Abspritzides below a servo control circuit of the fuel injection valve. From this channel branches off at the height of the Hubüber GmbHs adopted from an inlet throttle, is passed over the fuel from the channel into a control chamber of the hydraulic coupler.
  • an outlet throttle is provided, which connects the control chamber with a 2/2-way valve. If an injection takes place, is opens the switching valve for a short time, so that the pressure in the control chamber drops, resulting in the spraying of fuel from the pressure chamber into a chamber of the internal combustion engine.
  • the fuel injection valve according to the invention with the features of claim 1 has the advantage that the solenoid valve has at least three different positions, so that more extensive shaping of the injection curve are possible, with a relatively inexpensive design can be achieved.
  • the solenoid valve has a first energizable solenoid coil, a second energizable solenoid coil and a permanently magnetized armature provided between the magnet coils.
  • the two magnetic coils are energized so that in each case a magnetic repulsion of the armature is achieved.
  • the armature is held reliably in the center position, wherein the magnetic forces compensate for any flow forces that are transmitted via a valve needle of the solenoid valve to the armature compensate.
  • the permanently magnetized armature has an annular permanent magnet with two concentrically arranged poles spaced apart in the radial direction.
  • a Curie temperature (depolarization temperature) of the permanent magnets is above 100 ° C.
  • the Curie temperature indicates from which temperature the magnet loses its magnetization.
  • the Curie temperature is above 100 ° C, it is ensured that no demagnetization of the permanent magnets occurs during normal operation of the fuel injection valve.
  • the servo control circuit has a control chamber, that an inlet is provided with an inlet throttle, which opens into the control chamber, that the first outlet and the second outlet are connected to the control chamber, that the first outlet has a throttle and that second sequence has a throttle.
  • the servo control circuit for driving a first valve needle part has a first control chamber, which is connected to the first outlet, and for driving a second valve needle part has a second control chamber, which is connected to the second outlet, and in that a first inlet with a Inlet restrictor, which opens into the first control chamber, and a second inlet with an inlet throttle, which opens into the second control chamber, are provided.
  • a differentiated control of the valve needle parts on the pressures in the control rooms is possible.
  • first valve needle part to cooperate with a valve seat surface to form a sealing seat in order to control the spraying of fuel via at least one nozzle opening
  • second valve needle part to cooperate with the valve seat surface to form a sealing seat in order to spray off fuel via at least one control further nozzle opening.
  • a remanence of the permanent magnets is in each case above 0.3 T.
  • An embodiment of the permanent magnets of neodymium and / or iron and / or boron has the advantage that due to a relatively high energy density, a very small volume of construction is possible and / or large magnetic forces or short switching times possible are.
  • a seat diameter of a sealing seat of the solenoid valve which serves to block the connection between the first outlet and the second outlet with the return in the first position, is smaller than a needle diameter of a valve needle of the solenoid valve.
  • the needle diameter of the valve needle of the solenoid valve is smaller than a seat diameter of another sealing seat, which serves to block the second sequence in the third position.
  • the valve needle of the solenoid valve keeps itself in the other end position by itself in the seat.
  • the solenoid valve may be configured so that the valve needle of the solenoid valve automatically stops in the respective seat in both end positions. Only to hold the valve needle of the solenoid valve in a middle position then a permanent energization of the solenoid valve is required.
  • Fig. 1 shows a first embodiment of a fuel injection valve 1 of the invention in a schematic, axial sectional view.
  • the fuel injection valve 1 can serve in particular as an injector for fuel injection systems of air-compressing, self-igniting internal combustion engines.
  • the fuel injection valve 1 is suitable for commercial vehicles or passenger cars.
  • a preferred use of the fuel injection valve 1 is for a fuel injection system with a common rail, the diesel fuel under high pressure leads to a plurality of fuel injection valves 1.
  • the fuel injection valve 1 according to the invention is also suitable for other applications.
  • the fuel injection valve 1 has a multi-part valve housing 2, which is suitably connected to a nozzle body 3. On the nozzle body 3, a valve seat surface 4 is formed, which cooperates with a valve closing body 5 to a sealing seat.
  • the valve closing body 5 is integrally formed with a valve needle 6, which is provided in a fuel chamber 7 of the nozzle body 3.
  • the fuel injection valve 1 is connected via a high pressure line 8 to a high pressure pump 9, wherein the connection can be made indirectly via a common rail.
  • the high-pressure line 8 has a branch, so that the high-pressure line 8 opens directly into the fuel chamber 7.
  • an inlet throttle 10 is provided, via which the high-pressure line 8 opens into a control chamber 11.
  • the control chamber 11 is bounded by the nozzle body 3 or a throttle plate connected to the nozzle body 3, a control chamber sleeve 12 and a piston section 13 of the valve needle 6.
  • the control chamber sleeve 12 is pressed by a spring element 14 against the nozzle body 3 and the throttle plate.
  • pressure results in a resultant force on the valve needle 6, which causes an opening or closing of the valve closing body 5, so that the sealing seat formed between the valve seat surface 4 and the valve closing body 5 is opened or closed, wherein In the open state, fuel can be sprayed off via nozzle openings 15 from the fuel chamber 7 into a combustion chamber of the internal combustion engine.
  • the fuel injection valve 1 also has a solenoid valve 20 which is provided inside the valve housing 2.
  • the solenoid valve 20 has a valve needle 21.
  • the solenoid valve 20 has a valve closing body 22 and an armature 23.
  • the valve closing body 22 is arranged at one end of the valve needle 21 and the armature 23 is arranged in the region of another end of the valve needle 21.
  • the armature 23 is permanently magnetized and accordingly has at least one permanently magnetic material, for example a ferrite material or neodymium and / or iron and / or boron.
  • the magnetic polarization of the armature 23 is in the Fig. 1 represented by "N" for North Pole and "S" for South Pole.
  • Of the Anchor 23 is arranged in an armature space 24 of the nozzle body 3, so that a certain adjustment movement of the armature 23 and thus an adjustment of the valve needle 21 of the solenoid valve 20 is made possible.
  • the armature 23 connected to the valve needle 21 is arranged between a first magnet coil 25 and a second magnet coil 26 of the solenoid valve 20.
  • the magnetic coils 25, 26 have ferromagnetic metal rings 27, 28, each with a U-profile. Within the metal rings 27, 28 are wire coils 29, 30 are provided, which are energized independently of each other.
  • the first magnetic coil 25 is energized so that a magnetic repulsion of the armature 23 of the first magnetic coil 25 is reached.
  • the second magnetic coil 26 is energized so that a magnetic repulsion of the armature 23 of the second magnetic coil 26 can be achieved.
  • the first magnet coil 25 and / or the second magnet coil 26 can also each be energized in an opposite direction in order to achieve an attraction of the armature 23 to the first magnet coil 25 and the second magnet coil 26.
  • the solenoid valve 20 is at least designed so that in each case a repulsion of the armature 23 of the first solenoid coil 25 and the second solenoid coil 26 by corresponding energization of the magnetic coils 25, 26 can be achieved.
  • the switching behavior of the solenoid valve 20, in particular the switching speed can be additionally influenced.
  • the solenoid valve 20 has a control valve chamber 31 which is connectable via a return 32 to a tank or the like.
  • first position of the solenoid valve 20 is a means of the Closed valve seat 22 formed sealing seat 33 closed, so that the connection between the control valve chamber 31 and the return line 32 is locked.
  • the control chamber 11 is connected to the control valve chamber 31 by means of a first outlet 34 and a second outlet 35.
  • the first outlet 34 has a throttle 36 and the outlet 35 has a throttle 37.
  • the throttles 36, 37 thus represent with respect to the control chamber 11 drain throttles.
  • the processes 34, 35 open into the control valve chamber 31, wherein in the in the Fig.
  • the solenoid valve 20 may be placed in a second position by energizing both the first solenoid coil 25 and the second solenoid coil 26 so that repulsion of the armature 23 both with respect to the first solenoid coil 25 and with respect to the second solenoid coil 26 is reached.
  • the armature 23 is thus at least substantially in the middle between the two magnetic coils 25, 26, since there cancel the acting on the armature 23, repulsive magnetic forces of the magnetic coils 25, 26 in approximately.
  • a resulting restoring force is generated on the armature 23, which increases, for example, exponentially with the adjustment of the central position.
  • the sealing seat 33 is opened, so that a connection between the control valve chamber 31 and the return 32 consists.
  • both the first drain 34 and the second drain 35 are connected to the return 32 via the control valve chamber 31.
  • flow forces acting on the valve closing body 22 are compensated by the restoring force generated during an adjustment of the valve closing body 22 from the second position, resulting from the magnetic fields of the two magnetic coils 25, 26.
  • the armature 23 and thus the valve needle 21 and the valve closing body 22 is held at least substantially in the second position.
  • the resulting throttling effect is smaller than each individual throttling action of the throttles 36, 37, since fuel from the control chamber 11 flows via the two outlets 34, 35 into the control valve chamber 31 to the return 32.
  • a relatively fast opening of the valve needle 6 can be achieved, so that a rapid increase in the amount of fuel discharged per unit time via the nozzle openings 15 is achieved.
  • the solenoid valve 20 also has a third position in which the valve closing body 22 closes the second outlet 35 by closing a sealing seat 38. In this third position, there is thus no connection between the second outlet 35 and the control valve chamber 31, while the first outlet 34 is connected to the control valve chamber 31 and at the same time there is an open connection between the control valve chamber 31 and the return 32.
  • the entire throttle effect with respect to the processes 34, 35 given solely by the throttle 36. Therefore, a relatively large ratio of the total throttle effect of the drains 34, 35, which is equal to the effect of the drain throttle 36, is achieved with respect to the inlet throttle 10.
  • a seat diameter of the sealing seat 33 of the solenoid valve 20, which serves to block the connection between the first drain 34 and the second drain 35 with the return 32 in the first position, is smaller than a needle diameter of the valve needle 21 of the solenoid valve 20.
  • the control valve chamber 31 has High pressure while the return 32 has low pressure. Thus, the valve needle 21 keeps itself in the sealing seat 33 without further energization of the solenoid valve.
  • the needle diameter of the valve needle 21 of the solenoid valve 20 is smaller than a seat diameter of the other sealing seat, which serves to lock the second drain 35 in the third position.
  • valve needle 21 in both end positions an automatic hold the valve needle 21 can be achieved in the respective sealing seat, so that in each case a hydraulic fixation is achieved.
  • the switching of the solenoid valve 20 in the first position, which in the Fig. 1 can also be done by the first solenoid is energized so that an attraction of the armature 23 is reached.
  • a switching of the solenoid valve 20 in the third position can also be achieved in that the second magnetic coil 26 is energized so that a tightening of the armature 23 is reached.
  • the switching speed can be increased, for example, by energizing the first magnetic coil 25 such that a repulsion of the armature 23 is achieved while the second magnetic coil 26 is energized in the opposite direction, so that an attraction of the armature 23 is achieved by the second magnetic coil 26 to get a quick switch from the one in the Fig. 1 to reach the first position shown in the third position.
  • the inlet throttle 10, the control chamber 11, and the outlet throttles 36, 37 are part of a servo control circuit 40 of the fuel injection valve 1.
  • the in the Fig. 1 illustrated embodiment of the servo control circuit 40 represents a possibility in which the three switching states of the solenoid valve 20 is used in an advantageous manner for varying the A / Z ratio.
  • the solenoid valve 20 may also be combined with differently designed servo control circuits 40.
  • the solenoid valve 20 controls by means of the servo control circuit 40, a fuel quantity which can be sprayed through the nozzle openings 50, wherein the control is influenced substantially by the choice of the respective position of the solenoid valve 20. Further possibilities of influencing arise in particular by influencing the switching speed of the solenoid valve 20.
  • Fig. 2 shows a second embodiment of a fuel injection valve 1 in a simplified, schematic sectional view.
  • the valve needle 6 has a first valve needle part 41 and a second valve needle part 42.
  • the control of the first valve needle part 41 via a first control chamber 43 which is bounded by the control chamber sleeve 12, a further control chamber sleeve 44, the valve needle parts 41, 42 and a throttle plate 45.
  • the control of the second valve needle part 42 via a second control chamber 46, which is bounded by the further control chamber sleeve 44, the second valve needle part 42 and the throttle plate 45.
  • a plurality of throttles 36, 37, 47, 48 are formed, namely the inlet throttles 47, 48 and the outlet throttles 36, 37.
  • the inlet throttle 47 of a first inlet 51 opens into the first control chamber 43.
  • Die The inlet throttle 48 of a second inlet 52 opens into the second control chamber 46.
  • the outlet throttle 36 is part of the first outlet 34, which connects the first control chamber 43 to the control valve chamber 31.
  • the outlet throttle 37 is part of the second outlet 35, which connects the second control chamber 46 with the control valve chamber 31.
  • spring elements 14, 49 are provided, which act on the control chamber sleeves 12, 44 against the throttle plate 45 and the valve needle parts 41, 42 in the unpressurized state in the in the Fig. 2 Adjust illustrated starting position, in which the fuel injection valve 1 is closed.
  • the inlet throttle 47 is part of the first inlet 51, which leads from the inlet 8 into the first control chamber 43. Furthermore, the inlet throttle 48 is part of the second inlet 52, which leads from the inlet 8 into the second control chamber 46.
  • the first inlet 51 opens into the first control chamber 43 and the second inlet 52 opens into the second control chamber 46th
  • the nozzle body 3 has the nozzle openings 15 and further nozzle openings 50.
  • the first valve needle part 41 with the valve seat surface 4 forms a sealing seat, which seals the nozzle openings 15.
  • the second valve needle part 42 with the valve seat surface 4 forms a sealing seat, which seals the other nozzle openings 50.
  • different positions of the first valve needle part 41 and the second valve needle part 42 can be achieved to respectively open or close the nozzle openings 15 and the other nozzle openings 50, so that fuel over the Nozzle openings 15 and / or the other nozzle openings 50 and / or that no fuel on the nozzle openings 15, 50 is sprayed. This can lead to a quantity of fuel sprayed off per unit of time and, on the other hand, the jet geometry of the sprayed-off fuel.
  • the servo control circuit 40 includes in this embodiment, the throttles 36, 37, 47, 48, the first control chamber 43 and the second control chamber 46th
  • the invention is not limited to the described embodiments.
  • the invention is suitable for servo-controlled injectors, as used for example in diesel direct injection.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)

Description

Stand der TechnikState of the art

Die Erfindung betrifft ein Brennstoffeinspritzventil für Brennstoffeinspritzanlagen von Brennkraftmaschinen. Speziell betrifft die Erfindung einen Injektor für Brennstoffeinspritzanlagen von luftverdichtenden, selbstzündenden Brennkraftmaschinen.The invention relates to a fuel injection valve for fuel injection systems of internal combustion engines. Specifically, the invention relates to an injector for fuel injection systems of air-compressing, self-igniting internal combustion engines.

EP 1 724 462 offenbart ein Ventil gemäß dem Oberbegriff des unabhängigen Anspruchs 1. EP 1 724 462 discloses a valve according to the preamble of independent claim 1.

Aus der DE 101 64 123 A1 ist ein Brennstoffeinspritzventil zur direkten Einspritzung von Dieselbrennstoff in eine Brennkraftmaschine bekannt. Das bekannte Brennstoffeinspritzventil weist ein aus mehreren Gehäuseteilen bestehendes Ventilgehäuse auf. Dabei ist ein Brennstoffeinlassstutzen vorgesehen, wobei innerhalb des Ventilgehäuses ein Kanal zur Durchleitung von Brennstoff ausgebildet ist, der in einen Druckraum mündet, welcher in Abspritzrichtung gesehen unterhalb eines Servosteuerkreislaufs des Brennstoffeinspritzventils vorgesehen ist. Von diesem Kanal zweigt auf der Höhe der Hubübersetzungseinrichtung eine Zulaufdrossel ab, über die Brennstoff aus dem Kanal in einen Steuerraum des hydraulischen Kopplers geführt wird. Ferner ist eine Ablaufdrossel vorgesehen, die den Steuerraum mit einem 2/2-Schaltventil verbindet. Soll eine Einspritzung erfolgen, wird das Schaltventil kurzzeitig geöffnet, so dass der Druck im Steuerraum absinkt, was zum Abspritzen von Brennstoff aus dem Druckraum in eine Kammer der Brennkraftmaschine führt.From the DE 101 64 123 A1 For example, a fuel injector for direct injection of diesel fuel into an internal combustion engine is known. The known fuel injection valve has a valve housing consisting of several housing parts. In this case, a fuel inlet nozzle is provided, wherein within the valve housing, a channel for the passage of fuel is formed, which opens into a pressure chamber, which is provided in Abspritzrichtung below a servo control circuit of the fuel injection valve. From this channel branches off at the height of the Hubübersetzungseinrichtung from an inlet throttle, is passed over the fuel from the channel into a control chamber of the hydraulic coupler. Furthermore, an outlet throttle is provided, which connects the control chamber with a 2/2-way valve. If an injection takes place, is opens the switching valve for a short time, so that the pressure in the control chamber drops, resulting in the spraying of fuel from the pressure chamber into a chamber of the internal combustion engine.

Das aus der DE 101 64 123 A1 bekannte Brennstoffeinspritzventil hat den Nachteil, dass die Form des Einspritzverlaufs durch die konstruktive Ausgestaltung des Brennstoffeinspritzventils im Wesentlichen fest vorgegeben ist, wobei die Länge des Einspritzverlaufs durch die Schaltzeitpunkte für das Schaltventil beeinflussbar ist, so dass für darüber hinausgehende Einspritzverlaufsformungen konstruktive Änderungen am Brennstoffeinspritzventil erforderlich sind.That from the DE 101 64 123 A1 known fuel injection valve has the disadvantage that the shape of the injection curve is fixed by the structural design of the fuel injector substantially fixed, the length of the injection profile can be influenced by the switching times for the switching valve, so that for more than injection curve shaping changes in design of the fuel injector are required.

Offenbarung der ErfindungDisclosure of the invention

Das erfindungsgemäße Brennstoffeinspritzventil mit den Merkmalen des Anspruchs 1 hat demgegenüber den Vorteil, dass das Magnetventil zumindest drei verschiedene Stellungen aufweist, so dass weitergehende Formungen des Einspritzverlaufs möglich sind, wobei eine relativ kostengünstige Ausgestaltung erzielbar ist.The fuel injection valve according to the invention with the features of claim 1 has the advantage that the solenoid valve has at least three different positions, so that more extensive shaping of the injection curve are possible, with a relatively inexpensive design can be achieved.

Erfindungsgemäß weist das Magnetventil eine erste bestrombare Magnetspule, eine zweite bestrombare Magnetspule und einen zwischen den Magnetspulen vorgesehenen permanent magnetisierten Anker auf. In Abhängigkeit von der Bestromung der jeweiligen Magnetspule können unterschiedliche Schaltstellungen des Magnetventils realisiert werden. Speziell ist es vorteilhaft, dass die beiden Magnetspulen so bestromt sind, dass jeweils eine magnetische Abstoßung des Ankers erzielt ist. Dadurch wird der Anker zuverlässig in der Mittelstellung gehalten, wobei die Magnetkräfte eventuelle Strömungskräfte, die über eine Ventilnadel des Magnetventils auf den Anker übertragen werden, kompensieren.According to the invention, the solenoid valve has a first energizable solenoid coil, a second energizable solenoid coil and a permanently magnetized armature provided between the magnet coils. Depending on the energization of the respective solenoid different switching positions of the solenoid valve can be realized. Specifically, it is advantageous that the two magnetic coils are energized so that in each case a magnetic repulsion of the armature is achieved. As a result, the armature is held reliably in the center position, wherein the magnetic forces compensate for any flow forces that are transmitted via a valve needle of the solenoid valve to the armature compensate.

Erfindungsgemäß weist der permanent magnetisierte Anker einen ringförmigen Dauermagneten mit zwei konzentrisch angeordneten, in radialer Richtung beabstandeten Polen auf. Dabei liegt eine Curietemperatur (Depolarisationstemperatur) der Dauermagnete jeweils über 100 °C. Die Curietemperatur gibt an, ab welcher Temperatur der Magnet seine Magnetisierung verliert. Wenn die Curietemperatur über 100 °C liegt, ist sichergestellt, dass während des normalen Betriebs des Brennstoffeinspritzventils keine Entmagnetisierung der Dauermagnete auftritt.According to the invention, the permanently magnetized armature has an annular permanent magnet with two concentrically arranged poles spaced apart in the radial direction. In this case, a Curie temperature (depolarization temperature) of the permanent magnets is above 100 ° C. The Curie temperature indicates from which temperature the magnet loses its magnetization. When the Curie temperature is above 100 ° C, it is ensured that no demagnetization of the permanent magnets occurs during normal operation of the fuel injection valve.

Durch die in den Unteransprüchen ausgeführte Maßnahmen sind vorteilhafte Weiterbildungen des im Anspruch 1 angegebenen Brennstoffeinspritzventils möglich.The measures set out in the dependent claims advantageous refinements of the fuel injection valve specified in claim 1 are possible.

Vorteilhaft ist es, dass der Servosteuerkreislauf einen Steuerraum aufweist, dass ein Zulauf mit einer Zulaufdrossel vorgesehen ist, der in den Steuerraum mündet, dass der erste Ablauf und der zweite Ablauf mit dem Steuerraum verbunden sind, dass der erste Ablauf eine Drossel aufweist und dass der zweite Ablauf eine Drossel aufweist. Somit sind in Abhängigkeit von der jeweils gewählten Schaltstellung des Magnetventils Variationen in der Gesamtwirkung der sich über die beiden Abläufe aus dem Steuerraum ergebenden Drosselwirkungen möglich. Somit kann das Verhältnis der Gesamtwirkung der Ablaufdrosseln in Bezug auf die Wirkung der Zulaufdrossel variiert werden. Somit kann speziell die Öffnungs- und Schließbewegung einer Ventilnadel des Brennstoffeinspritzventils beeinflusst werden, um den Verlauf der abgespritzten Brennstoffmenge zu variieren.It is advantageous that the servo control circuit has a control chamber, that an inlet is provided with an inlet throttle, which opens into the control chamber, that the first outlet and the second outlet are connected to the control chamber, that the first outlet has a throttle and that second sequence has a throttle. Thus, in Depending on the selected switching position of the solenoid valve variations in the overall effect of the two processes resulting from the control room throttle effects possible. Thus, the ratio of the overall effect of the drainage throttles with respect to the effect of the inlet throttle can be varied. Thus, in particular, the opening and closing movement of a valve needle of the fuel injection valve can be influenced in order to vary the course of the amount of fuel sprayed off.

Vorteilhaft ist es, dass der Servosteuerkreislauf zum Ansteuern eines ersten Ventilnadelteils einen ersten Steuerraum, der mit dem ersten Ablauf verbunden ist, und zum Ansteuern eines zweiten Ventilnadelteils einen zweiten Steuerraum aufweist, der mit dem zweiten Ablauf verbunden ist, und dass ein erster Zulauf mit einer Zulaufdrossel, der in den ersten Steuerraum mündet, und ein zweiter Zulauf mit einer Zulaufdrossel, der in den zweiten Steuerraum mündet, vorgesehen sind. Somit ist eine differenzierte Ansteuerung der Ventilnadelteile über die Drucke in den Steuerräumen möglich.It is advantageous that the servo control circuit for driving a first valve needle part has a first control chamber, which is connected to the first outlet, and for driving a second valve needle part has a second control chamber, which is connected to the second outlet, and in that a first inlet with a Inlet restrictor, which opens into the first control chamber, and a second inlet with an inlet throttle, which opens into the second control chamber, are provided. Thus, a differentiated control of the valve needle parts on the pressures in the control rooms is possible.

Ferner ist es vorteilhaft, dass das erste Ventilnadelteil mit einer Ventilsitzfläche zu einem Dichtsitz zusammenwirkt, um ein Abspritzen von Brennstoff über zumindest eine Düsenöffnung zu steuern, und dass das zweite Ventilnadelteil mit der Ventilsitzfläche zu einem Dichtsitz zusammenwirkt, um ein Abspritzen von Brennstoff über zumindest eine weitere Düsenöffnung zu steuern. Dadurch ist eine variable Ansteuerung der Düsenöffnung und der weiteren Düsenöffnung möglich, so dass unterschiedliche Brennstoffmengen, die abgespritzt werden, und unterschiedliche Strahlgeometrien in Bezug auf die jeweilige Lage der Düsenöffnung und der weiteren Düsenöffnung realisiert werden können.Furthermore, it is advantageous for the first valve needle part to cooperate with a valve seat surface to form a sealing seat in order to control the spraying of fuel via at least one nozzle opening, and for the second valve needle part to cooperate with the valve seat surface to form a sealing seat in order to spray off fuel via at least one control further nozzle opening. As a result, a variable control of the nozzle opening and the other nozzle opening is possible, so that different amounts of fuel that are hosed, and different beam geometries with respect to the respective position of the nozzle opening and the can be realized further nozzle opening.

In vorteilhafter Weise liegt eine Remanenz der Dauermagnete jeweils über 0,3 T. Dadurch ist eine relativ kleine Ausgestaltung des Magnetvolumens möglich. Eine Ausgestaltung der Dauermagnete aus Neodym und/oder Eisen und/oder Bor hat den Vorteil, dass auf Grund einer relativ hohen Energiedichte ein sehr kleines Bauvolumen ermöglicht ist und/oder große Magnetkräfte beziehungsweise kurze Schaltzeiten ermöglicht sind.Advantageously, a remanence of the permanent magnets is in each case above 0.3 T. This makes a relatively small configuration of the magnet volume possible. An embodiment of the permanent magnets of neodymium and / or iron and / or boron has the advantage that due to a relatively high energy density, a very small volume of construction is possible and / or large magnetic forces or short switching times possible are.

Vorteilhaft ist es, dass ein Sitzdurchmesser eines Dichtsitzes des Magnetventils, der zum Sperren der Verbindung zwischen dem ersten Ablauf und dem zweiten Ablauf mit dem Rücklauf in der ersten Stellung dient, kleiner als ein Nadeldurchmesser einer Ventilnadel des Magnetventils ist. Dadurch hält sich die Ventilnadel des Magnetventils selbsttätig im Sitz.It is advantageous that a seat diameter of a sealing seat of the solenoid valve, which serves to block the connection between the first outlet and the second outlet with the return in the first position, is smaller than a needle diameter of a valve needle of the solenoid valve. As a result, the valve needle of the solenoid valve automatically keeps in the seat.

Ferner ist es vorteilhaft, dass der Nadeldurchmesser der Ventilnadel des Magnetventils kleiner als ein Sitzdurchmesser eines weiteren Dichtsitzes ist, der zum Sperren des zweiten Ablaufs in der dritten Stellung dient. Dadurch hält sich die Ventilnadel des Magnetventils auch in der anderen Endstellung von selbst im Sitz.Further, it is advantageous that the needle diameter of the valve needle of the solenoid valve is smaller than a seat diameter of another sealing seat, which serves to block the second sequence in the third position. As a result, the valve needle of the solenoid valve keeps itself in the other end position by itself in the seat.

Spezill kann das Magnetventil so ausgestaltet sein, dass sich die Ventilnadel des Magnetventils in beiden Endstellungen selbsttätig im jeweiligen Sitz hält. Nur zum Halten der Ventilnadel des Magnetventils in einer mittleren Stellung ist dann eine dauerhafte Bestromung des Magnetventils erforderlich.Specifically, the solenoid valve may be configured so that the valve needle of the solenoid valve automatically stops in the respective seat in both end positions. Only to hold the valve needle of the solenoid valve in a middle position then a permanent energization of the solenoid valve is required.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Bevorzugte Ausführungsbeispiele der Erfindung sind in der nachfolgenden Beschreibung unter Bezugnahme auf die beigefügten Zeichnungen, in denen sich entsprechende Elemente mit übereinstimmenden Bezugszeichen versehen sind, näher erläutert. Es zeigt:

  • Fig. 1 ein erstes Ausführungsbeispiel eines Brennstoffeinspritzventils der Erfindung in einer auszugsweisen, axialen Schnittdarstellung und
  • Fig. 2 ein zweites Ausführungsbeispiel eines Brennstoffeinspritzventils der Erfindung in einer auszugsweisen, axialen Schnittdarstellung.
Preferred embodiments of the invention are explained in more detail in the following description with reference to the accompanying drawings, in which corresponding elements are provided with identical reference numerals. It shows:
  • Fig. 1 a first embodiment of a Fuel injection valve of the invention in a partial, axial sectional view and
  • Fig. 2 A second embodiment of a fuel injection valve of the invention in an excerpt, axial sectional view.

Ausführungsformen der ErfindungEmbodiments of the invention

Fig. 1 zeigt ein erstes Ausführungsbeispiel eines Brennstoffeinspritzventils 1 der Erfindung in einer schematischen, axialen Schnittdarstellung. Das Brennstoffeinspritzventil 1 kann insbesondere als Injektor für Brennstoffeinspritzanlagen von luftverdichtenden, selbstzündenden Brennkraftmaschinen dienen. Speziell eignet sich das Brennstoffeinspritzventil 1 für Nutzkraftwagen oder Personenkraftwagen. Ein bevorzugter Einsatz des Brennstoffeinspritzventils 1 besteht für eine Brennstoffeinspritzanlage mit einem Common-Rail, das Dieselbrennstoff unter hohem Druck zu mehreren Brennstoffeinspritzventilen 1 führt. Das erfindungsgemäße Brennstoffeinspritzventil 1 eignet sich jedoch auch für andere Anwendungsfälle. Fig. 1 shows a first embodiment of a fuel injection valve 1 of the invention in a schematic, axial sectional view. The fuel injection valve 1 can serve in particular as an injector for fuel injection systems of air-compressing, self-igniting internal combustion engines. Specifically, the fuel injection valve 1 is suitable for commercial vehicles or passenger cars. A preferred use of the fuel injection valve 1 is for a fuel injection system with a common rail, the diesel fuel under high pressure leads to a plurality of fuel injection valves 1. However, the fuel injection valve 1 according to the invention is also suitable for other applications.

Das Brennstoffeinspritzventil 1 weist ein mehrteiliges Ventilgehäuse 2 auf, das auf geeignete Weise mit einem Düsenkörper 3 verbunden ist. An dem Düsenkörper 3 ist eine Ventilsitzfläche 4 ausgebildet, die mit einem Ventilschließkörper 5 zu einem Dichtsitz zusammenwirkt. Der Ventilschließkörper 5 ist einstückig mit einer Ventilnadel 6 ausgebildet, die in einem Brennstoffraum 7 des Düsenkörpers 3 vorgesehen ist. Das Brennstoffeinspritzventil 1 ist über eine Hochdruckleitung 8 mit einer Hochdruckpumpe 9 verbunden, wobei die Verbindung mittelbar über ein Common-Rail erfolgen kann. Die Hochdruckleitung 8 weist eine Abzweigung auf, so dass die Hochdruckleitung 8 zum einen direkt in den Brennstoffraum 7 mündet. Zum anderen ist eine Zulaufdrossel 10 vorgesehen, über die die Hochdruckleitung 8 in einen Steuerraum 11 mündet. Der Steuerraum 11 ist durch den Düsenkörper 3 beziehungsweise eine mit dem Düsenkörper 3 verbundene Drosselplatte, eine Steuerraumhülse 12 und einen Kolbenabschnitt 13 der Ventilnadel 6 begrenzt. Dabei wird die Steuerraumhülse 12 über ein Federelement 14 gegen den Düsenkörper 3 beziehungsweise die Drosselplatte gepresst. In Abhängigkeit von dem im Steuerraum 11 herrschenden Druck kommt es zu einer resultierenden Kraft auf die Ventilnadel 6, die ein Öffnen oder ein Schließen des Ventilschließkörpers 5 bewirkt, so dass der zwischen der Ventilsitzfläche 4 und dem Ventilschließkörper 5 gebildete Dichtsitz geöffnet beziehungsweise geschlossen ist, wobei im geöffneten Zustand Brennstoff über Düsenöffnungen 15 aus dem Brennstoffraum 7 in eine Brennkammer der Brennkraftmaschine abspritzbar ist.The fuel injection valve 1 has a multi-part valve housing 2, which is suitably connected to a nozzle body 3. On the nozzle body 3, a valve seat surface 4 is formed, which cooperates with a valve closing body 5 to a sealing seat. The valve closing body 5 is integrally formed with a valve needle 6, which is provided in a fuel chamber 7 of the nozzle body 3. The fuel injection valve 1 is connected via a high pressure line 8 to a high pressure pump 9, wherein the connection can be made indirectly via a common rail. The high-pressure line 8 has a branch, so that the high-pressure line 8 opens directly into the fuel chamber 7. On the other hand, an inlet throttle 10 is provided, via which the high-pressure line 8 opens into a control chamber 11. The control chamber 11 is bounded by the nozzle body 3 or a throttle plate connected to the nozzle body 3, a control chamber sleeve 12 and a piston section 13 of the valve needle 6. In this case, the control chamber sleeve 12 is pressed by a spring element 14 against the nozzle body 3 and the throttle plate. Depending on the pressure prevailing in the control chamber 11 pressure results in a resultant force on the valve needle 6, which causes an opening or closing of the valve closing body 5, so that the sealing seat formed between the valve seat surface 4 and the valve closing body 5 is opened or closed, wherein In the open state, fuel can be sprayed off via nozzle openings 15 from the fuel chamber 7 into a combustion chamber of the internal combustion engine.

Das Brennstoffeinspritzventil 1 weist außerdem ein Magnetventil 20 auf, das innerhalb des Ventilgehäuses 2 vorgesehen ist. Das Magnetventil 20 weist eine Ventilnadel 21 auf. Ferner weist das Magnetventil 20 einen Ventilschließkörper 22 und einen Anker 23 auf. Dabei ist der Ventilschließkörper 22 an einem Ende der Ventilnadel 21 angeordnet und der Anker 23 ist im Bereich eines anderen Endes der Ventilnadel 21 angeordnet. Der Anker 23 ist permanent magnetisiert und weist entsprechend zumindest ein permanent magnetisches Material auf, beispielsweise ein Ferritmaterial oder Neodym und/oder Eisen und/oder Bor. Die magnetische Polarisierung des Ankers 23 ist in der Fig. 1 durch "N" für Nordpol und "S" für Südpol veranschaulicht. Der Anker 23 ist dabei in einem Ankerraum 24 des Düsenkörpers 3 angeordnet, so dass eine gewisse Verstellbewegung des Ankers 23 und somit eine Verstellung der Ventilnadel 21 des Magnetventils 20 ermöglicht ist.The fuel injection valve 1 also has a solenoid valve 20 which is provided inside the valve housing 2. The solenoid valve 20 has a valve needle 21. Furthermore, the solenoid valve 20 has a valve closing body 22 and an armature 23. In this case, the valve closing body 22 is arranged at one end of the valve needle 21 and the armature 23 is arranged in the region of another end of the valve needle 21. The armature 23 is permanently magnetized and accordingly has at least one permanently magnetic material, for example a ferrite material or neodymium and / or iron and / or boron. The magnetic polarization of the armature 23 is in the Fig. 1 represented by "N" for North Pole and "S" for South Pole. Of the Anchor 23 is arranged in an armature space 24 of the nozzle body 3, so that a certain adjustment movement of the armature 23 and thus an adjustment of the valve needle 21 of the solenoid valve 20 is made possible.

Der mit der Ventilnadel 21 verbundene Anker 23 ist zwischen einer ersten Magnetspule 25 und einer zweiten Magnetspule 26 des Magnetventils 20 angeordnet. Die Magnetspulen 25, 26 weisen dabei ferromagnetische Metallringe 27, 28 mit jeweils einem U-Profil auf. Innerhalb der Metallringe 27, 28 sind Drahtspulen 29, 30 vorgesehen, die unabhängig voneinander bestrombar sind. Die erste Magnetspule 25 ist so bestrombar, dass eine magnetische Abstoßung des Ankers 23 von der ersten Magnetspule 25 erreichbar ist. Ferner ist die zweite Magnetspule 26 so bestrombar, dass eine magnetische Abstoßung des Ankers 23 von der zweiten Magnetspule 26 erreichbar ist. Die erste Magnetspule 25 und/oder die zweite Magnetspule 26 können auch jeweils in einer Gegenrichtung bestrombar sein, um eine Anziehung des Ankers 23 an die erste Magnetspule 25 beziehungsweise die zweite Magnetspule 26 zu erreichen. Das Magnetventil 20 ist aber zumindest so ausgestaltet, dass jeweils eine Abstoßung des Ankers 23 von der ersten Magnetspule 25 sowie der zweiten Magnetspule 26 durch entsprechende Bestromung der Magnetspulen 25, 26 erreichbar ist. Mit der Bestromung der ersten Magnetspule 25 und/oder der zweiten Magetspule 26 in Gegenrichtung kann das Schaltverhalten des Magnetventils 20, insbesondere die Schaltgeschwindigkeit, zusätzlich beeinflusst werden.The armature 23 connected to the valve needle 21 is arranged between a first magnet coil 25 and a second magnet coil 26 of the solenoid valve 20. The magnetic coils 25, 26 have ferromagnetic metal rings 27, 28, each with a U-profile. Within the metal rings 27, 28 are wire coils 29, 30 are provided, which are energized independently of each other. The first magnetic coil 25 is energized so that a magnetic repulsion of the armature 23 of the first magnetic coil 25 is reached. Further, the second magnetic coil 26 is energized so that a magnetic repulsion of the armature 23 of the second magnetic coil 26 can be achieved. The first magnet coil 25 and / or the second magnet coil 26 can also each be energized in an opposite direction in order to achieve an attraction of the armature 23 to the first magnet coil 25 and the second magnet coil 26. However, the solenoid valve 20 is at least designed so that in each case a repulsion of the armature 23 of the first solenoid coil 25 and the second solenoid coil 26 by corresponding energization of the magnetic coils 25, 26 can be achieved. With the energization of the first solenoid coil 25 and / or the second Magetspule 26 in the opposite direction, the switching behavior of the solenoid valve 20, in particular the switching speed, can be additionally influenced.

Das Magnetventil 20 weist einen Steuerventilraum 31 auf, der über einen Rücklauf 32 mit einem Tank oder dergleichen verbindbar ist. In der in der Fig. 1 dargestellten ersten Stellung des Magnetventils 20 ist ein mittels des Ventilschließkörpers 22 gebildeter Dichtsitz 33 geschlossen, so dass die Verbindung zwischen dem Steuerventilraum 31 und dem Rücklauf 32 gesperrt ist. Der Steuerraum 11 ist mittels eines ersten Ablaufs 34 und eines zweiten Ablaufs 35 mit dem Steuerventilraum 31 verbunden. Dabei weist der erste Ablauf 34 eine Drossel 36 auf und der Ablauf 35 weist eine Drossel 37 auf. Die Drosseln 36, 37 stellen somit in Bezug auf den Steuerraum 11 Ablaufdrosseln dar. Die Abläufe 34, 35 münden in den Steuerventilraum 31, wobei in der in der Fig. 1 dargestellten ersten Stellung eine Verbindung der Abläufe 34, 35 mit dem Rücklauf 32 gesperrt ist. Allerdings besteht bei dem dargestellten Ausführungsbeispiel eine Verbindung der beiden Abläufe 34, 35 über den Steuerventilraum 31. Im Betrieb des Brennstoffeinspritzventils 1 kann das Magnetventil 20 in die erste Stellung gebracht und in dieser gehalten werden, indem die zweite Magnetspule 26 bestromt wird, während die erste Magnetspule 25 stromfrei ist. Dadurch wird eine Abstoßung des Ankers 23 von der zweiten Magnetspule 26 erreicht.The solenoid valve 20 has a control valve chamber 31 which is connectable via a return 32 to a tank or the like. In the in the Fig. 1 shown first position of the solenoid valve 20 is a means of the Closed valve seat 22 formed sealing seat 33 closed, so that the connection between the control valve chamber 31 and the return line 32 is locked. The control chamber 11 is connected to the control valve chamber 31 by means of a first outlet 34 and a second outlet 35. In this case, the first outlet 34 has a throttle 36 and the outlet 35 has a throttle 37. The throttles 36, 37 thus represent with respect to the control chamber 11 drain throttles. The processes 34, 35 open into the control valve chamber 31, wherein in the in the Fig. 1 shown first position a connection of the processes 34, 35 is locked to the return 32. However, in the illustrated embodiment, a connection of the two processes 34, 35 via the control valve chamber 31. In operation of the fuel injection valve 1, the solenoid valve 20 can be brought into the first position and held therein by the second solenoid 26 is energized, while the first Solenoid coil 25 is de-energized. As a result, a repulsion of the armature 23 is achieved by the second magnetic coil 26.

Das Magnetventil 20 kann in eine zweite Stellung gebracht werden, indem sowohl die erste Magnetspule 25 als auch die zweite Magnetspule 26 bestromt werden, so dass eine Abstoßung des Ankers 23 sowohl in Bezug auf die erste Magnetspule 25 als auch in Bezug auf die zweite Magnetspule 26 erreicht ist. In dieser zweiten Stellung befindet sich der Anker 23 somit zumindest im Wesentlichen in der Mitte zwischen den beiden Magnetspulen 25, 26, da sich dort die auf den Anker 23 einwirkenden, abstoßenden Magnetkräfte der Magnetspulen 25, 26 in etwa aufheben. Durch Verstellen des Ankers 23 aus dieser Mittellage wird eine resultierende Rückstellkraft auf den Anker 23 erzeugt, die beispielsweise exponentiell mit der Verstellung aus der Mittellage zunimmt. In der zweiten Stellung ist der Dichtsitz 33 geöffnet, so dass eine Verbindung zwischen dem Steuerventilraum 31 und dem Rücklauf 32 besteht. Somit sind in der zweiten Stellung sowohl der erste Ablauf 34 als auch der zweite Ablauf 35 über den Steuerventilraum 31 mit dem Rücklauf 32 verbunden. Eventuell auftretende Strömungskräfte, die auf den Ventilschließkörper 22 einwirken, werden durch die bei einer Verstellung des Ventilschließkörpers 22 aus der zweiten Stellung erzeugte Rückstellkraft, die aus den Magnetfeldern der beiden Magnetspulen 25, 26 resultiert, kompensiert. Somit wird der Anker 23 und damit die Ventilnadel 21 sowie der Ventilschließkörper 22 zumindest im Wesentlichen in der zweiten Stellung gehalten.The solenoid valve 20 may be placed in a second position by energizing both the first solenoid coil 25 and the second solenoid coil 26 so that repulsion of the armature 23 both with respect to the first solenoid coil 25 and with respect to the second solenoid coil 26 is reached. In this second position, the armature 23 is thus at least substantially in the middle between the two magnetic coils 25, 26, since there cancel the acting on the armature 23, repulsive magnetic forces of the magnetic coils 25, 26 in approximately. By adjusting the armature 23 from this central position a resulting restoring force is generated on the armature 23, which increases, for example, exponentially with the adjustment of the central position. In the second Position, the sealing seat 33 is opened, so that a connection between the control valve chamber 31 and the return 32 consists. Thus, in the second position, both the first drain 34 and the second drain 35 are connected to the return 32 via the control valve chamber 31. Possibly occurring flow forces acting on the valve closing body 22, are compensated by the restoring force generated during an adjustment of the valve closing body 22 from the second position, resulting from the magnetic fields of the two magnetic coils 25, 26. Thus, the armature 23 and thus the valve needle 21 and the valve closing body 22 is held at least substantially in the second position.

In der zweiten Stellung ist die resultierende Drosselwirkung kleiner als jede einzelne Drosselwirkung der Drosseln 36, 37, da Brennstoff aus dem Steuerraum 11 über die beiden Abläufe 34, 35 in den Steuerventilraum 31 zum Rücklauf 32 fließt. Somit ergibt sich ein relativ kleines Verhältnis der effektiven Wirkung der beiden Ablaufdrosseln 36, 37 in Bezug auf die Wirkung der Zulaufdrossel 10. Damit lässt sich ein relativ schnelles Öffnen der Ventilnadel 6 erreichen, so dass ein rascher Anstieg der pro Zeiteinheit abgegebenen Brennstoffmenge über die Düsenöffnungen 15 erzielt ist.In the second position, the resulting throttling effect is smaller than each individual throttling action of the throttles 36, 37, since fuel from the control chamber 11 flows via the two outlets 34, 35 into the control valve chamber 31 to the return 32. This results in a relatively small ratio of the effective effect of the two outlet throttles 36, 37 with respect to the effect of the inlet throttle 10. Thus, a relatively fast opening of the valve needle 6 can be achieved, so that a rapid increase in the amount of fuel discharged per unit time via the nozzle openings 15 is achieved.

Das Magnetventil 20 weist ferner eine dritte Stellung auf, in der der Ventilschließkörper 22 durch Schließen eines Dichtsitzes 38 den zweiten Ablauf 35 verschließt. In dieser dritten Stellung besteht somit keine Verbindung zwischen dem zweiten Ablauf 35 und dem Steuerventilraum 31, während der erste Ablauf 34 mit dem Steuerventilraum 31 verbunden ist und zugleich eine geöffnete Verbindung zwischen dem Steuerventilraum 31 und dem Rücklauf 32 besteht. Somit ist die gesamte Drosselwirkung in Bezug auf die Abläufe 34, 35 allein durch die Drossel 36 gegeben. Daher wird ein relativ großes Verhältnis der gesamten Drosselwirkung der Abläufe 34, 35, die gleich der Wirkung der Ablaufdrossel 36 ist, in Bezug auf die Zulaufdrossel 10 erreicht. Durch Schalten des Magnetventils 20 aus der ersten Stellung in die dritte Stellung kann somit ein langsameres Öffnen der Ventilnadel 21 erzielt werden, so dass die pro Zeiteinheit abgespritzte Brennstoffmenge langsamer ansteigt, wenn von der ersten Stellung in die zweite Stellung geschalten wird. Das Erreichen der dritten Schaltstellung erfolgt, indem die erste Magnetspule 25 bestromt wird und die zweite Magnetspule 26 stromfrei geschaltet ist.The solenoid valve 20 also has a third position in which the valve closing body 22 closes the second outlet 35 by closing a sealing seat 38. In this third position, there is thus no connection between the second outlet 35 and the control valve chamber 31, while the first outlet 34 is connected to the control valve chamber 31 and at the same time there is an open connection between the control valve chamber 31 and the return 32. Thus is the entire throttle effect with respect to the processes 34, 35 given solely by the throttle 36. Therefore, a relatively large ratio of the total throttle effect of the drains 34, 35, which is equal to the effect of the drain throttle 36, is achieved with respect to the inlet throttle 10. By switching the solenoid valve 20 from the first position to the third position thus a slower opening of the valve needle 21 can be achieved, so that the amount of fuel sprayed off per unit time increases more slowly when switching from the first position to the second position. Achieving the third switching position is effected by the first solenoid coil 25 is energized and the second solenoid coil 26 is de-energized.

Ein Sitzdurchmesser des Dichtsitzes 33 des Magnetventils 20, der zum Sperren der Verbindung zwischen dem ersten Ablauf 34 und dem zweiten Ablauf 35 mit dem Rücklauf 32 in der ersten Stellung dient, ist kleiner als ein Nadeldurchmesser der Ventilnadel 21 des Magnetventils 20. Der Steuerventilraum 31 hat Hochdruck, während der Rücklauf 32 Niederdruck hat. Somit hält sich die Ventilnadel 21 auch ohne weitere Bestromung des Magnetventils selbsttätig im Dichtsitz 33.A seat diameter of the sealing seat 33 of the solenoid valve 20, which serves to block the connection between the first drain 34 and the second drain 35 with the return 32 in the first position, is smaller than a needle diameter of the valve needle 21 of the solenoid valve 20. The control valve chamber 31 has High pressure while the return 32 has low pressure. Thus, the valve needle 21 keeps itself in the sealing seat 33 without further energization of the solenoid valve.

Ferner ist der Nadeldurchmesser der Ventilnadel 21 des Magnetventils 20 kleiner als ein Sitzdurchmesser des weiteren Dichtsitzes, der zum Sperren des zweiten Ablaufs 35 in der dritten Stellung dient. Nach dem Schalten des Magnetventils in die dritte Stellung hat der Steuerventilraum 31 Niederdruck, während der Ankerraum 24 Hochdruck hat. Somit wird die Ventilnadel 21 auch in dieser Stellung selbsttätig im Dichtsitz 38 gehalten.Further, the needle diameter of the valve needle 21 of the solenoid valve 20 is smaller than a seat diameter of the other sealing seat, which serves to lock the second drain 35 in the third position. After switching the solenoid valve to the third position, the control valve chamber 31 has low pressure, while the armature space 24 has high pressure. Thus, the valve needle 21 is automatically held in this position in the sealing seat 38.

Somit kann in beiden Endstellungen ein selbsttätiges Halten der Ventilnadel 21 im jeweiligen Dichtsitz erreicht werden, so dass jeweils eine hydraulische Fixierung erreicht ist.Thus, in both end positions an automatic hold the valve needle 21 can be achieved in the respective sealing seat, so that in each case a hydraulic fixation is achieved.

Das Schalten des Magnetventils 20 in die erste Stellung, die in der Fig. 1 dargestellt ist, kann auch erfolgen, indem die erste Magnetspule so bestromt wird, dass eine Anziehung des Ankers 23 erreicht ist. Entsprechend kann ein Schalten des Magnetventils 20 in die dritte Stellung auch dadurch erreicht werden, dass die zweite Magnetspule 26 so bestromt wird, dass ein Anziehen des Ankers 23 erreicht ist. Ferner kann die Schaltgeschwindigkeit erhöht werden, indem beispielsweise die erste Magnetspule 25 so bestromt wird, dass eine Abstoßung des Ankers 23 erreicht ist, während die zweite Magnetspule 26 in Gegenrichtung bestromt ist, so dass eine Anziehung des Ankers 23 von der zweiten Magnetspule 26 erreicht ist, um ein schnelles Schalten von der in der Fig. 1 dargestellten ersten Stellung in die dritte Stellung zu erreichen.The switching of the solenoid valve 20 in the first position, which in the Fig. 1 can also be done by the first solenoid is energized so that an attraction of the armature 23 is reached. Accordingly, a switching of the solenoid valve 20 in the third position can also be achieved in that the second magnetic coil 26 is energized so that a tightening of the armature 23 is reached. Furthermore, the switching speed can be increased, for example, by energizing the first magnetic coil 25 such that a repulsion of the armature 23 is achieved while the second magnetic coil 26 is energized in the opposite direction, so that an attraction of the armature 23 is achieved by the second magnetic coil 26 to get a quick switch from the one in the Fig. 1 to reach the first position shown in the third position.

Zum Schutz des permanent magnetisierten Ankers 23 gegen Zugkräfte kann eine Beschichtung oder Verpackung des Ankers 23 oder zumindest eines Teils des Ankers 23 erfolgen, beispielsweise durch Eingießen des Ankers 23 in einen glasfaserverstärkten Kunststoff, durch Einkleben des Ankers 23 in Aluminiumplatten, durch Klammern oder Einpressen des Ankers 23 zwischen austenitischen Eisenplatten oder dergleichen.To protect the permanently magnetized armature 23 against tensile forces, a coating or packaging of the armature 23 or at least a portion of the armature 23, for example by pouring the armature 23 in a glass fiber reinforced plastic, by gluing the armature 23 in aluminum plates, by clamping or pressing the Anchor 23 between austenitic iron plates or the like.

In dem Ventilgehäuse 2 kann außerdem eine als Hochdruckleitung ausgestaltete Brennstoffleitung 39 vorgesehen sein, die mit der Hochdruckleitung 8 verbunden ist. In diesem Fall befindet sich im Betrieb des Brennstoffeinspritzventils 1 auch in dem Ankerraum 24 unter hohem Druck stehender Brennstoff.In the valve housing 2 may also be designed as a high-pressure line configured fuel line 39, which is connected to the high-pressure line 8. In this case, the fuel injection valve 1 is also in the armature space 24 under high pressure fuel.

Die Zulaufdrossel 10, der Steuerraum 11, und die Ablaufdrosseln 36, 37 sind Teil eines Servosteuerkreislaufs 40 des Brennstoffeinspritzventils 1. Die in der Fig. 1 dargestellte Ausgestaltung des Servosteuerkreislaufs 40 stellt eine Möglichkeit dar, bei der die drei Schaltzustände des Magnetventils 20 in vorteilhafter Weise zur Variation des A/Z-Verhältnisses zum Einsatz kommt. Das Magnetventil 20 kann aber auch mit anders ausgestalteten Servosteuerkreisläufen 40 kombiniert sein. Das Magnetventil 20 steuert dabei mittels des Servosteuerkreislaufs 40 eine Brennstoffmenge, die durch die Düsenöffnungen 50 abspritzbar ist, wobei die Steuerung im Wesentlichen durch die Wahl der jeweiligen Stellung des Magnetventils 20 beeinflusst ist. Weitere Möglichkeiten der Einflussnahme ergeben sich insbesondere durch die Beeinflussung der Schaltgeschwindigkeit des Magnetventils 20.The inlet throttle 10, the control chamber 11, and the outlet throttles 36, 37 are part of a servo control circuit 40 of the fuel injection valve 1. The in the Fig. 1 illustrated embodiment of the servo control circuit 40 represents a possibility in which the three switching states of the solenoid valve 20 is used in an advantageous manner for varying the A / Z ratio. The solenoid valve 20 may also be combined with differently designed servo control circuits 40. The solenoid valve 20 controls by means of the servo control circuit 40, a fuel quantity which can be sprayed through the nozzle openings 50, wherein the control is influenced substantially by the choice of the respective position of the solenoid valve 20. Further possibilities of influencing arise in particular by influencing the switching speed of the solenoid valve 20.

Fig. 2 zeigt ein zweites Ausführungsbeispiel eines Brennstoffeinspritzventils 1 in einer vereinfachten, schematischen Schnittdarstellung. In diesem Ausführungsbeispiel weist die Ventilnadel 6 ein erstes Ventilnadelteil 41 und ein zweites Ventilnadelteil 42 auf. Die Ansteuerung des ersten Ventilnadelteils 41 erfolgt über einen ersten Steuerraum 43, der durch die Steuerraumhülse 12, eine weitere Steuerraumhülse 44, die Ventilnadelteile 41, 42 und eine Drosselplatte 45 begrenzt ist. Die Ansteuerung des zweiten Ventilnadelteils 42 erfolgt über einen zweiten Steuerraum 46, der durch die weitere Steuerraumhülse 44, das zweite Ventilnadelteil 42 und die Drosselplatte 45 begrenzt ist. In der Drosselplatte 45 sind mehrere Drosseln 36, 37, 47, 48 ausgebildet, nämlich die Zulaufdrosseln 47, 48 und die Ablaufdrosseln 36, 37. Die Zulaufdrossel 47 eines ersten Zulaufs 51 mündet in den ersten Steuerraum 43. Die Zulaufdrossel 48 eines zweiten Zulaufs 52 mündet in den zweiten Steuerraum 46. Die Ablaufdrossel 36 ist Teil des ersten Ablaufs 34, der den ersten Steuerraum 43 mit dem Steuerventilraum 31 verbindet. Die Ablaufdrossel 37 ist Teil des zweiten Ablaufs 35, der den zweiten Steuerraum 46 mit dem Steuerventilraum 31 verbindet. Ferner sind Federelemente 14, 49 vorgesehen, die die Steuerraumhülsen 12, 44 gegen die Drosselplatte 45 beaufschlagen und die Ventilnadelteile 41, 42 im drucklosen Zustand in die in der Fig. 2 dargestellte Ausgangslage verstellen, in der das Brennstoffeinspritzventil 1 geschlossen ist. Fig. 2 shows a second embodiment of a fuel injection valve 1 in a simplified, schematic sectional view. In this embodiment, the valve needle 6 has a first valve needle part 41 and a second valve needle part 42. The control of the first valve needle part 41 via a first control chamber 43 which is bounded by the control chamber sleeve 12, a further control chamber sleeve 44, the valve needle parts 41, 42 and a throttle plate 45. The control of the second valve needle part 42 via a second control chamber 46, which is bounded by the further control chamber sleeve 44, the second valve needle part 42 and the throttle plate 45. In the throttle plate 45 a plurality of throttles 36, 37, 47, 48 are formed, namely the inlet throttles 47, 48 and the outlet throttles 36, 37. The inlet throttle 47 of a first inlet 51 opens into the first control chamber 43. Die The inlet throttle 48 of a second inlet 52 opens into the second control chamber 46. The outlet throttle 36 is part of the first outlet 34, which connects the first control chamber 43 to the control valve chamber 31. The outlet throttle 37 is part of the second outlet 35, which connects the second control chamber 46 with the control valve chamber 31. Further, spring elements 14, 49 are provided, which act on the control chamber sleeves 12, 44 against the throttle plate 45 and the valve needle parts 41, 42 in the unpressurized state in the in the Fig. 2 Adjust illustrated starting position, in which the fuel injection valve 1 is closed.

Die Zulaufdrossel 47 ist Teil des ersten Zulaufs 51, der von dem Zulauf 8 in den ersten Steuerraum 43 führt. Ferner ist die Zulaufdrossel 48 Teil des zweiten Zulaufs 52, der von dem Zulauf 8 in den zweiten Steuerraum 46 führt. Somit mündet der erste Zulauf 51 in den ersten Steuerraum 43 und der zweite Zulauf 52 mündet in den zweiten Steuerraum 46.The inlet throttle 47 is part of the first inlet 51, which leads from the inlet 8 into the first control chamber 43. Furthermore, the inlet throttle 48 is part of the second inlet 52, which leads from the inlet 8 into the second control chamber 46. Thus, the first inlet 51 opens into the first control chamber 43 and the second inlet 52 opens into the second control chamber 46th

Der Düsenkörper 3 weist die Düsenöffnungen 15 sowie weitere Düsenöffnungen 50 auf. Dabei bildet das erste Ventilnadelteil 41 mit der Ventilsitzfläche 4 einen Dichtsitz, der die Düsenöffnungen 15 abdichtet. Ferner bildet das zweite Ventilnadelteil 42 mit der Ventilsitzfläche 4 einen Dichtsitz, der die weiteren Düsenöffnungen 50 abdichtet. In Abhängigkeit von den Drucken im ersten Steuerraum 43 und im zweiten Steuerraum 46 können unterschiedliche Stellungen des ersten Ventilnadelteils 41 und des zweiten Ventilnadelteils 42 erreicht werden, um die Düsenöffnungen 15 und die weiteren Düsenöffnungen 50 jeweils zu öffnen oder zu schließen, so dass Brennstoff über die Düsenöffnungen 15 und/oder die weiteren Düsenöffnungen 50 und/oder dass kein Brennstoff über die Düsenöffnungen 15, 50 abgespritzt wird. Dadurch kann zum einen die pro Zeiteinheit abgespritzte Brennstoffmenge und zum anderen die Strahlgeometrie des abgespritzten Brennstoffs beeinflusst werden.The nozzle body 3 has the nozzle openings 15 and further nozzle openings 50. In this case, the first valve needle part 41 with the valve seat surface 4 forms a sealing seat, which seals the nozzle openings 15. Furthermore, the second valve needle part 42 with the valve seat surface 4 forms a sealing seat, which seals the other nozzle openings 50. Depending on the pressures in the first control chamber 43 and the second control chamber 46, different positions of the first valve needle part 41 and the second valve needle part 42 can be achieved to respectively open or close the nozzle openings 15 and the other nozzle openings 50, so that fuel over the Nozzle openings 15 and / or the other nozzle openings 50 and / or that no fuel on the nozzle openings 15, 50 is sprayed. This can lead to a quantity of fuel sprayed off per unit of time and, on the other hand, the jet geometry of the sprayed-off fuel.

Die Steuerung der Drucke in den Steuerräumen 43, 46 erfolgt über das Magnetventil 20. Dabei ermöglicht das Magnetventil 20 auf Grund der zumindest drei verschiedenen Schaltstellungen eine Ansteuerung sowohl des ersten Ventilnadelteils 41 als auch des zweiten Ventilnadelteils 42, wobei in der dritten Schaltstellung auch eine Betätigung nur des ersten Ventilnadelteils 41 erfolgen kann. Somit ist zur Ansteuerung der beiden Ventilnadelteile 41, 42 nur ein Steuerventil, nämlich das Magnetventil 20, erforderlich. Dadurch ergibt sich eine kompakte Bauweise des Brennstoffeinspritzventils 1 und die Möglichkeit, das Brennstoffeinspritzventil 1 wirtschaftlich herzustellen.The control of the pressures in the control chambers 43, 46 via the solenoid valve 20. In this case allows the solenoid valve 20 due to the at least three different switching positions a control of both the first valve needle part 41 and the second valve needle part 42, wherein in the third switching position and an operation only the first valve needle part 41 can take place. Thus, only one control valve, namely the solenoid valve 20, is required to control the two valve needle parts 41, 42. This results in a compact design of the fuel injection valve 1 and the ability to produce the fuel injection valve 1 economically.

Der Servosteuerkreislauf 40 umfasst in diesem Ausführungsbeispiel die Drosseln 36, 37, 47, 48, den ersten Steuerraum 43 und den zweiten Steuerraum 46.The servo control circuit 40 includes in this embodiment, the throttles 36, 37, 47, 48, the first control chamber 43 and the second control chamber 46th

Die Erfindung ist nicht auf die beschriebenen Ausführungsbeispiele beschränkt. Insbesondere eignet sich die Erfindung für servogesteuerte Injektoren, wie sie beispielsweise bei der Diesel-Direkteinspritzung eingesetzt werden.The invention is not limited to the described embodiments. In particular, the invention is suitable for servo-controlled injectors, as used for example in diesel direct injection.

Claims (14)

  1. Fuel injection valve (1), in particular injector for fuel injection systems of air-compressing, autoignition internal combustion engines, having a solenoid valve (20) arranged in a valve housing (2) and having a servo control circuit (40), wherein the solenoid valve (20), by means of the servo control circuit (40), controls an amount of fuel that can be injected through at least one nozzle opening (15, 50), wherein the solenoid valve (20), in a first position, blocks a connection of a first outlet (34) and of a second outlet (35) of the servo control circuit (40) to a return line (32), and in a second position, opens up the first outlet (34) and the second outlet (35), and in a third position, opens up the first outlet (34) and blocks the second outlet (35), characterized in that the solenoid valve (20) has a first energizable magnet coil (25), a second energizable magnet coil (26) and a permanently magnetized armature (23) provided between the magnet coils, and in that the permanently magnetized armature (23) has an annular permanent magnet with two concentrically arranged poles spaced apart in a radial direction.
  2. Fuel injection valve according to Claim 1, characterized in that the servo control circuit (40) has a control chamber (11), in that an inlet (8) is provided with an inlet throttle (10) which issues into the control chamber (11), in that the first outlet (34) and the second outlet (35) are connected to the control chamber (11), in that the first outlet (34) has a throttle (36), and in that the second outlet (35) has a throttle (37).
  3. Fuel injection valve according to Claim 1, characterized in that the servo control circuit (40) has, for the actuation of a first valve needle part (41), a first control chamber (43) which is connected to the first outlet (34), and has, for the actuation of a second valve needle part (42), a second control chamber (46) which is connected to the second outlet (35), and in that a first inlet (51) is provided with an inlet throttle (47) which issues into the first control chamber (43), and a second inlet (52) is provided with an inlet throttle (48) which issues into the second control chamber (46).
  4. Fuel injection valve according to Claim 3, characterized in that the first valve needle part (41) interacts with a valve seat surface (4) to form a sealing seat in order to control an injection of fuel via at least one nozzle opening (15), and in that the second valve needle part (42) interacts with the valve seat surface (4) to form a sealing seat in order to control an injection of fuel via at least one further nozzle opening (50).
  5. Fuel injection valve according to one of Claims 1 to 4, characterized in that a Curie temperature of the permanent magnets lies in each case above 100°C.
  6. Fuel injection valve according to one of Claims 1 to 5, characterized in that a retentivity of the permanent magnets lies in each case above 0.3 T.
  7. Fuel injection valve according to one of Claims 1 to 6, characterized in that the permanent magnets are produced from a material which has neodymium and/or iron and/or boron.
  8. Fuel injection valve according to one of Claims 1 to 7, characterized in that, for the switching of the solenoid valve (20), at least one magnet coil (25, 26) can be energized such that magnetic repulsion of the armature (23) by said magnet coil (25, 26) can be attained.
  9. Fuel injection valve according to one of Claims 1 to 8, characterized in that, for the switching of the solenoid valve (20) into the second position, the first magnet coil (25) and the second magnet coil (26) can be energized in such a way that repulsion of the armature (23) both by the first magnet coil (25) and also by the second magnet coil (26) can be attained.
  10. Fuel injection valve according to one of Claims 1 to 9, characterized in that, for the switching of the solenoid valve (20) into the first position, the first magnet coil (25) and the second magnet coil (26) can be energized in such a way that attraction of the armature (23) by the first magnet coil (25) and/or repulsion of the armature (23) by the second magnet coil (26) can be attained.
  11. Fuel injection valve according to one of Claims 1 to 10, characterized in that, for the switching of the solenoid valve (20) into the third position, the first magnet coil (25) and the second magnet coil (26) can be energized in such a way that repulsion of the armature (23) by the first magnet coil (25) and/or attraction of the armature (23) by the second magnet coil (26) can be attained.
  12. Fuel injection valve according to one of Claims 1 to 11, characterized in that the solenoid valve (20), in the first position, connects the first outlet (34) to the second outlet (35).
  13. Fuel injection valve according to one of Claims 1 to 12, characterized in that a seat diameter of a sealing seat (33) of the solenoid valve (20), which sealing seat serves for the blocking of the connection between the first outlet (34) and the second outlet (35) to the return line (32) in the first position, is smaller than a needle diameter of a valve needle (21) of the solenoid valve (20).
  14. Fuel injection valve according to one of Claims 1 to 13, characterized in that a needle diameter of a valve needle (21) of the solenoid valve (20) is smaller than a seat diameter of a further sealing seat (38) which serves for the blocking of the second outlet (35) in the third position.
EP20070122092 2006-12-29 2007-12-03 Fuel injector valve Not-in-force EP1939440B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200610061947 DE102006061947A1 (en) 2006-12-29 2006-12-29 Fuel injector

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EP1939440A2 EP1939440A2 (en) 2008-07-02
EP1939440A3 EP1939440A3 (en) 2009-09-09
EP1939440B1 true EP1939440B1 (en) 2013-06-19

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FR2924175A3 (en) * 2007-11-23 2009-05-29 Renault Sas Fuel injecting device for combustion engine, has sliding needle comprising portion introduced in control chamber, and closing unit adopting intermediate stable configuration in which fuel leakage opening is partially closed
GB0919645D0 (en) 2009-11-10 2009-12-23 Sentec Ltd Flux switched fuel injector
US9562505B2 (en) * 2013-06-11 2017-02-07 Cummins Inc. System and method for control of fuel injector spray
DE102013112752A1 (en) * 2013-11-19 2015-05-21 Denso Corporation fuel injector
DE102013112751A1 (en) * 2013-11-19 2015-05-21 Denso Corporation fuel injector
DE102017202932A1 (en) * 2017-02-23 2018-08-23 Robert Bosch Gmbh Fuel injection valve for injecting a gaseous and / or liquid fuel
DE102017212084A1 (en) 2017-07-14 2019-01-17 Robert Bosch Gmbh Bistable solenoid valve for a hydraulic brake system and method for controlling such a valve
CN114458502A (en) * 2022-03-09 2022-05-10 哈尔滨工程大学 Permanent magnet-electromagnetic coupling magnetic field high-speed electromagnetic valve capable of stably sitting
CN114483404B (en) * 2022-03-09 2023-02-14 哈尔滨工程大学 Electromagnetic-permanent magnet multi-magnetic field combined type high-speed electromagnetic valve with flexible damping
CN114458504B (en) * 2022-03-09 2022-10-28 哈尔滨工程大学 Variable-damping pre-magnetized permanent magnet-electromagnetic hybrid excitation high-speed electromagnetic valve
CN115977842B (en) * 2023-01-05 2024-04-12 钧风电控科技(泰州)有限责任公司 Auxiliary closing fuel injector

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JP2001012636A (en) * 1999-06-29 2001-01-16 Aisan Ind Co Ltd Fuel injection device having a plurality of solenoids and a common cylinder
JP3578105B2 (en) * 2001-04-12 2004-10-20 トヨタ自動車株式会社 Fuel injection device
DE10164123A1 (en) 2001-12-24 2003-01-30 Bosch Gmbh Robert Fuel injection device for direct injection internal combustion engine with valve device having elastic delay element between valve seat and control space at its opposite ends
DE102005020832A1 (en) * 2005-05-04 2006-11-09 Robert Bosch Gmbh Automotive fuel injection jet has two sliding needles both linked to a common fuel flow regulation chamber

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EP1939440A2 (en) 2008-07-02
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