EP1346150A1 - Fuel injection device for an internal combustion engine - Google Patents

Fuel injection device for an internal combustion engine

Info

Publication number
EP1346150A1
EP1346150A1 EP01989387A EP01989387A EP1346150A1 EP 1346150 A1 EP1346150 A1 EP 1346150A1 EP 01989387 A EP01989387 A EP 01989387A EP 01989387 A EP01989387 A EP 01989387A EP 1346150 A1 EP1346150 A1 EP 1346150A1
Authority
EP
European Patent Office
Prior art keywords
control valve
fuel injection
chamber
valve member
pressure
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Withdrawn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
EP01989387A
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 EP1346150A1 publication Critical patent/EP1346150A1/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Withdrawn legal-status Critical Current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
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0017—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
    • F02M57/023—Injectors structurally combined with fuel-injection pumps characterised by the pump drive mechanical
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically
    • F02M59/368—Pump inlet valves being closed when actuated
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
    • F02M59/468—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means using piezoelectric operating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • F02M61/205—Means specially adapted for varying the spring tension or assisting the spring force to close the injection-valve, e.g. with damping of valve lift
    • 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
    • F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
    • F02M63/0035—Poppet valves, i.e. having a mushroom-shaped valve member that moves perpendicularly to the plane of the valve seat
    • 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
    • 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
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0047—Four-way valves or valves with more than four ways
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0049—Combined valve units, e.g. for controlling pumping chamber and injection valve
    • 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
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • F02M2200/704—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with actuator and actuated element moving in different directions, e.g. in opposite directions

Definitions

  • the invention relates to a fuel injection device for an internal combustion engine according to the preamble of claim 1.
  • Such a fuel injection device is known from DE 198 35 494 AI.
  • This fuel injector has one of one
  • Pump piston limited pump work space that can be filled with fuel via a connection controlled by a control valve device and can be connected to a relief chamber. During a respective fuel injection, the pump work space is closed
  • Control valve device separated from the relief chamber and the pump work chamber is connected to the relief chamber by the control valve device to end the fuel injection.
  • the fuel injector also has
  • Fuel injection valve with an injection valve member which controls at least one injection opening and which is acted upon by the pressure prevailing in the pump work space in the opening direction and by a closing force in the closing direction. Closing the
  • Fuel injection valve takes place when the pump work chamber is relieved via the control valve device into the relief chamber by means of the injection valve member effective closing force. Short-term closing and reopening of the fuel injection valve is difficult here, since the pressure in the pump workspace only decreases and builds up again after a delay. A brief closing and reopening of the fuel injection valve is advantageous for a pre-injection and / or a post-injection of a small amount of fuel before or after the main injection of a large amount of fuel with regard to the pollutant emission and the noise development of the internal combustion engine.
  • the fuel injection device according to the invention with the features of claim 1 has the advantage that the control valve means
  • Fuel injection valve can be closed briefly by means of the pressure prevailing in the pump work space to interrupt the fuel injection.
  • the injection valve member is in addition to
  • Closing force is acted upon by the pressure prevailing in the pump work chamber in the closing direction, so that the fuel injection valve closes quickly.
  • the fuel injection device according to the invention thus enables a pre-injection and / or a post-injection of a small amount of fuel.
  • Fuel injection device for an internal combustion engine in a schematic representation according to a first embodiment, Figure 2 shows the fuel injection device with a control valve device according to a second
  • FIG. 1 shows the control valve device of Figure 2 in a first switching position
  • Figure 3 shows the control valve device of Figure 2 in a second switching position
  • Figure 4 shows the control valve device of Figure 2 in a third switching position.
  • FIG. 1 and 2 show a fuel injection device for an internal combustion engine 10, in particular a self-igniting internal combustion engine of a motor vehicle.
  • Fuel injection device is designed as a so-called pump nozzle unit, with a separate pump nozzle unit being provided for each cylinder of internal combustion engine 10.
  • the internal combustion engine 10 has one
  • the pump piston 14 is sealingly guided in a bore 16 and delimits a pump working space 18 in the bore 16.
  • the pump piston 14 is held in contact with the cam 12 by a prestressed compression spring 15.
  • the fuel injector also includes a fuel injector 20 that is one in one Has valve body 21 axially displaceably guided injection valve member 22.
  • the valve body 21 has at least one, preferably a plurality of injection openings 23 at its end region facing the combustion chamber of the cylinder of the internal combustion engine 10.
  • the injection valve member 22 has, for example, an approximately conical sealing surface 24 which interacts with a valve seat 25 formed in the valve body 21, from which the injection openings 23 lead away.
  • a fuel injector 20 that is one in one Has valve body 21 axially displaceably guided injection valve member 22.
  • the valve body 21 has at least one, preferably a plurality of injection openings 23 at its end region facing the combustion chamber of the cylinder of the internal combustion engine 10.
  • the injection valve member 22 has, for example, an approximately conical sealing surface 24 which interacts with a valve seat 25 formed in the valve body 21, from which the injection openings 23 lead away.
  • a valve seat 25 formed in the valve body 21, from which the injection openings 23 lead away.
  • Injection valve member 22 formed annular space 26 which is connected to the pump work chamber 18.
  • the injection valve member 22 has a pressure shoulder 27 arranged in the annular space 26, via which the pressure prevailing in the annular space 26 has a pressure in the opening direction 28 of the
  • Injection valve member 22 exerts force on this.
  • the injection valve member 22 is acted upon by a force generated by a prestressed compression spring 29 in the closing direction, that is to say counter to the opening direction 28.
  • the injection valve member 22 can be moved against the force of the closing spring 29 in the opening direction 28 and thereby opens the injection openings 23 through which fuel is injected into the combustion chamber of the internal combustion engine 10.
  • the injection valve member 22 is pressed in the closing direction with its sealing surface 24 into the valve seat 25 on the valve body 21, so that the injection openings 23 are closed.
  • the fuel injection device is explained in more detail below with reference to FIG. 1 in accordance with a first exemplary embodiment.
  • the fuel injector has a control valve device 30 through which a connection of the pump work space 18 is controlled with a relief space 31, the relief space being an area in which low pressure prevails and not the high pressure generated by the pump piston 14.
  • the relief space 31 is, for example, an area that corresponds to a
  • Fuel tank is connected. During the suction stroke of the pump piston 14, fuel is also drawn from the relief chamber into the pump work chamber 18.
  • the control valve device 30 also controls a connection of the pump work chamber 18 to a pressure chamber 32.
  • the pressure prevailing in the pressure chamber 32 acts on a piston 33 which is guided in a longitudinally displaceable manner.
  • the closing spring 29 acting on the injection valve member 22 is supported on the side of the piston 33 remote from the pressure chamber 32.
  • the control valve device 30 has a control valve member 35 which is displaceably guided in the longitudinal direction and which has a first sealing surface 36 in a first longitudinal direction, which is, for example, approximately conical.
  • the sealing surface 36 includes in the longitudinal direction
  • Shaft 37 which is sealingly guided in a bore 38 of a control valve body in a longitudinally displaceable manner.
  • an undercut 39 is formed on the control valve member 35.
  • a connection 40 to the pump work chamber 18 opens into the bore 38 in the area of the undercut 39 of the control valve member 35.
  • a sealing section 36 is adjoined by a cylindrical section 41 of the control valve member 35, which has a larger diameter than the shaft
  • a second sealing surface 42 is arranged at the end region of the section 41 of the control valve member 35 in the longitudinal direction opposite the first sealing surface 36, for example by a sealing surface with the end face of the section 41 connected ball 43 is formed.
  • the diameter of the ball 43 is smaller than the diameter of the section 41.
  • the section 41 and the ball 43 of the control valve member 35 are arranged in a bore section 44 of the control valve body which is enlarged in diameter compared to the bore 38.
  • the transition from the bore section 44 to the bore 38 is, for example, approximately conical and forms a first valve seat 45 with which the first sealing surface 36 of the control valve member 35 cooperates.
  • the bore section 44 merges again into a bore 46 with a smaller diameter, the transition being, for example, approximately conical and forming a second valve seat 47 with which the second sealing surface 42 of the control valve member 35 cooperates.
  • annular shoulder 48 is also formed, between which and the end of the section 41 of the control valve member 35 surrounding the ball 43, a prestressed compression spring 49 is clamped.
  • the compression valve 49 acts on the control valve member 35 with its first sealing surface 36 towards the first valve seat 45.
  • a connection 55 to the pressure chamber 32 opens into the bore section 44.
  • the control valve member 35 has a flange 50. Staggered in the longitudinal direction to the flange 50, a first coil 51 is arranged on one side thereof and a second coil 52 on the other side. The coils 51, 52 are electrically connected to a control device 53.
  • the flange 50 of the control valve member 35 represents a magnet armature and together with the coils 51, 52 each form an electromagnet.
  • the flange 50 is supported from the side facing away from the shaft 37 from a prestressed compression spring 54 which counteracts the compression spring 49 and through which the control valve member 35 is acted upon with its second sealing surface 42 towards the second valve seat 47.
  • both coils 51, 52 are not energized, the control valve member 35 is in a central position shown in FIG. 1, in which both the first sealing surface 36 is lifted off the first valve seat 45 and the second sealing surface 42 is lifted off the second valve seat 47.
  • the pump work chamber 18 is connected by the control valve device 30 both to the relief chamber 31 and to the pressure chamber 32. No high pressure can therefore build up in the pump work chamber 18.
  • the suction stroke of the pump piston 14 it sucks fuel from the relief chamber 31 into the pump working chamber 18. If fuel injection is to begin during the delivery stroke of the pump piston 14, the first coil 51 is energized so that the flange 50 is attracted by the coil 51 against the force of the compression spring 54.
  • the control valve member 35 is brought into contact with the first valve seat 45 with its first sealing surface 36 and the pump work chamber 18 is thus separated from the relief chamber 31 and from the pressure chamber 32.
  • High pressure builds up in the pump work chamber 18, which also acts in the annular chamber 26 of the fuel injection valve 20 and opens it.
  • the first coil 51 is no longer energized and instead the second coil 52 is energized, so that the flange 50 of the
  • Control valve member 35 is attracted to the second coil 52.
  • the control valve member 35 is supported by the force of the compression spring 50 and against the compression spring 49 with its second first sealing surface 42 in contact with the second valve seat 47, so that the pump working space 18 is connected to the pressure chamber 32 and is separated from the relief chamber 31.
  • the high pressure of the pump working chamber 18 thus acts in the pressure chamber 32 and acts on the piston 33, which in turn increases the force of the closing spring 29 and thereby closes the fuel injection valve 20.
  • the second coil 52 is no longer energized and instead the first coil 51 is energized again, so that the control valve member 35 rests with its first sealing surface 36 on the first valve seat 45 and separates the pressure chamber 32 from the pump work chamber 18.
  • both coils 51, 52 are not energized, so that the control valve member 35 is in its central position and the pump work chamber 18 is connected to the relief chamber 31, so that high pressure can no longer build up in the pump work chamber 18 and the fuel injection valve through the force of the closing spring 29 acting on the injection valve member 22 is closed.
  • An interruption of the fuel injection caused by the control valve device 30 as explained above can be provided to achieve a pre-injection of a small amount of fuel before the injection of a larger main injection amount and / or to achieve a post-injection of a small amount of fuel after the injection of a larger main injection amount.
  • FIGS. 2 to 4 show the fuel injection device according to a second exemplary embodiment, essentially only the control valve device 130 being modified compared to the first exemplary embodiment.
  • the control valve device 130 connects the pump work chamber 18 to the relief chamber 31 and connects the pump work chamber 18 to the pressure chamber 32 controlled.
  • the control valve device 130 has two separate control valve members 160, 180, which are arranged offset coaxially to one another in the longitudinal direction and are guided so as to be displaceable in the longitudinal direction.
  • the connection of the pump work chamber 18 to the relief chamber 31 is controlled by a first control valve member 160.
  • the first control valve member 160 has a shaft 161, with which it is guided in a bore 162 of a control valve body so as to be sealingly displaceable in the longitudinal direction.
  • Adjoining the stem 161 is, for example, an approximately conical first sealing surface 163, which is arranged at the transition of the control valve member 160 from the stem 161 to a section 164 of larger diameter.
  • An undercut 167 is formed on the control valve member 160 between the stem 161 and the sealing surface 163.
  • the section 164 of the control valve member 160 is arranged in a bore section 165 of the control valve body with a larger diameter than the bore 162.
  • an approximately conical first valve seat 166 is formed, with which the first sealing surface 163 of the first control valve member 160 interacts.
  • a connection 168 to the pump work chamber 18 opens into the bore 162 and a connection to the relief chamber 31 opens in the bore section 165
  • a prestressed compression spring 169 is arranged, through which the control valve member 160 is acted upon with its sealing surface 163 towards the valve seat 166.
  • the second control valve member 180 has a shaft 181 projecting into the bore 162, to which a section 182 with a larger diameter adjoins the first control valve member 160 and which has a larger diameter compared to the bore 162 enlarged bore section 183 is arranged. Section 182 is followed by a second shaft 184 of no diameter on the second control valve member 180, which is sealingly guided in a bore 185 of the control valve body.
  • An approximately conical second sealing surface 186 is formed at the transition from section 182 to shaft 184, and an undercut 187 is formed between this and shaft 184.
  • an approximately conical second valve seat 189 is formed at the transition from the bore section 183 to the bore 185.
  • a prestressed compression spring 190 is arranged, through which the control valve member 180 is acted upon by its sealing surface 186 towards the valve seat 189.
  • a connection 191 to the pump work chamber 18 opens into the bore 185.
  • a connection 192 with the pressure chamber 32 opens into the bore section 183.
  • a stem portion 194 with an enlarged diameter is formed at the end of the stem 184 of the second control valve member 180 facing away from the sealing surface 186.
  • the shaft section 194 is guided in a cylinder 195 so as to be tightly displaceable.
  • a prestressed compression spring 196 is arranged between the end of the cylinder 195 and the end face of the shaft section 194 facing it, which counteracts the force of the compression spring 190.
  • annular surface 197 facing away from the compression spring 196 is formed.
  • the end region of the second control valve member 180 with the annular surface 197 is arranged in a control pressure chamber 198.
  • the annular surface 197 of the control valve member 180 is from the control pressure prevailing in the control pressure chamber 198 applied, which exerts a force counteracting the compression spring 196 on the control valve member 180.
  • the control pressure in the control pressure chamber 198 is determined by an actuator 199, which is a piezo actuator, for example.
  • the piezo actuator 199 is connected to an electrical control device 200, by which the level of an electrical voltage applied to the piezo actuator 199 is determined.
  • the length of the piezo actuator 199 and thus the control pressure in the control pressure chamber 198 change.
  • the piezo actuator 199 can determine the control pressure in the control pressure chamber 198 by means of a hydraulic ratio, which makes it possible that even with small changes the Length of the piezo actuator 199 can cause relatively large changes in the control pressure. If by the control device 200 no electrical
  • Pump piston 14 has no voltage applied to piezo actuator 199 by control device 200, and control valve device 130 is in a first switching position shown in FIG. 2.
  • the second control valve member 180 is the force of
  • Compression spring 196 against the force of the compression spring 190 with its second sealing surface 186 is lifted off the second valve seat 189 with a stroke h2.
  • the end of its stem 181 abuts the second control valve member 180 against the front end of the stem 161 of the first control valve member 160 and moves it against the force of the compression spring 169, so that the first control valve member 160 is lifted with its first sealing surface 163 from the first valve seat 166 with a stroke hl.
  • the force exerted by the compression spring 196 on the second control valve member 180 and, via this, also on the first control valve member 160 is thus greater than the sum of the force exerted by the compression spring 169 on the first control valve member 160 and the force exerted by the compression spring 190 on the second control valve member 180 exerted force.
  • the pump piston 14 can draw fuel into the pump work chamber 18 from the relief chamber 31 through the bore section 165 around the first control valve member 160 and through the connection 168.
  • the point in time at which fuel injection begins during the delivery stroke of the pump piston 14 is determined by the control device 200 by applying a voltage to the piezo actuator 199 and the control valve device 130 being in a second switching position shown in FIG. 3.
  • the control pressure in the control pressure chamber 198 is increased so that a pressure force acts on the second control valve member 180 in addition to the force of the compression spring 190 against the force of the compression spring 196.
  • the second control valve member 180 thus moves in the longitudinal direction until it comes to rest with its second sealing surface 186 on the second valve seat 189, so that the pump working chamber 18 is separated from the pressure chamber 32.
  • the first control valve member 160 also causes the compression spring 169 acting on it to move in the longitudinal direction until it is at its first
  • Sealing surface 163 comes to rest on the first valve seat 166, so that the pump working chamber 18 is also separated from the relief chamber 31.
  • high pressure builds up in the pump work chamber 18, through which the Fuel injection valve 20 is opened and fuel is injected into the combustion chamber of the internal combustion engine.
  • the end face of the stem 181 of the second control valve member 180 is not on the end face of the stem 161 of the first control valve member 160, but there is a distance a between them.
  • the control device 200 reduces the electrical voltage applied to the piezo actuator 199, but does not reduce it to zero, and the control valve device 130 is in a third switching position shown in FIG. 4.
  • the control pressure in the control pressure chamber 198 is thereby reduced, so that the force exerted by the compression spring 196 on the second control valve member 180 is greater than the force exerted by the compression spring 190 and the control pressure.
  • the second control valve member 180 then moves in the longitudinal direction and lifts with its second sealing surface 186 from the second valve seat 189 and travels through a stroke h3 corresponding approximately to the distance a from the first control valve member 160.
  • the force exerted by the compression spring 196 is not sufficient to to move the first control valve member 160 against the force of the compression spring 169 in the opening direction so that it remains in contact with the first valve seat 166 with its first sealing surface 163 and does not open a connection to the relief chamber 31.
  • the pump work chamber 18 is thus connected to the pressure chamber 32 via the opened second control valve member 180, so that high pressure prevails there.
  • the control device 200 increases the electrical voltage applied to the piezo actuator 199 again, so that the second control valve member 180 moves in the longitudinal direction by the force of the compression spring 190 and the force caused by the control pressure and comes with its second sealing surface 186 to the second valve seat 189 and the control valve device 130 is again in its second switching position according to FIG. 3.
  • the pressure chamber 32 is then preferably connected to the relief chamber 31 in order to relieve it and to open the
  • connection of the pressure chamber 32 to the relief chamber 31 can preferably be controlled by the second control valve member 180.
  • Fuel injection valve 20 are closed by bringing the control valve device 130 into its third switching position shown in FIG. 4, in which the pressure chamber 32 is connected to the pump work chamber 18 by the second control valve member 180.
  • the fuel injection valve 20 can then be used for another fuel injection, for example one
  • the control device 200 After injection, can be opened again by bringing the control valve device 130 into its switching position shown in FIG. 3 and the pressure chamber 32 again being separated from the pump work chamber 18 by the second control valve member 180 and being connected to the relief chamber 31.
  • the control device 200 no longer applies any electrical voltage to the piezo actuator 199, so that the compression spring 196 both lifts the second control valve member 180 with its second sealing surface 186 from the second valve seat 189 and also the first control valve member 160 with its first sealing surface 163 is lifted from the first valve seat 166.
  • the switching position of the control valve device 130 according to FIG. 3 in its open position in the third switching position of the control valve device 130 according to FIG. 4 in the longitudinal direction is smaller by the distance a than the stroke that the second control valve member 180 from its closed position in the second and third switching position 3 and FIG. 4 in its open position in the switching position of the control valve device 130 according to FIG. 2 in the longitudinal direction.
  • the cylinder 16 with the pump piston 14 and the pump work chamber 18, the fuel injection valve 20 and the control valve device 30 according to the first exemplary embodiment and the control valve device 130 according to the second exemplary embodiment preferably form a common structural unit as a pump-nozzle unit.

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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)
  • Electromagnetism (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

The fuel injection device comprises a pump working chamber (18), defined by a pump piston (14), which may be filled with fuel through a connection, controlled by a control valve device (30; 130) and which may be connected to a discharge chamber (31). The pump working chamber (18) is separated from the discharge chamber (31) during each fuel injection by means of the control valve device (30; 130) and connected to the discharge chamber (31), by means of the control valve device (30; 130), in order to end the fuel injection. Furthermore, to interrupt a fuel injection, a connection of the pump working chamber (18) to a pressure chamber (32) of the injection valve member (22) is controlled by means of the control valve device (30; 130), whereby the injection valve member (22) is at least indirectly pressurised by the pressure in the pressure chamber (32) in the closing direction.

Description

Kraftstoffeinspritzeinrichtung für eine BrennkraftmaschineFuel injection device for an internal combustion engine
Stand der TechnikState of the art
Die Erfindung geht aus von einer Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine nach der Gattung des Anspruchs 1.The invention relates to a fuel injection device for an internal combustion engine according to the preamble of claim 1.
Eine solche Kraftstoffeinspritzeinrichtung ist durch die DE 198 35 494 AI bekannt. Diese Kraftstoffeinspritzeinrichtung weist einen von einemSuch a fuel injection device is known from DE 198 35 494 AI. This fuel injector has one of one
Pumpenkolben begrenzten Pumpenarbeitsraum auf, der über eine durch eine Steuerventileinrichtung gesteuerte Verbindung mit Kraftstoff befüllbar ist und mit einem Entlastungsraum verbindbar ist. Während einer jeweiligen Kraftstoffeinspritzung ist der Pumpenarbeitsraum durch diePump piston limited pump work space that can be filled with fuel via a connection controlled by a control valve device and can be connected to a relief chamber. During a respective fuel injection, the pump work space is closed
Steuerventileinrichtung vom Entlastungsraum getrennt und zur Beendigung der Kraftstoffeinspritzung ist der Pumpenarbeitsraum durch die Steuerventileinrichtung mit dem Entlastungsraum verbunden. Die Kraftstoffeinspritzeinrichtung weist außerdem einControl valve device separated from the relief chamber and the pump work chamber is connected to the relief chamber by the control valve device to end the fuel injection. The fuel injector also has
Kraftstoffeinspritzventil mit einem Einspritzventilglied auf, das wenigstens eine Einspritzöffnung steuert und das vom im Pumpenarbeitsraum herrschenden Druck in Öffnungsrichtung und durch eine Schließkraft in Schließrichtung beaufschlagt ist. Das Schließen desFuel injection valve with an injection valve member which controls at least one injection opening and which is acted upon by the pressure prevailing in the pump work space in the opening direction and by a closing force in the closing direction. Closing the
Kraftstoffeinspritzventils erfolgt bei der Entlastung des Pumpenarbeitsraums über die Steuerventileinrichtung in den Entlastungsraum durch die auf das Einspritzventilglied wirkende Schließkraft. Ein kurzzeitiges Schließen und Wiederöffnen des Kraftstoffeinspritzventils ist hierbei nur schwer möglich, da sich der Druck im Pumpenarbeitsraum nur verzögert abbaut und wieder aufbaut . Ein kurzzeitiges Schließen und Wiederöffnen des Kraftstoffeinspritzventils ist für eine Voreinspritzung und/oder eine Nacheinspritzung einer geringen Menge von Kraftstoff vor bzw. nach der Haupteinspritzung einer großen Kraftstoffmenge vorteilhaft im Hinblick auf die Schadstoffemission und die Geräuschentwicklung der Brennkraftmaschine.Fuel injection valve takes place when the pump work chamber is relieved via the control valve device into the relief chamber by means of the injection valve member effective closing force. Short-term closing and reopening of the fuel injection valve is difficult here, since the pressure in the pump workspace only decreases and builds up again after a delay. A brief closing and reopening of the fuel injection valve is advantageous for a pre-injection and / or a post-injection of a small amount of fuel before or after the main injection of a large amount of fuel with regard to the pollutant emission and the noise development of the internal combustion engine.
Vorteile der ErfindungAdvantages of the invention
Die erfindungsgemäße Kraftstoffeinspritzeinrichtung mit den Merkmalen gemäß Anspruch 1 hat demgegenüber den Vorteil, daß durch die Steuerventileinrichtung dasThe fuel injection device according to the invention with the features of claim 1 has the advantage that the control valve means
Kraftstoffeinspritzventil mittels des im Pumpenarbeitsraum herrschenden Druckes zu einer Unterbrechung der Kraftstoffeinspritzung kurzzeitig geschlossen werden kann. Das Einspritzventilglied wird dabei zusätzlich zu derFuel injection valve can be closed briefly by means of the pressure prevailing in the pump work space to interrupt the fuel injection. The injection valve member is in addition to
Schließkraft durch den im Pumpenarbeitsraum herrschenden Druck in Schließrichtung beaufschlagt, so daß das Kraftstoffeinspritzventil schnell schließt . Die erfindungsgemäße Kraftstoffeinspritzeinrichtung ermöglicht somit eine Voreinspritzung und/oder eine Nacheinspritzung einer geringen Kraftstoffmenge .Closing force is acted upon by the pressure prevailing in the pump work chamber in the closing direction, so that the fuel injection valve closes quickly. The fuel injection device according to the invention thus enables a pre-injection and / or a post-injection of a small amount of fuel.
In den abhängigen Ansprüchen sind vorteilhafte Ausgestaltungen und Weiterbildungen der erfindungsgemäßen Kraftstoffeinspritzeinrichtung angegeben. Die Ausbildung gemäß Anspruch 4 ermöglicht eine schneilschaltende und einfach aufgebaute Steuerventileinrichtung. ZeichnungAdvantageous refinements and developments of the fuel injection device according to the invention are specified in the dependent claims. The embodiment according to claim 4 enables a quick-switching and simply constructed control valve device. drawing
Zwei Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 eineTwo embodiments of the invention are shown in the drawing and explained in more detail in the following description. 1 shows a
Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine in schematischer Darstellung gemäß einem ersten Ausführungsbeispiel, Figur 2 die Kraftstoffeinspritzeinrichtung mit einer Steuerventileinrichtung gemäß einem zweitenFuel injection device for an internal combustion engine in a schematic representation according to a first embodiment, Figure 2 shows the fuel injection device with a control valve device according to a second
Ausführungsbeispiel in einer ersten Schaltstellung, Figur 3 die Steuerventileinrichtung von Figur 2 in einer zweiten Schaltstellung und Figur 4 die Steuerventileinrichtung von Figur 2 in einer dritten Schaltstellung.Embodiment in a first switching position, Figure 3 shows the control valve device of Figure 2 in a second switching position and Figure 4 shows the control valve device of Figure 2 in a third switching position.
Beschreibung der AusführungsbeispieleDescription of the embodiments
In den Figuren 1 und 2 ist eine Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine 10, insbesondere eine selbstzündende Brennkraftmaschine eines Kraftfahrzeugs dargestellt. Die1 and 2 show a fuel injection device for an internal combustion engine 10, in particular a self-igniting internal combustion engine of a motor vehicle. The
Kraftstoffeinspritzeinrichtung ist als sogenannte Pumpe- Düse-Einheit ausgebildet, wobei für jeden Zylinder der Brennkraftmaschine 10 eine separate Pumpe-Düse-Einheit vorgesehen ist. Die Brennkraftmaschine 10 weist eineFuel injection device is designed as a so-called pump nozzle unit, with a separate pump nozzle unit being provided for each cylinder of internal combustion engine 10. The internal combustion engine 10 has one
Nockenwelle mit Nocken 12 auf, über die ein Pumpenkolben 14 der Kraftstoffeinspritzeinrichtung in einer Hubbewegung angetrieben wird. Der Pumpenkolben 14 ist in einer Bohrung 16 dichtend geführt und begrenzt in der Bohrung 16 einen Pumpenarbeitsraum 18 begrenzt. Der Pumpenkolben 14 wird durch eine vorgespannte Druckfeder 15 in Anlage am Nocken 12 gehalten.Camshaft with cams 12, via which a pump piston 14 of the fuel injection device is driven in one stroke movement. The pump piston 14 is sealingly guided in a bore 16 and delimits a pump working space 18 in the bore 16. The pump piston 14 is held in contact with the cam 12 by a prestressed compression spring 15.
Die Kraftstoffeinspritzeinrichtung weist außerdem ein Kraftstoffeinspritzventil 20 auf, das ein in einem Ventilkörper 21 axial verschiebbar geführtes Einspritzventilglied 22 aufweist. Der Ventilkörper 21 weist an seinem dem Brennraum des Zylinders der Brennkraftmaschine 10 zugewandten Endbereich wenigstens eine, vorzugsweise mehrere Einspritzöffnungen 23 auf. Das Einspritzventilglied 22 weist an seinem dem Brennraum zugewandten Endbereich eine beispielsweise etwa kegelförmige Dichtfläche 24 auf, die mit einem im Ventilkörper 21 ausgebildeten Ventilsitz 25 zusammenwirkt, von dem aus die Einspritzöffnungen 23 abführen. Im Ventilkörper 21 ist ein dasThe fuel injector also includes a fuel injector 20 that is one in one Has valve body 21 axially displaceably guided injection valve member 22. The valve body 21 has at least one, preferably a plurality of injection openings 23 at its end region facing the combustion chamber of the cylinder of the internal combustion engine 10. At its end region facing the combustion chamber, the injection valve member 22 has, for example, an approximately conical sealing surface 24 which interacts with a valve seat 25 formed in the valve body 21, from which the injection openings 23 lead away. In the valve body 21 is a
Einspritzventilglied 22 umgebender Ringraum 26 ausgebildet, der mit dem Pumpenarbeitsraum 18 verbunden ist . Das Einspritzventilglied 22 weist eine im Ringraum 26 angeordnete Druckschulter 27 auf, über die der im Ringraum 26 herrschende Druck eine in Öffnungsrichtung 28 desInjection valve member 22 formed annular space 26 which is connected to the pump work chamber 18. The injection valve member 22 has a pressure shoulder 27 arranged in the annular space 26, via which the pressure prevailing in the annular space 26 has a pressure in the opening direction 28 of the
Einspritzventilglieds 22 wirkende Kraft auf dieses ausübt. Das Einspritzventilglied 22 ist durch eine von einer vorgespannten Druckfeder 29 erzeugte Kraft in Schließrichtung, das heißt entgegen der Öffnungsrichtung 28, beaufschlagt. Durch den vom Pumpenkolben 14 imInjection valve member 22 exerts force on this. The injection valve member 22 is acted upon by a force generated by a prestressed compression spring 29 in the closing direction, that is to say counter to the opening direction 28. By the pump piston 14 in the
Pumpenarbeitsraum 18 beim Förderhub erzeugten Druck, der auch im Ringraum 26 herrscht, ist das Einspritzventilglied 22 gegen die Kraft der Schließfeder 29 in Öffnungsrichtung 28 bewegbar und gibt dabei die Einspritzöffnungen 23 frei, durch die Kraftstoff in den Brennraum der Brennkraftmaschine 10 eingespritzt wird. Zur Beendigung derPump work chamber 18 pressure generated during the delivery stroke, which also prevails in the annular space 26, the injection valve member 22 can be moved against the force of the closing spring 29 in the opening direction 28 and thereby opens the injection openings 23 through which fuel is injected into the combustion chamber of the internal combustion engine 10. To end the
Kraftstoffeinspritzung wird das Einspritzventilglied 22 in Schließrichtung mit seiner Dichtfläche 24 in den Ventilsitz 25 am Ventilkörper 21 gepresst, so daß die Einspritzöffnungen 23 verschlossen werden.Fuel injection, the injection valve member 22 is pressed in the closing direction with its sealing surface 24 into the valve seat 25 on the valve body 21, so that the injection openings 23 are closed.
Nachfolgend wird die Kraftstoffeinspritzeinrichtung anhand Figur 1 gemäß einem ersten Ausführungsbeispiel näher erläutert. Die Kraftstoffeinspritzeinrichtung weist eine Steuerventileinrichtung 30 auf, durch die eine Verbindung des Pumpenarbeitsraums 18 mit einem Entlastungsraum 31 gesteuert wird, wobei der Entlastungsraum ein Bereich ist, in dem Niederdruck und nicht der durch den Pumpenkolben 14 erzeugte Hochdruck herrscht. Der Entlastungsraum 31 ist beispielsweise ein Bereich, der mit einemThe fuel injection device is explained in more detail below with reference to FIG. 1 in accordance with a first exemplary embodiment. The fuel injector has a control valve device 30 through which a connection of the pump work space 18 is controlled with a relief space 31, the relief space being an area in which low pressure prevails and not the high pressure generated by the pump piston 14. The relief space 31 is, for example, an area that corresponds to a
Kraftstoffvorratstank verbunden ist. Aus dem Entlastungsraum erfolgt beim Saughub des Pumpenkolbens 14 auch eine Ansaugung von Kraftstoff in den Pumpenarbeitsraum 18. Durch die Steuerventileinrichtung 30 wird außerdem eine Verbindung des Pumpenarbeitsraums 18 mit einem Druckraum 32 gesteuert. Der im Druckraum 32 herrschende Druck beaufschlagt einen längsverschiebbar geführten Kolben 33. An der dem Druckraum 32 abgewandten Seite des Kolbens 33 stützt sich die auf das Einspritzventilglied 22 wirkende Schließfeder 29 ab.Fuel tank is connected. During the suction stroke of the pump piston 14, fuel is also drawn from the relief chamber into the pump work chamber 18. The control valve device 30 also controls a connection of the pump work chamber 18 to a pressure chamber 32. The pressure prevailing in the pressure chamber 32 acts on a piston 33 which is guided in a longitudinally displaceable manner. The closing spring 29 acting on the injection valve member 22 is supported on the side of the piston 33 remote from the pressure chamber 32.
Die Steuerventileinrichtung 30 weist ein in Längsrichtung verschiebbar geführtes Steuerventilglied 35 auf, das in einer ersten Längsrichtung eine erste Dichtfläche 36 aufweist, die beispielsweise etwa konisch ausgebildet ist. An die Dichtfläche 36 schließt sich in Längsrichtung einThe control valve device 30 has a control valve member 35 which is displaceably guided in the longitudinal direction and which has a first sealing surface 36 in a first longitudinal direction, which is, for example, approximately conical. The sealing surface 36 includes in the longitudinal direction
Schaft 37 an, der in einer Bohrung 38 eines Steuerventilkörpers dichtend längsverschiebbar geführt ist. Am Übergang von der Dichtfläche 36 zum Schaft 37 ist ein Freistich 39 am Steuerventilglied 35 ausgebildet. In die Bohrung 38 mündet im Bereich des Freistichs 39 des Steuerventilglieds 35 eine Verbindung 40 zum Pumpenarbeitsraum 18. Auf der dem Schaft 37 gegenüberliegenden Seite schließt sich an die Dichtfläche 36 ein zylinderischer Abschnitt 41 des Steuerventilglieds 35 an, der einen größeren Durchmesser aufweist als der SchaftShaft 37, which is sealingly guided in a bore 38 of a control valve body in a longitudinally displaceable manner. At the transition from the sealing surface 36 to the shaft 37, an undercut 39 is formed on the control valve member 35. A connection 40 to the pump work chamber 18 opens into the bore 38 in the area of the undercut 39 of the control valve member 35. On the side opposite the shaft 37, a sealing section 36 is adjoined by a cylindrical section 41 of the control valve member 35, which has a larger diameter than the shaft
37. Am Endbereich des Abschnitts 41 des Steuerventilglieds 35 ist in der der ersten Dichtfläche 36 entgegengesetzten Längsrichtung eine zweite Dichtfläche 42 angeordnet, die beispielsweise durch eine mit der Stirnseite des Abschnitts 41 verbundene Kugel 43 gebildet ist. Der Durchmesser der Kugel 43 ist kleiner als der Durchmesser des Abschnitts 41.37. A second sealing surface 42 is arranged at the end region of the section 41 of the control valve member 35 in the longitudinal direction opposite the first sealing surface 36, for example by a sealing surface with the end face of the section 41 connected ball 43 is formed. The diameter of the ball 43 is smaller than the diameter of the section 41.
Der Abschnitt 41 und die Kugel 43 des Steuerventilglieds 35 sind in einem im Durchmesser gegenüber der Bohrung 38 vergrößerten Bohrungsabschnitt 44 des Steuerventilkörpers angeordnet . Der Übergang vom Bohrungsabschnitt 44 zur Bohrung 38 ist beispielsweise annähernd konisch ausgebildet und bildet einen ersten Ventilsitz 45, mit dem die erste Dichtfläche 36 des Steuerventilglieds 35 zusammenwirkt. An seinem der Bohrung 38 abgewandten Ende geht der Bohrungsabschnitt 44 wieder in eine Bohrung 46 mit kleinerem Durchmesser über, wobei der Übergang beispielsweise annähernd konisch ausgebildet ist und einen zweiten Ventilsitz 47 bildet, mit dem die zweite Dichtfläche 42 des Steuerventilglieds 35 zusammenwirkt. Am Ende des Bohrungsabschnitts 44 am zweiten Ventilsitz 47 ist außerdem eine Ringschulter 48 gebildet, zwischen der und der die Kugel 43 umgebenden Stirnseite des Abschnitts 41 des Steuerventilglieds 35 eine vorgespannte Druckfeder 49 eingespannt ist. Durch die Druckfeder 49 wird das Steuerventilglied 35 mit seiner ersten Dichtfläche 36 zum ersten Ventilsitz 45 hin beaufschlagt. In den Bohrungsabschnitt 44 mündet eine Verbindung 55 zum Druckraum 32.The section 41 and the ball 43 of the control valve member 35 are arranged in a bore section 44 of the control valve body which is enlarged in diameter compared to the bore 38. The transition from the bore section 44 to the bore 38 is, for example, approximately conical and forms a first valve seat 45 with which the first sealing surface 36 of the control valve member 35 cooperates. At its end facing away from the bore 38, the bore section 44 merges again into a bore 46 with a smaller diameter, the transition being, for example, approximately conical and forming a second valve seat 47 with which the second sealing surface 42 of the control valve member 35 cooperates. At the end of the bore section 44 on the second valve seat 47, an annular shoulder 48 is also formed, between which and the end of the section 41 of the control valve member 35 surrounding the ball 43, a prestressed compression spring 49 is clamped. The compression valve 49 acts on the control valve member 35 with its first sealing surface 36 towards the first valve seat 45. A connection 55 to the pressure chamber 32 opens into the bore section 44.
Im dem Freistich 39 abgewandten Endbereich des Schafts 37 weist das Steuerventilglied 35 einen Flansch 50 auf. In Längsrichtung zum Flansch 50 versetzt ist auf einer Seite von diesem eine erste Spule 51 und auf der anderen Seite eine zweite Spule 52 angeordnet. Die Spulen 51,52 sind elektrisch mit einer Steuereinrichtung 53 verbunden. Der Flansch 50 des Steuerventilglieds 35 stellt einen Magnetanker dar und bildet zusammen mit den Spulen 51,52 jeweils einen Elektromagneten. Am Flansch 50 stützt sich auf der dem Schaft 37 abgewandten Seite eine vorgespannte Druckfeder 54 ab, die der Druckfeder 49 entgegenwirkt und durch die das Steuerventilglied 35 mit seiner zweiten Dichtfläche 42 zum zweiten Ventilsitz 47 hin beaufschlagt ist.In the end region of the shaft 37 facing away from the undercut 39, the control valve member 35 has a flange 50. Staggered in the longitudinal direction to the flange 50, a first coil 51 is arranged on one side thereof and a second coil 52 on the other side. The coils 51, 52 are electrically connected to a control device 53. The flange 50 of the control valve member 35 represents a magnet armature and together with the coils 51, 52 each form an electromagnet. The flange 50 is supported from the side facing away from the shaft 37 from a prestressed compression spring 54 which counteracts the compression spring 49 and through which the control valve member 35 is acted upon with its second sealing surface 42 towards the second valve seat 47.
Wenn beide Spulen 51,52 nicht bestromt sind, so befindet sich das Steuerventilglied 35 in einer in Figur 1 dargestellten Mittelstellung, in der sowohl die erste Dichtfläche 36 vom ersten Ventilsitz 45 abgehoben ist als auch die zweite Dichtfläche 42 vom zweiten Ventilsitz 47 abgehoben ist . Der Pumpenarbeitsraum 18 ist durch die Steuerventileinrichtung 30 sowohl mit dem Entlastungsraum 31 als auch mit dem Druckraum 32 verbunden. Im Pumpenarbeitsraum 18 kann sich somit kein Hochdruck aufbauen. Beim Saughub des Pumpenkolbens 14 saugt dieser aus dem Entlastungsraum 31 Kraftstoff in den Pumpenarbeitsraum 18 an. Wenn beim Förderhub des Pumpenkolbens 14 die Kraftstoffeinspritzung beginnen soll, so wird die erste Spule 51 bestromt, so daß der Flansch 50 gegen die Kraft der Druckfeder 54 von der Spule 51 angezogen wird. Hierdurch wird das Steuerventilglied 35 mit seiner ersten Dichtfläche 36 in Anlage am ersten Ventilsitz 45 gebracht und somit der Pumpenarbeitsraum 18 vom Entlastungsraum 31 und vom Druckraum 32 getrennt. Im Pumpenarbeitsraum 18 baut sich hierdurch Hochdruck auf, der auch im Ringraum 26 des Kraftstoffeinspritzventils 20 wirkt und dieses öffnet. Zu einer Unterbrechung der Kraftstoffeinspritzung wird die erste Spule 51 nicht mehr bestromt und stattdessen die zweite Spule 52 bestromt, so daß der Flansch 50 desIf both coils 51, 52 are not energized, the control valve member 35 is in a central position shown in FIG. 1, in which both the first sealing surface 36 is lifted off the first valve seat 45 and the second sealing surface 42 is lifted off the second valve seat 47. The pump work chamber 18 is connected by the control valve device 30 both to the relief chamber 31 and to the pressure chamber 32. No high pressure can therefore build up in the pump work chamber 18. During the suction stroke of the pump piston 14, it sucks fuel from the relief chamber 31 into the pump working chamber 18. If fuel injection is to begin during the delivery stroke of the pump piston 14, the first coil 51 is energized so that the flange 50 is attracted by the coil 51 against the force of the compression spring 54. As a result, the control valve member 35 is brought into contact with the first valve seat 45 with its first sealing surface 36 and the pump work chamber 18 is thus separated from the relief chamber 31 and from the pressure chamber 32. High pressure builds up in the pump work chamber 18, which also acts in the annular chamber 26 of the fuel injection valve 20 and opens it. To interrupt the fuel injection, the first coil 51 is no longer energized and instead the second coil 52 is energized, so that the flange 50 of the
Steuerventilglieds 35 von der zweiten Spule 52 angezogen wird. Hierdurch wird das Steuerventilglied 35 unterstützt durch die Kraft der Druckfeder 50 und gegen die Druckfeder 49 mit seiner zweiten ersten Dichtfläche 42 in Anlage am zweiten Ventilsitz 47 gebracht, so daß der Pumpenarbeitsraum 18 mit dem Druckraum 32 verbunden und vom Entlastungsraum 31 getrennt ist. Somit herrscht im Druckraum 32 der Hochdruck des Pumpenarbeitsraum 18, der auf den Kolben 33 wirkt, wodurch wiederum die Kraft der Schließfeder 29 erhöht und dadurch das Kraftstoffeinspritzventil 20 geschlossen wird. Zu einer weiteren Kraftstoffeinspritzung wird die zweite Spule 52 nicht mehr bestromt und stattdessen wieder die erste Spule 51 bestromt, so daß das Steuerventilglied 35 mit seiner ersten Dichtfläche 36 wieder am ersten Ventilsitz 45 anliegt und den Druckraum 32 vom Pumpenarbeitsraum 18 trennt. Zur Beendigung der Kraftstoffeinspritzung werden beide Spulen 51,52 nicht bestromt, so daß sich das Steuerventilglied 35 in seiner Mittelstellung befindet und der Pumpenarbeitsraum 18 mit dem Entlastungsraum 31 verbunden ist, so daß sich im Pumpenarbeitsraum 18 kein Hochdruck mehr aufbauen kann und das Kraftstoffeinspritzventil durch die auf das Einspritzventilglied 22 wirkende Kraft der Schließfeder 29 geschlossen wird. Eine wie vorstehend erläutert durch die Steuerventileinrichtung 30 bewirkte Unterbrechung der Kraftstoffeinspritzung kann zur Erzielung einer Voreinspritzung einer geringen Kraftstoffmenge vor der Einspritzung einer größeren Haupteinspritzmenge und/oder zur Erzielung einer Nacheinspritzung einer geringen Kraftstoffmenge nach der Einspritzung einer größeren Haupteinspritzmenge vorgesehen werden.Control valve member 35 is attracted to the second coil 52. As a result, the control valve member 35 is supported by the force of the compression spring 50 and against the compression spring 49 with its second first sealing surface 42 in contact with the second valve seat 47, so that the pump working space 18 is connected to the pressure chamber 32 and is separated from the relief chamber 31. The high pressure of the pump working chamber 18 thus acts in the pressure chamber 32 and acts on the piston 33, which in turn increases the force of the closing spring 29 and thereby closes the fuel injection valve 20. For a further fuel injection, the second coil 52 is no longer energized and instead the first coil 51 is energized again, so that the control valve member 35 rests with its first sealing surface 36 on the first valve seat 45 and separates the pressure chamber 32 from the pump work chamber 18. To end the fuel injection, both coils 51, 52 are not energized, so that the control valve member 35 is in its central position and the pump work chamber 18 is connected to the relief chamber 31, so that high pressure can no longer build up in the pump work chamber 18 and the fuel injection valve through the force of the closing spring 29 acting on the injection valve member 22 is closed. An interruption of the fuel injection caused by the control valve device 30 as explained above can be provided to achieve a pre-injection of a small amount of fuel before the injection of a larger main injection amount and / or to achieve a post-injection of a small amount of fuel after the injection of a larger main injection amount.
In den Figuren 2 bis 4 ist die Kraftstoffeinspritzeinrichtung gemäß einem zweiten Ausführungsbeispiel dargestellt, wobei gegenüber dem ersten Ausführungsbeispiel im wesentlichen nur die Steuerventileinrichtung 130 modifiziert ist. Durch die Steuerventileinrichtung 130 wird eine Verbindung des Pumpenarbeitsraums 18 mit dem Entlastungsraum 31 und eine Verbindung des Pumpenarbeitsraums 18 mit dem Druckraum 32 gesteuert. Die Steuerventileinrichtung 130 weist zwei getrennte Steuerventilglieder 160,180 auf, die in Längsrichtung zueinander versetzt koaxial zueinander angeordnet sind und die in Längsrichtung verschiebbar geführt sind. Durch ein erstes Steuerventilglied 160 wird die Verbindung des Pumpenarbeitsraums 18 mit dem Entlastungsräum 31 gesteuert. Das erste Steuerventilglied 160 weist einen Schaft 161 auf, mit dem es in einer Bohrung 162 eines Steuerventilkörpers in Längsrichtung dichtend verschiebbar geführt ist. An den Schaft 161 schließt sich eine beispielsweise annähernd konisch ausgebildete erste Dichtfläche 163 an, die am Übergang des Steuerventilglieds 160 vom Schaft 161 zu einem im Durchmesser größeren Abschnitt 164 angeordnet ist. Zwischen dem Schaft 161 und der Dichtfläche 163 ist am Steuerventilglied 160 ein Freistich 167 ausgebildet. Der Abschnitt 164 des Steuerventilglieds 160 ist in einem Bohrungsabschnitt 165 des Steuerventilkörpers mit gegenüber der Bohrung 162 vergrößertem Durchmesser angeordnet . Am Übergang vom Bohrungsabschnitt 165 zur Bohrung 162 ist ein annähernd konischer erster Ventilsitz 166 ausgebildet, mit dem die erste Dichtfläche 163 des ersten Steuerventilglieds 160 zusammenwirkt. In die Bohrung 162 mündet eine Verbindung 168 zum Pumpenarbeitsraum 18 und im Bohrungsabschnitt 165 mündet eine Verbindung mit dem Entlastungsraum 31. Zwischen demFIGS. 2 to 4 show the fuel injection device according to a second exemplary embodiment, essentially only the control valve device 130 being modified compared to the first exemplary embodiment. The control valve device 130 connects the pump work chamber 18 to the relief chamber 31 and connects the pump work chamber 18 to the pressure chamber 32 controlled. The control valve device 130 has two separate control valve members 160, 180, which are arranged offset coaxially to one another in the longitudinal direction and are guided so as to be displaceable in the longitudinal direction. The connection of the pump work chamber 18 to the relief chamber 31 is controlled by a first control valve member 160. The first control valve member 160 has a shaft 161, with which it is guided in a bore 162 of a control valve body so as to be sealingly displaceable in the longitudinal direction. Adjoining the stem 161 is, for example, an approximately conical first sealing surface 163, which is arranged at the transition of the control valve member 160 from the stem 161 to a section 164 of larger diameter. An undercut 167 is formed on the control valve member 160 between the stem 161 and the sealing surface 163. The section 164 of the control valve member 160 is arranged in a bore section 165 of the control valve body with a larger diameter than the bore 162. At the transition from the bore section 165 to the bore 162, an approximately conical first valve seat 166 is formed, with which the first sealing surface 163 of the first control valve member 160 interacts. A connection 168 to the pump work chamber 18 opens into the bore 162 and a connection to the relief chamber 31 opens in the bore section 165
Grund des Bohrungsabschnitts 165 und der diesem zugewandten Stirnseite des Steuerventilglieds 160 ist eine vorgespannte Druckfeder 169 angeordnet, durch die das Steuerventilglied 160 mit seiner Dichtfläche 163 zum Ventilsitz 166 hin beaufschlagt ist.Due to the bore section 165 and the end face of the control valve member 160 facing it, a prestressed compression spring 169 is arranged, through which the control valve member 160 is acted upon with its sealing surface 163 towards the valve seat 166.
Das zweite Steuerventilglied 180 weist einen in die Bohrung 162 ragenden Schaft 181 auf, an den sich vom ersten Steuerventilglied 160 weg ein Abschnitt 182 mit größerem Durchmesser anschließt, der in einem im Durchmesser gegenüber der Bohrung 162 vergrößerten Bohrungsabschnitt 183 angeordnet ist . An den Abschnitt 182 schließt sich ein am zweiten Steuerventilglied 180 ein weiterer Schaft 184 mit keinerem Durchmesser an, der in einer Bohrung 185 des Steuerventilkörpers dichtend verschiebbar geführt ist. AmThe second control valve member 180 has a shaft 181 projecting into the bore 162, to which a section 182 with a larger diameter adjoins the first control valve member 160 and which has a larger diameter compared to the bore 162 enlarged bore section 183 is arranged. Section 182 is followed by a second shaft 184 of no diameter on the second control valve member 180, which is sealingly guided in a bore 185 of the control valve body. At the
Übergang vom Abschnitt 182 zum Schaft 184 ist eine annähernd konische zweite Dichtfläche 186 ausgebildet und zwischen dieser und dem Schaft 184 ist ein Freistich 187 ausgebildet. Am Übergang vom Bohrungsabschnitt 183 zur Bohrung 185 ist ein annähernd konischer zweiter Ventilsitz 189 ausgebildet. Zwischen einer am Übergang der Bohrung 162 zum Bohrungsabschnitt 183 gebildeten Ringschulter und der dieser zugewandten Stirnseite des Abschnitts 182 des Steuerventilglieds 180 ist eine vorgespannte Druckfeder 190 angeordnet, durch die das Steuerventilglied 180 mit seiner Dichtfläche 186 zum Ventilsitz 189 hin beaufschlagt ist. In die Bohrung 185 mündet im Bereich des Freistichs 187 des Steuerventilglieds 180 eine Verbindung 191 zum Pumpenarbeitsraum 18. In den Bohrungsabschnitt 183 mündet eine Verbindung 192 mit dem Druckraum 32.An approximately conical second sealing surface 186 is formed at the transition from section 182 to shaft 184, and an undercut 187 is formed between this and shaft 184. At the transition from the bore section 183 to the bore 185, an approximately conical second valve seat 189 is formed. Between a ring shoulder formed at the transition from the bore 162 to the bore section 183 and the end face of the section 182 of the control valve member 180 facing this, a prestressed compression spring 190 is arranged, through which the control valve member 180 is acted upon by its sealing surface 186 towards the valve seat 189. In the area 185 of the undercut 187 of the control valve member 180, a connection 191 to the pump work chamber 18 opens into the bore 185. A connection 192 with the pressure chamber 32 opens into the bore section 183.
An dem der Dichtfläche 186 abgewandten Ende des Schafts 184 des zweiten Steuerventilglieds 180 ist ein im Durchmesser vergrößerter Schaftabschnitt 194 ausgebildet. Der Schaftabschnitt 194 ist in einem Zylinder 195 dicht verschiebbar geführt. Zwischen dem Ende des Zylinders 195 und der diesem zugewandten Stirnseite des Schaftabschnitts 194 ist eine vorgespannte Druckfeder 196 angeordnet, die der Kraft der Druckfeder 190 entgegenwirkt. Am Übergang vom Schaft 184 zum Schaftabschnitt 194 ist am SteuerventilgliedAt the end of the stem 184 of the second control valve member 180 facing away from the sealing surface 186, a stem portion 194 with an enlarged diameter is formed. The shaft section 194 is guided in a cylinder 195 so as to be tightly displaceable. A prestressed compression spring 196 is arranged between the end of the cylinder 195 and the end face of the shaft section 194 facing it, which counteracts the force of the compression spring 190. At the transition from the stem 184 to the stem portion 194 is on the control valve member
180 eine der Druckfeder 196 abgewandte Ringfläche 197 gebildet. Der Endbereich des zweiten Steuerventilglieds 180 mit der Ringfläche 197 ist in einem Steuerdruckraum 198 angeordnet. Die Ringfläche 197 des Steuerventilglieds 180 ist vom im Steuerdruckraum 198 herrschenden Steuerdruck beaufschlagt, der eine der Druckfeder 196 entgegenwirkende Kraft auf das Steuerventilglied 180 ausübt. Der Steuerdruck im Steuerdruckraum 198 wird durch einen Aktor 199 bestimmt, der beispielsweise ein Piezoaktor ist. Der Piezoaktor 199 ist mit einer elektrischen Steuereinrichtung 200 verbunden, durch die die Höhe einer an den Piezoaktor 199 angelegten elektrischen Spannung bestimmt wird. Abhängig von der Höhe der an diesen angelegten elektrischen Spannung ändert sich die Länge des Piezoaktors 199 und damit der Steuerdruck im Steuerdruckraum 198. Der Piezoaktor 199 kann über eine hydraulische Übersetzung den Steuerdruck im Steuerdruckraum 198 bestimmen, wodurch ermöglicht wird, daß bereits bei geringen Änderungen der Länge des Piezoaktors 199 relativ starke Änderungen des Steuerdrucks bewirkt werden können. Wenn durch die Steuereinrichtung 200 keine elektrische180 an annular surface 197 facing away from the compression spring 196 is formed. The end region of the second control valve member 180 with the annular surface 197 is arranged in a control pressure chamber 198. The annular surface 197 of the control valve member 180 is from the control pressure prevailing in the control pressure chamber 198 applied, which exerts a force counteracting the compression spring 196 on the control valve member 180. The control pressure in the control pressure chamber 198 is determined by an actuator 199, which is a piezo actuator, for example. The piezo actuator 199 is connected to an electrical control device 200, by which the level of an electrical voltage applied to the piezo actuator 199 is determined. Depending on the level of the electrical voltage applied to it, the length of the piezo actuator 199 and thus the control pressure in the control pressure chamber 198 change. The piezo actuator 199 can determine the control pressure in the control pressure chamber 198 by means of a hydraulic ratio, which makes it possible that even with small changes the Length of the piezo actuator 199 can cause relatively large changes in the control pressure. If by the control device 200 no electrical
Spannung an den Piezoaktor 199 angelegt wird, so ist der Steuerdruck im Steuerdruckraum 198 so gering, daß das zweite Steuerventilglied 180 durch die Kraft der Druckfeder 196 gegen die Kraft der Druckfeder 190 mit seiner Dichtfläche 186 vom Ventilsitz 189 abgehoben ist.Voltage is applied to the piezo actuator 199, the control pressure in the control pressure chamber 198 is so low that the second control valve member 180 is lifted from the valve seat 189 with its sealing surface 186 by the force of the compression spring 196 against the force of the compression spring 190.
Nachfolgend wird die Funktion der Kraftstoffeinspritzeinrichtung mit der Steuerventileinrichtung 130 gemäß dem zweiten Ausführungsbeispiel erläutert. Beim Saughub desThe function of the fuel injection device with the control valve device 130 according to the second exemplary embodiment is explained below. During the suction stroke of the
Pumpenkolbens 14 ist durch die Steuereinrichtung 200 keine Spannung an den Piezoaktor 199 angelegt und die Steuerventileinrichtung 130 befindet sich in einer in Figur 2 dargestellten ersten Schaltstellung. Das zweite Steuerventilglied 180 wird dabei durch die Kraft derPump piston 14 has no voltage applied to piezo actuator 199 by control device 200, and control valve device 130 is in a first switching position shown in FIG. 2. The second control valve member 180 is the force of
Druckfeder 196 gegen die Kraft der Druckfeder 190 mit seiner zweiten Dichtfläche 186 vom zweiten Ventilsitz 189 mit einem Hub h2 abgehoben. Das zweite Steuerventilglied 180 liegt mit dem Stirnende seines Schafts 181 am Stirnende des Schafts 161 des ersten Steuerventilglieds 160 an und bewegt dieses gegen die Kraft der Druckfeder 169, so daß das erste Steuerventilglied 160 mit seiner ersten Dichtfläche 163 vom ersten Ventilsitz 166 mit einem Hub hl abgehoben ist. Die durch die Druckfeder 196 auf das zweite Steuerventilglied 180 und über dieses auch auf das erste Steuerventilglied 160 ausgeübte Kraft ist somit größer als die Summe der durch die Druckfeder 169 auf das erste Steuerventilglied 160 ausgeübten Kraft und der durch die Druckfeder 190 aus das zweite Steuerventilglied 180 ausgeübten Kraft. Durch den Pumpenkolben 14 kann bei dessen Saughub vom Entlastungsraum 31 durch den Bohrungsabschnitt 165 um das erste Steuerventilglied 160 herum und durch die Verbindung 168 Kraftstoff in den Pumpenarbeitsraum 18 ansaugen.Compression spring 196 against the force of the compression spring 190 with its second sealing surface 186 is lifted off the second valve seat 189 with a stroke h2. The end of its stem 181 abuts the second control valve member 180 against the front end of the stem 161 of the first control valve member 160 and moves it against the force of the compression spring 169, so that the first control valve member 160 is lifted with its first sealing surface 163 from the first valve seat 166 with a stroke hl. The force exerted by the compression spring 196 on the second control valve member 180 and, via this, also on the first control valve member 160 is thus greater than the sum of the force exerted by the compression spring 169 on the first control valve member 160 and the force exerted by the compression spring 190 on the second control valve member 180 exerted force. During its suction stroke, the pump piston 14 can draw fuel into the pump work chamber 18 from the relief chamber 31 through the bore section 165 around the first control valve member 160 and through the connection 168.
Der Zeitpunkt des Beginns der Kraftstoffeinspritzung beim Förderhub des Pumpenkolbens 14 wird durch die Steuereinrichtung 200 bestimmt, indem durch diese eine Spannung an den Piezoaktor 199 angelegt wird und sich die Steuerventileinrichtung 130 in einer in Figur 3 dargestellten zweiten Schaltstellung befindet. Hierbei wird der Steuerdruck im Steuerdruckraum 198 erhöht, so daß auf das zweite Steuerventilglied 180 zusätzlich zu der Kraft der Druckfeder 190 eine Druckkraft entgegen der Kraft der Druckfeder 196 wirkt. Das zweite Steuerventilglied 180 bewegt sich somit in Längsrichtung, bis es mit seiner zweiten Dichtfläche 186 am zweiten Ventilsitz 189 zur Anlage kommt, so daß der Pumpenarbeitsraum 18 vom Druckraum 32 getrennt ist. Das erste Steuerventilglied 160 bewegt sich bewirkt durch die auf dieses wirkende Druckfeder 169 ebenfalls in Längsrichtung, bis es mit seiner erstenThe point in time at which fuel injection begins during the delivery stroke of the pump piston 14 is determined by the control device 200 by applying a voltage to the piezo actuator 199 and the control valve device 130 being in a second switching position shown in FIG. 3. Here, the control pressure in the control pressure chamber 198 is increased so that a pressure force acts on the second control valve member 180 in addition to the force of the compression spring 190 against the force of the compression spring 196. The second control valve member 180 thus moves in the longitudinal direction until it comes to rest with its second sealing surface 186 on the second valve seat 189, so that the pump working chamber 18 is separated from the pressure chamber 32. The first control valve member 160 also causes the compression spring 169 acting on it to move in the longitudinal direction until it is at its first
Dichtfläche 163 am ersten Ventilsitz 166 zur Anlage kommt, so daß der Pumpenarbeitsraum 18 auch vom Entlastungsraum 31 getrennt ist . Beim Förderhub des Pumpenkolbens 14 baut sich im Pumpenarbeitsraum 18 Hochdruck auf, durch den das Kraftstoffeinspritzventil 20 geöffnet wird und Kraftstoff in den Brennraum der Brennkraftmaschine eingespritzt wird.Sealing surface 163 comes to rest on the first valve seat 166, so that the pump working chamber 18 is also separated from the relief chamber 31. During the delivery stroke of the pump piston 14, high pressure builds up in the pump work chamber 18, through which the Fuel injection valve 20 is opened and fuel is injected into the combustion chamber of the internal combustion engine.
Wenn das erste Einspritzventilglied 160 mit seiner ersten Dichtfläche 163 am ersten Ventilsitz 166 anliegt und das zweite Einspritzventilglied 180 mit seiner zweiten Dichtfläche 186 am zweiten Ventilsitz 189 anliegt, so liegt der Schaft 181 des zweiten Steuerventilglieds 180 mit seiner Stirnseite nicht an der Stirnseite des Schafts 161 des ersten Steuerventilglieds 160 an, sondern zwischen diesen ist ein Abstand a vorhanden.If the first injection valve member 160 bears on the first valve seat 166 with its first sealing surface 163 and the second injection valve member 180 bears on the second valve seat 189 with its second sealing surface 186, the end face of the stem 181 of the second control valve member 180 is not on the end face of the stem 161 of the first control valve member 160, but there is a distance a between them.
Wenn die Kraftstoffeinspritzung unterbrochen werden soll, beispielsweise nach eine Voreinspritzung, so wird durch die Steuereinrichtung 200 die an den Piezoaktor 199 angelegte elektrische Spannung verringert, jedoch nicht auf Null reduziert und die Steuerventileinrichtung 130 befindet sich in einer in Figur 4 dargestellten dritten Schaltstellung. Der Steuerdruck im Steuerdruckraum 198 wird hierbei verringert, so daß die durch die Druckfeder 196 auf das zweite Steuerventilglied 180 ausgeübte Kraft größer ist als die durch die Druckfeder 190 und den Steuerdruck ausgeübte Kraft. Das zweite Steuerventilglied 180 bewegt sich dann in Längsrichtung und hebt mit seiner zweiten Dichtfläche 186 vom zweiten Ventilsitz 189 ab und durchfährt einen Hub h3 entsprechend etwa dem Abstand a vom ersten Steuerventilglied 160. Die durch die Druckfeder 196 ausgeübte Kraft reicht jedoch nicht aus, um auch das erste Steuerventilglied 160 gegen die Kraft der Druckfeder 169 in Öffnungsrichtung zu bewegen, so daß dieses mit seiner ersten Dichtfläche 163 in Anlage am ersten Ventilsitz 166 bleibt und keine Verbindung zum Entlastungsraum 31 freigibt. Der Pumpenarbeitsraum 18 ist somit über das geöffnete zweite Steuerventilglied 180 mit dem Druckraum 32 verbunden, so daß dort Hochdruck herrscht. Von dem im Druckraum 32 herrschenden Druck ist ein auf das Einspritzventilglied 22 wirkender Schließkolben 133 beaufschlagt, durch den bei im Durckraum 32 herrschendem Hochdruck das Kraftstoffeinspritzventil 20 geschlossen wird.If the fuel injection is to be interrupted, for example after a pre-injection, the control device 200 reduces the electrical voltage applied to the piezo actuator 199, but does not reduce it to zero, and the control valve device 130 is in a third switching position shown in FIG. 4. The control pressure in the control pressure chamber 198 is thereby reduced, so that the force exerted by the compression spring 196 on the second control valve member 180 is greater than the force exerted by the compression spring 190 and the control pressure. The second control valve member 180 then moves in the longitudinal direction and lifts with its second sealing surface 186 from the second valve seat 189 and travels through a stroke h3 corresponding approximately to the distance a from the first control valve member 160. However, the force exerted by the compression spring 196 is not sufficient to to move the first control valve member 160 against the force of the compression spring 169 in the opening direction so that it remains in contact with the first valve seat 166 with its first sealing surface 163 and does not open a connection to the relief chamber 31. The pump work chamber 18 is thus connected to the pressure chamber 32 via the opened second control valve member 180, so that high pressure prevails there. There is a pressure in the pressure chamber 32 acting on the injection valve member 22 closing piston 133, by which the fuel injection valve 20 is closed at high pressure prevailing in the pressure chamber 32.
Für eine Fortsetzung der Kraftstoffeinspritzung, beispielsweise zu einer Haupteinspritzung, wird durch die Steuereinrichtung 200 die an den Piezoaktor 199 angelegte elektrische Spannung wieder erhöht, so daß sich das zweite Steuerventilglied 180 durch die Kraft der Druckfeder 190 und die vom Steuerdruck verursachte Kraft in Längsrichtung bewegt und mit seiner zweiten Dichtfläche 186 am zweiten Ventilsitz 189 zur Anlage kommt und sich die Steuerventileinrichtung 130 wieder in ihrer zweiten Schaltstellung gemäß Figur 3 befindet. Der Druckraum 32 wird dann vorzugsweise mit dem Entlastungsraum 31 verbunden, um diesen zu entlasten und das Öffnen desFor a continuation of the fuel injection, for example for a main injection, the control device 200 increases the electrical voltage applied to the piezo actuator 199 again, so that the second control valve member 180 moves in the longitudinal direction by the force of the compression spring 190 and the force caused by the control pressure and comes with its second sealing surface 186 to the second valve seat 189 and the control valve device 130 is again in its second switching position according to FIG. 3. The pressure chamber 32 is then preferably connected to the relief chamber 31 in order to relieve it and to open the
Kraftstoffeinspritzventils 20 zu ermöglichen. Die Verbindung des Druckraums 32 mit dem Entlastungsraum 31 kann vorzugsweise durch das zweite Steuerventilglied 180 gesteuert werden.To allow fuel injector 20. The connection of the pressure chamber 32 to the relief chamber 31 can preferably be controlled by the second control valve member 180.
Zu einer weiteren Unterbrechung der Kraftstoffeinspritzung nach der Haupteinspritzung kann wiederum dasThis can in turn lead to a further interruption of the fuel injection after the main injection
Kraftstoffeinspritzventil 20 geschlossen werden, indem die Steuerventileinrichtung 130 in ihre in Figur 4 dargestellte dritte Schaltstellung gebracht wird, in der der Druckraum 32 durch das zweite Steuerventilglied 180 mit dem Pumpenarbeitsraum 18 verbunden wird. Anschließend kann das Kraftstoffeinspritzventil 20 für eine nochmalige Kraftstoffeinspritzung, beispielsweise einerFuel injection valve 20 are closed by bringing the control valve device 130 into its third switching position shown in FIG. 4, in which the pressure chamber 32 is connected to the pump work chamber 18 by the second control valve member 180. The fuel injection valve 20 can then be used for another fuel injection, for example one
Nacheinspritzung, nochmals geöffnet werden, indem die Steuerventileinrichtung 130 in ihre in Figur 3 dargestellte Schaltstellung gebracht wird und der Druckraum 32 wieder durch das zweite Steuerventilglied 180 vom Pumpenarbeitsraum 18 getrennt und mit dem Entlastungsraum 31 verbunden wird. Zur Beendigung der Kraftstoffeinspritzung wird durch die Steuereinrichtung 200 keine elektrische Spannung mehr an denPiezoaktor 199 angelegt, so daß durch die Druckfeder 196 sowohl das zweite Steuerventilglied 180 mit seiner zweiten Dichtfläche 186 vom zweiten Ventilsitz 189 abgehoben wird als auch durch dieses das erste Steuerventilglied 160 mit seiner ersten Dichtfläche 163 vom ersten Ventilsitz 166 abgehoben wird. Der Hub, den das erste Steuerventilglied 160 von seiner geschlossenen Stellung in der zweitenAfter injection, can be opened again by bringing the control valve device 130 into its switching position shown in FIG. 3 and the pressure chamber 32 again being separated from the pump work chamber 18 by the second control valve member 180 and being connected to the relief chamber 31. To terminate the fuel injection, the control device 200 no longer applies any electrical voltage to the piezo actuator 199, so that the compression spring 196 both lifts the second control valve member 180 with its second sealing surface 186 from the second valve seat 189 and also the first control valve member 160 with its first sealing surface 163 is lifted from the first valve seat 166. The stroke that the first control valve member 160 moves from its closed position to the second
Schaltstellung der Steuerventileinrichtung 130 gemäß Figur 3 in seine offene Stellung in der dritten Schaltstellung der Steuerventileinrichtung 130 gemäß Figur 4 in Längsrichtung ausführt, ist um den Abstand a geringer als der Hub, den das zweite Steuerventilglied 180 von seiner geschlossenen Stellung in der zweiten und dritten Schaltstellung der Steuerventileinrichtung 130 gemäß Figur 3 und Figur 4 in seine offene Stellung in der Schaltstellung der Steuerventileinrichtung 130 gemäß Figur 2 in Längsrichtung ausführt.The switching position of the control valve device 130 according to FIG. 3 in its open position in the third switching position of the control valve device 130 according to FIG. 4 in the longitudinal direction is smaller by the distance a than the stroke that the second control valve member 180 from its closed position in the second and third switching position 3 and FIG. 4 in its open position in the switching position of the control valve device 130 according to FIG. 2 in the longitudinal direction.
Der Zylinder 16 mit dem Pumpenkolben 14 und dem Pumpenarbeitsraum 18, das Kraftstoffeinspritzventil 20 sowie die Steuerventileinrichtung 30 gemäß dem ersten Ausführungsbeispiel bzw. die Steuerventileinrichtung 130 gemäß dem zweiten Ausführungsbeispiel bilden vorzugsweise eine gemeinsame Baueinheit als Pumpe-Düse-Einheit. The cylinder 16 with the pump piston 14 and the pump work chamber 18, the fuel injection valve 20 and the control valve device 30 according to the first exemplary embodiment and the control valve device 130 according to the second exemplary embodiment preferably form a common structural unit as a pump-nozzle unit.

Claims

Patentansprüche claims
1. Kraftstoffeinspritzeinrichtung für eine1. Fuel injector for one
Brennkraftmaschine mit einem von einem Pumpenkolben (14) begrenzten Pumpenarbeitsraum (18) , der über eine durch eine Steuerventileinrichtung (30; 130) gesteuerte Verbindung mit Kraftstoff befüllbar ist und mit einem Entlastungsraum (31) verbindbar ist, wobei während einer jeweiligenInternal combustion engine with a pump working chamber (18) bounded by a pump piston (14), which can be filled with fuel via a connection controlled by a control valve device (30; 130) and can be connected to a relief chamber (31), during a respective one
Kraftstoffeinspritzung der Pumpenarbeitsraum (18) durch die Steuerventileinrichtung (30; 130) vom Entlastungsraum (31) getrennt ist und zur Beendigung der Kraftstoffeinspritzung durch die Steuerventileinrichtung (30,-130) mit dem Entlastungsraum (31) verbunden ist, mit einem Kraftstoffeinspritzventil (20) mit einem Einspritzventilglied (22) , das wenigstens eine Einspritzöffnung (23) steuert, das vom im Pumpenarbeitsraum (18) herrschenden Druck in Öffnungsrichtung (28) entgegen einer Schließkraft beaufschlagt ist, dadurch gekennzeichnet, daß durch die Steuerventileinrichtung (30; 130) zu einer Unterbrechung der Kraftstoffeinspritzung außerdem eine Verbindung des Pumpenarbeitsraums (18) mit einem Druckraum (32) gesteuert wird, wobei das Einspritzventilglied (22) zumindest mittelbar durch den im Druckraum (32) herrschenden Druck in Schließrichtung beaufschlagt ist .Fuel injection of the pump working chamber (18) is separated from the relief chamber (31) by the control valve device (30; 130) and is connected to the relief chamber (31) to terminate the fuel injection by the control valve device (30, -130), with a fuel injection valve (20) with an injection valve member (22) which controls at least one injection opening (23) which is acted upon by the pressure prevailing in the pump work chamber (18) in the opening direction (28) against a closing force, characterized in that the control valve device (30; 130) leads to one Interruption of the fuel injection also controls a connection of the pump work chamber (18) to a pressure chamber (32), the injection valve member (22) being acted upon at least indirectly by the pressure prevailing in the pressure chamber (32) in the closing direction.
2. Kraftstoffeinspritzeinrichtung nach Anspruch 1, dadurch gekennzeichnet, daß zur Kraftstoffeinspritzung der Pumpenarbeitsraum (18) durch die Steuerventileinrichtung (30; 130) vom Entlastungsraum (31) und vom Druckraum (32) getrennt ist .2. Fuel injection device according to claim 1, characterized in that for fuel injection, the pump work chamber (18) by the control valve device (30; 130) is separated from the relief chamber (31) and from the pressure chamber (32).
3. Kraftstoffeinspritzeinrichtung nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß zur Beendigung der3. Fuel injection device according to claim 1 or 2, characterized in that to end the
Kraftstoffeinspritzung der Pumpenarbeitsraum (18) durch die Steuerventileinrichtung (30; 130) mit dem Entlastungsraum (31) und dem Druckraum (32) verbunden ist.Fuel injection of the pump work chamber (18) is connected to the relief chamber (31) and the pressure chamber (32) by the control valve device (30; 130).
4. Kraftstoffeinspritzeinrichtung nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß die4. Fuel injection device according to one of claims 1 to 3, characterized in that the
Steuerventileinrichtung (30) ein Steuerventilglied (35) aufweist, das durch wenigstens einen Aktor (51,52) entlang einer Längsrichtung bewegbar ist, daß das Steuerventilglied (35) in einer ersten Längsrichtung mit einer erstenControl valve device (30) has a control valve member (35) which can be moved along a longitudinal direction by at least one actuator (51, 52), that the control valve member (35) in a first longitudinal direction with a first
Dichtfläche (36) mit einem ersten Ventilsitz (45) zur Steuerung der Verbindung des Pumpenarbeitsraums (18) mit dem Entlastungsraum (31) zusammenwirkt und daß das Steuerventilglied (35) in der entgegengesetzten Längsrichtung mit einer zweiten Dichtfläche (42) mit einem zweiten Ventilsitz (47) zur Steuerung der Verbindung des Pumpenarbeitsraums (18) mit dem Druckraum (32) zusammenwirkt .Sealing surface (36) cooperates with a first valve seat (45) for controlling the connection of the pump work chamber (18) to the relief chamber (31) and that the control valve member (35) in the opposite longitudinal direction with a second sealing surface (42) with a second valve seat ( 47) cooperates to control the connection of the pump work space (18) with the pressure space (32).
5. Kraftstoffeinspritzeinrichtung nach Anspruch 4, dadurch gekennzeichnet, daß für die Bewegung des Steuerventilglieds (35) in die beiden Längsrichtungen getrennte Aktoren (51,52) vorgesehen sind.5. Fuel injection device according to claim 4, characterized in that separate actuators (51, 52) are provided for the movement of the control valve member (35) in the two longitudinal directions.
6. Kraftstoffeinspritzeinrichtung nach Anspruch 4 oder 5, dadurch gekennzeichnet, daß der wenigstens eine Aktor (51,52) ein Elektromagnet ist.6. Fuel injection device according to claim 4 or 5, characterized in that the at least one actuator (51,52) is an electromagnet.
7. Kraftstoffeinspritzeinrichtung nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß die Steuerventileinrichtung (130) zwei getrennte Steuerventilglieder (160,180) aufweist, die entlang einer Längsrichtung bewegbar und zueinander versetzt sind, daß ein erstes Steuerventilglied (160) in einer Längsrichtung mit einer ersten Dichtfläche (163) mit einem ersten Ventilsitz (166) zur Steuerung der Verbindung des Pumpenarbeitsraums (18) mit dem Entlastungsraum (31) zusammenwirkt und daß ein zweites Steuerventilglied (180) in derselben Längsrichtung mit einer zweiten Dichtfläche (186) mit einem zweiten Ventilsitz (189) zur Steuerung der Verbindung des Pumpenarbeitsraums (18) mit dem Druckraum (32) zusammenwirkt, und daß beide Steuerventilglieder (160,180) vorzugsweise durch einen einzigen Aktor (199) bewegbar sind.7. Fuel injection device according to one of claims 1 to 3, characterized in that the Control valve device (130) has two separate control valve members (160, 180) which are movable along a longitudinal direction and offset from one another, that a first control valve member (160) in a longitudinal direction with a first sealing surface (163) with a first valve seat (166) for controlling the connection of the pump work chamber (18) cooperates with the relief chamber (31) and that a second control valve member (180) in the same longitudinal direction with a second sealing surface (186) with a second valve seat (189) for controlling the connection of the pump work chamber (18) to the pressure chamber ( 32) cooperates, and that both control valve members (160, 180) are preferably movable by a single actuator (199).
8. Kraftstoffeinspritzeinrichtung nach Anspruch 7, dadurch gekennzeichnet, daß durch den Aktor (199) das zweite Steuerventilglied (180) mit einem ersten Hub (b.3) in Längsrichtung bewegbar ist, so daß dieses mit seiner zweiten Dichtfläche (186) vom zweiten Ventilsitz (189) abhebt und die Verbindung des Pumpenarbeitsraums (18) mit dem Druckraum (32) freigibt, während das erste Steuerventilglied (160) mit seiner ersten Dichtfläche (163) in Anlage am ersten Ventilsitz (166) bleibt, so daß der Pumpenarbeitsraum (18) vom Entlatungsraum (31) getrennt ist.8. Fuel injection device according to claim 7, characterized in that the actuator (199), the second control valve member (180) with a first stroke (b.3) is movable in the longitudinal direction, so that this with its second sealing surface (186) from the second valve seat (189) lifts up and releases the connection between the pump work chamber (18) and the pressure chamber (32), while the first control valve member (160) remains in contact with the first valve seat (166) with its first sealing surface (163), so that the pump work chamber (18 ) is separated from the baffle (31).
9. Kraftstoffeinspritzeinrichtung nach Anspruch 8, dadurch gekennzeichnet, daß durch den Aktor (199) das zweite Steuerventilglied (180) mit einem zweiten, größeren Hub (h2) in Längsrichtung bewegbar ist, so daß dieses am ersten Steuerventilglied (160) zur Anlage kommt und dieses mit seiner ersten Dichtfläche (163) vom ersten Ventilsitz (166) mit einem geringeren Hub (hl) als dem zweiten Hub (h2) des zweiten Steuerventilglieds (180) abhebt. 9. Fuel injection device according to claim 8, characterized in that the actuator (199), the second control valve member (180) with a second, larger stroke (h2) is movable in the longitudinal direction so that it comes to rest on the first control valve member (160) and this with its first sealing surface (163) lifts from the first valve seat (166) with a shorter stroke (hl) than the second stroke (h2) of the second control valve member (180).
10. Kraftstoffeinspritzeinrichtung nach einem der Ansprüche 7 bis 9, dadurch gekennzeichnet, daß die beiden Steuerventilglieder (160,180) jeweils durch eine Schließfeder (169,190) mit ihrer Dichtfläche (163,186) zum jeweiligen Ventilsitz (166,189) hin beaufschlagt sind.10. Fuel injection device according to one of claims 7 to 9, characterized in that the two control valve members (160, 180) are each acted upon by a closing spring (169, 190) with their sealing surface (163, 186) towards the respective valve seat (166, 189).
11. Kraftstoffeinspritzeinrichtung nach einem der Ansprüche 7 bis 10, dadurch gekennzeichnet, daß das zweite Steuerventilglied (180) durch eine Feder (196) in Öffnungsrichtung beaufschlagt ist und von dem in einem Steuerdruckraum (198) herrschenden Steuerdruck in Schließrichtung beaufschlagt ist und daß der Steuerdruck durch den Aktor (199) gesteuert wird.11. Fuel injection device according to one of claims 7 to 10, characterized in that the second control valve member (180) is acted upon by a spring (196) in the opening direction and is acted upon by the control pressure prevailing in a control pressure chamber (198) in the closing direction and in that the control pressure is controlled by the actuator (199).
12. Kraftstoffeinspritzeinrichtung nach einem der Ansprüche 7 bis 11, dadurch gekennzeichnet, daß der Aktor (199) ein Piezoaktor ist, der abhängig von einer an diesen angelegten elektrischen Spannung seine Länge ändert .12. Fuel injection device according to one of claims 7 to 11, characterized in that the actuator (199) is a piezo actuator which changes its length depending on an electrical voltage applied to it.
13. Kraftstoffeinspritzeinrichtung nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß von dem im Druckraum (32) herrschenden Druck ein längsverschiebbar geführter Kolben (33/133) beaufschlagt ist, der zumindest mittelbar in Schließrichtung auf das Einspritzventilglied (22) wirkt. 13. Fuel injection device according to one of the preceding claims, characterized in that is acted upon by the pressure prevailing in the pressure chamber (32) pressure, a longitudinally displaceably guided piston (33/133) acting at least indirectly in the closing direction on the injection valve member (22).
EP01989387A 2000-12-16 2001-12-07 Fuel injection device for an internal combustion engine Withdrawn EP1346150A1 (en)

Applications Claiming Priority (3)

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DE10062896 2000-12-16
DE10062896A DE10062896B4 (en) 2000-12-16 2000-12-16 Fuel injection device for an internal combustion engine
PCT/DE2001/004623 WO2002048540A1 (en) 2000-12-16 2001-12-07 Fuel injection device for an internal combustion engine

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EP (1) EP1346150A1 (en)
JP (1) JP2004515708A (en)
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US20040011887A1 (en) 2004-01-22
WO2002048540A1 (en) 2002-06-20

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