EP1252432B1 - Direktgesteuerte kraftstoffeinspritzeinrichtung für eine kolbenbrennkraftmaschine - Google Patents

Direktgesteuerte kraftstoffeinspritzeinrichtung für eine kolbenbrennkraftmaschine Download PDF

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Publication number
EP1252432B1
EP1252432B1 EP00988800A EP00988800A EP1252432B1 EP 1252432 B1 EP1252432 B1 EP 1252432B1 EP 00988800 A EP00988800 A EP 00988800A EP 00988800 A EP00988800 A EP 00988800A EP 1252432 B1 EP1252432 B1 EP 1252432B1
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EP
European Patent Office
Prior art keywords
pressure
valve
piston
actuator
fuel injection
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP00988800A
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German (de)
English (en)
French (fr)
Other versions
EP1252432A2 (de
Inventor
Gunter GÜRICH
Hermann Josef Laumen
Karl Joachim SCHMÜCKER
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.)
FEV Europe GmbH
Original Assignee
FEV Motorentechnik GmbH and Co KG
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 FEV Motorentechnik GmbH and Co KG filed Critical FEV Motorentechnik GmbH and Co KG
Publication of EP1252432A2 publication Critical patent/EP1252432A2/de
Application granted granted Critical
Publication of EP1252432B1 publication Critical patent/EP1252432B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/12—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship providing a continuous cyclic delivery with variable pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0003—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0003—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure
    • F02M63/0005—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure using valves actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0003—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure
    • F02M63/0007—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure using electrically actuated valves

Definitions

  • common rail systems formed fuel injectors for a reciprocating internal combustion engine with Direct fuel injection consist essentially of a Nozzle part with injector, one injector having closing nozzle needle, the pressurization through the fuel to be injected via a servo-hydraulic system is movable in the open position.
  • the required Form is via the high-pressure part of the fuel supply, d. H. taken off the common rail.
  • the injection pressure can be influenced very flexibly and via the control of a servo valve and
  • the nozzle needle can be injection time and injection duration also set with high flexibility.
  • the invention is based on the object, a fuel injection device for a direct fuel injection which makes it possible during the respective injection time to vary the injection quantity, d. H. the injection rate to shape.
  • a fuel injection device for a reciprocating internal combustion engine with a nozzle part with injection nozzle, which has a pressure chamber, in the a nozzle needle closing the injection nozzle is guided, when pressurized by the fuel to be injected is movable in the open position, wherein the pressure chamber via a connection channel with a control part in connection stands, which has a valve chamber into which the connecting channel on the one hand and one with the fuel supply connected high-pressure channel on the other hand opens and in the a valve body acting as a piston system is guided, the by a valve spring on a valve seat in the closed position is held, and with an actuator connected to the valve body is in operative connection and this when activated moved into predetermined opening positions and a corresponding Flow from the high-pressure channel into the connecting channel releases, as well as with a compensation piston of the above Pressure in the connecting channel in the opposite direction to the force effect of the actuator can be acted upon.
  • the nozzle part designed so that when pressurized the Nozzle needle the passage cross-section to the nozzle openings as completely as possible, with intermediate positions are not provided.
  • the control of the volume flow takes place via the valve body provided in the control part, the Hub by a corresponding control of the actuator can be varied.
  • the valve body is in this case preferably designed as a seat valve to the tightness in the closed Condition.
  • the actuator is here Appropriately designed so that he is in relation to his Adjusting travel proportional to the applied job energy is trained.
  • electrical Actuators that are voltage-proportional with respect to their travel are formed adjusting, as for example given by so-called solid state actuators are.
  • solid state actuators come here in particular piezoelectric Actuators but also magneto-strictive actuators into consideration. Also electromagnetically working actuators can be used.
  • the arrangement of a in its diameter correspondingly sized compensating piston advantageous, over the pressure in the connecting channel is acted upon the nozzle part and accordingly against the force of the actuator acts. This results in a so-called Pressure feedback, the good controllability of from the high pressure side in the connecting channel flowing volume flow and thus allows a good shaping of the injection rate.
  • Valve body on a side facing away from the actuator end with a Compensating piston is provided, which exceeds the pressure in the connecting channel can be acted upon.
  • control part a to the low pressure side of the fuel supply opening Relief valve has, which the connection channel is assigned, and the activation of the actuator closes.
  • control part has a pressure divider, the one with the high-pressure channel on the one hand and a piston system forming valve body with compensating piston on the other communicates and the over the actuator is adjustable.
  • Fig. 1 is a fuel injection device in the form of a flow chart for direct injection of the fuel in the individual cylinders of a reciprocating internal combustion engine shown.
  • the fuel injector has a fuel supply 1, essentially by a fuel tank 2, a high pressure pump 3 and a high pressure chamber 4, the so-called common rail.
  • Each cylinder of the reciprocating internal combustion engine is equipped with a nozzle part 5, which via a connecting channel 6, a Control part 7 and a high pressure passage 8 with the fuel supply 1 communicates.
  • the control part 7 is also available with a motor controller not shown here in connection, by acting as the control valve Control part 7 can be controlled so that the injection time the connection between high-pressure channel 8 and connecting channel 6 is opened and the high pressure Fuel can act on the nozzle part 5.
  • the special one Functionality will be described in more detail below.
  • the nozzle part 5 is essentially formed by a nozzle needle 9, which is guided in a pressure chamber 10, in which Connecting channel 6 opens.
  • the nozzle needle 9 has a needle tip 11 on, with a corresponding seat 12 of the Injector 13 cooperates and acts as a valve.
  • the injector 13 is provided with corresponding nozzle openings 14.
  • the closing spring 16 is arranged in a leakage space 18, the via a leakage line 19 with the low pressure line 17th is in communication, so that the accumulating in the leakage chamber 18 Leakage amounts are derived in the fuel tank 2 can.
  • the actuator 20 is preferably designed to be in relative to its travel proportional to the applied Job-setting energy is designed.
  • the control part 7 for example, as a throttle valve so given the opportunity that from the high pressure channel. 8 in the connecting channel 6 effluent flow through corresponding adjustment of the opening cross-section in the control part 7 to influence.
  • a pressurization designed as an injection valve nozzle part 5 in the illustrated schematic example completely opens, can via a corresponding change in the setting of the control section 7 of the nozzle part 5 supplied volume flow during the opening duration of the injection nozzle 13 can be varied.
  • control part 7 Structure and function of the control part 7 will be described below of different embodiments explained in more detail become.
  • the actuator 20 is advantageous as a so-called solid state actuator educated.
  • a piezoelectric is preferred working actuator used in relation to its travel or, because of its mechanical compliance, its adjusting force proportional to the voltage is trained.
  • a piezoelectric actuator it is also possible to use a magnetostrictive actuator, the current-proportional adjusting with respect to its travel is trained.
  • solid state actuators by a high switching speed, good controllability the Stellweges and also large Stell rule excel and
  • directly or possibly via a hydraulic Stroke translation acting on the control part in the control part 7 also results in only short opening times for as Injector valve formed nozzle part 5 the possibility of targeted shaping of the injection rate, d. H. a targeted Change in during the opening time of the injector introduced into the combustion chamber of the cylinder concerned Volume flow.
  • Fig. 2 shows an embodiment shown in the nozzle part. 5 and control part 7 with actuator 20 designed as a unit are.
  • the description of this embodiment is also the above-indicated specifics in the training to remove the control part 7.
  • Reference numerals used in FIG. 1 are also shown in FIG. 2 taken over, so that reference can be made.
  • FIG. 2 there is the overall arrangement from a carrier body constructed in several parts for reasons of production, by a coaxial assignment of nozzle part 5, Control part 7 and actuator 20 is marked.
  • the control part 7 has a valve arrangement 21.0 with a Valve chamber 21.1, in the high-pressure channel 8 on the one hand and the connecting channel 6 on the other side.
  • the valve room 21.1 is provided with a valve seat 22 to which a formed as a piston system valve body 23 via a valve spring 24 held with its valve member 23.1 in the closed position is, so that the high pressure passage 8 with respect to the connecting channel 6 is locked.
  • the for the valve spring 24th required space is connected to the leakage line 19.
  • the sections 23.1, 23.2, 23.3 and 23.4 have here partly different diameters.
  • the piezoelectric actuator 20 is in essentially formed by a stack of piezoelectric Body 20.1, with a not shown here, controllable Voltage source are connected and the one end supported on a housing part 20.2 and the other end on a Act transfer piston 20.3.
  • the transmission piston 20.3 is associated with a hydraulic chamber 20.4, which in itself known manner with a liquid, here with fuel, is filled.
  • the hydraulic chamber 20.4 is a pressure piston 23.1 associated with the valve body 23 in connection stands. If the piezoelectric body 20.1 with a voltage is applied, then the transfer piston 20.3 in Direction advanced to the hydraulic chamber 20.4 and then is under the action of contained in the hydraulic chamber 20.4 Fluid also the pressure piston 23.1 moved. Thereby, that the pressure piston 23.1 has a smaller diameter as the transmission piston 20.3, this results in a Stroke translation, d. H. according to the diameter ratio the valve body 23 via a relative to the voltage proportional Extension of the piezoelectric body 20.1 moved accordingly longer way.
  • the change in length of the piezoelectric body 20.1 takes place voltage proportional, so that according to the applied Voltage of the valve body 23 with its valve member 23.1 From the valve seat 22 lifts and thus a corresponding Flow cross-section releases, so that from the high-pressure channel 8 in the connecting channel 6 a throttling between the valve seat 22 and valve part 23.1 corresponding volume flow can pass, which then raises the nozzle needle 9 and the Injector 13 releases.
  • the valve part 23.1 approved opening cross section and according to the Duration of opening then enters fuel through the nozzle openings 14 in the combustion chamber of the cylinder in question.
  • Becomes reset the voltage on the piezoelectric body 20.1 is the valve member 23.1 on the valve seat via the valve spring 24 22 pressed and thus inhibited the fuel supply.
  • a compensation piston 25 arranged, the smaller diameter has as the valve member 23.2.
  • the compensation piston 25 can, as shown, connected to the valve body or be separated from the valve body. This compensation piston 25th is through a branch line 26 of the connection channel 6 through the pressure prevailing in the connecting channel 6 pressure applied. This results in a force feedback via the pressure in Closing direction of the valve body 23, ie against the force of the actuator 20.
  • valve body 23 not exclusively by the valve spring 24 against the force of the actuator 20 acts, but by the force feedback it is ensured that the valve body 23 during its longitudinal movement both in the opening direction as well as in the closing direction without play and without delay every change in length of the actuator adapts and thus a Energy-dependent in the case of a piezoelectric actuator voltage dependent, length change exactly to the movement of the Valve body 23 can be transferred. oscillatory movements are suppressed.
  • the degree of force feedback can be dimensioned. With a large degree of feedback, the controllability becomes better, but requires stronger actuators.
  • This force feedback allows, instead of a piezoelectric Actuator a simple electromagnetic Use actuator in which the force is proportional to the Energy supply is and thus also a defined admission the injection nozzle is possible.
  • a tension spring 20.5 is, is in the idle state, the pressure piston 23.1 via a Tension spring 20.5 acting on the relief valve 27 as Ball pressed and this held in the closed position.
  • Fig. 3 is a modified embodiment of the basis 2 described control part 7. Same Components are identified by like reference numerals.
  • the structure of the embodiment acc. Fig. 3 corresponds substantially the structure described with reference to FIG.
  • the valve body 23rd is integrally formed and actuator side of the pressure piston 23.1 firmly connected to the valve body 23.
  • the pressure piston 23.1 has a smaller diameter than the piston parts 23.2 and 23.3.
  • a relief valve 27 provided a hydraulic seat valve whose piston part 27.1 presses a valve needle 27.2 on its sealing seat, so that the connecting line 6 with respect to the low-pressure channel 17th is locked.
  • the valve Upon actuation of the valve is on the Pressure build-up in the hydraulic chamber 20.4 the closing force of the relief valve 27 pressure proportional increases and so the relief valve 27 reliable against the injection pressure in Connecting channel 6 held in the closed position.
  • FIG. 4 shows a further embodiment of the control part 7 shown.
  • the structure essentially corresponds to the structure the embodiment described with reference to FIG. 3, so that can be referenced. The difference is here only in that no separate relief valve is provided, but that the valve body 23 in the area his serving as a pressure piston 23.1 end as a relief valve 27 is designed and designed for this purpose as a slide valve is. As is apparent from the enlarged view in FIG.
  • valve body 23 is serving as a pressure piston 23.1 end of the valve body 23 at its end facing the valve chamber 21 Tapered shaped or with a sloping plane or groove and in such a way that in the closed position of Valve body 23, the actuator-side end of the cone part 27.4 in a communicating with the low pressure passage 17 Annulus 27.5 projects and in this case a passage cross-section leaves free.
  • the actuator 20 If the actuator 20 is de-energized, then moves the valve body 23 under the force of the closing spring 24 and the pressurization via the compensation piston 25 in the direction of the valve seat 22. In this case, then the Passage cross section at the annular space 27.5 released, so that the pressure in the connecting channel 6 can be reduced.
  • the order is here dimensioned so that the release of the passage cross-section to the annulus 27.5 virtually simultaneously with the seating of the locking part 23.2 on the valve seat 22nd is released.
  • Fig. 3 of the Relief valve 27 can by appropriate dimensioning the pressure reduction at the injection valve are guided so that a vapor bubble formation is avoided. In the described in Fig. 4 Embodiment, this can be achieved by an additional, reached on line 17 connected pressure relief valve become.
  • control part 7 can be used in the same way as described with reference to FIG. 2, namely as a structural unit combined with a nozzle part 5. It is also possible, as shown in the schematic diagram. Fig. 1 can be seen is, for all types of the control part 7 an arrangement to meet, in which the control part 7 separated from the nozzle part 5 is arranged. Accordingly, in the schematic Presentation acc. Fig. 1 leading to the control part 7 Branch line 26 indicated by dash-dotted lines.
  • Fig. 6 is the valve assembly 21.0 upstream of a so-called pressure divider 30.
  • Fig. 7 is on an enlarged scale an embodiment of the pressure divider 30 is shown.
  • the pressure divider consists essentially of a piston body 31, with its upper end with the actuator 20 is in operative connection (arrow 20 in Fig. 7) and the at its lower end via a spring plate 32 a return spring 33 is supported.
  • the piston body 31 is with a valve body 34 provided with a first valve seat 35.1 cooperates. In depressurized state of the Valve body 34 by the return spring 33 to the first Valve seat 35.1 pressed.
  • valve body 34 is facing on its return spring 33 Side assigned a second valve seat 35.2, the connects the annular space 37 with the outflow space 39, and the Valve body 34 closes the more, the further he moves in Direction of the arrow 20 moves.
  • the valve body forms 34 with the valve seats 35.1 and 35.2 a 3/2-way proportional valve with 100% negative coverage.
  • valve seat 35.2 Depending on the diameter of the Valve seat 35.2 takes place a feedback of the pressure in the annular space 37 on the actuator 20 so that an electromagnetic Actuator can be used.
  • the valve seat 35.2 can be designed as a flat seat to meet the requirements to minimize the manufacturing accuracy.
  • the valve body 34 is associated with a first annular space 36, in which opens a branch 8.1 of the high-pressure line and by the closed position defined by the valve seat 35.1 is completed.
  • the valve body 34 is in one second annular space 37 arranged, which via an overflow line 8.2 is in communication with a pressure chamber 38, the through the valve body 23 on its return spring 24th the opposite side is limited.
  • the valve body 34 is further in the region of the return spring 33, an outflow space 39 is assigned, the via a discharge line 40 with the low-pressure channel 17 is connected.
  • the pressure chamber 38 is connected via a line to a pressure chamber 41 in connection, the piston part 27.1 of the relief valve 27 is assigned.
  • the injection pressure can be modulated during the injection be controlled by the actuator 20 just so far, that he the valve body 34 in a position between the two Valve seats 35.1 and 35.2 moves in the annular space 37th and thus also in the space 38 sets the pressure, as Injection pressure is desired.
  • the pressure in the annular space 3 is also in the pressure chamber 41 on the piston body 27.1 of the relief valve 27, so that this pressure, the closing spring 27.3 in the closing direction supporting the valve body 27.2 works.
  • valve body 34 When the actuator 20 is deactivated, the valve body 34 is seated of the pressure divider 30 on its valve seat 35.1, so that the pressure chambers 41 and 38 are depressurized and thus the Valve arrangement 21.0 closes.
  • the still in the connection channel 6 Pending pressure can be through the line 17.1 and the relief valve 27 are degraded very quickly, so that the valve spring 16, the nozzle needle 9 very quickly in the closed position brings, wherein the valve spring 27.3 is designed so that the fastest possible pressure reduction, on the other but a residual pressure remains so that vapor bubbles are formed is avoided.
  • the embodiment acc. Fig. 8 is with respect to the control part 7 identically constructed in the function as the above Embodiment acc. Figs. 6 and 7.
  • the difference only consists in that the piston body 31 of the Pressure divider 30 at its the return spring 33 facing End is provided with a compensation piston 42, the over one of the overflow 8.2 branching branch line with the partial pressure can be acted upon and so a pressure feedback can be done. This allows the pressure divider 30 in the direction of the arrow via an electromagnetic actuator to press.
  • Fig. 9 corresponds substantially the above-described structure gem.
  • the control part 7 is modified only in such a way that the pressure chamber 41 of the relief valve via a throttle 43rd is directly connected to the low pressure passage 17 and the Pressure divider 30 here are designed as a 2/2-way valve can.
  • Fig. 10 is an embodiment of the injection valve with an openable in two stages nozzle needle 9 shown.
  • the Nozzle needle 9 is supported by a first soft Closing spring 16.1 on the housing.
  • a sliding body Provided 16.3, which turned away with his the nozzle needle 9 Side on a second harder closing spring 16.2 supported.
  • the sliding body 16.3 has a support extension 16.4 on, in the closed position of the nozzle needle 9 by a small Dimension a before the end of the piston body 15 of the nozzle needle 9 ends.
  • FIG. 11 a modification of the embodiment is gem.
  • FIG. 10 is shown.
  • the supports Closing spring 16 on a bypass piston 16.5 on his the closing spring averted side has a pressure chamber 16.6, via a throttle 16.7 to the connecting channel. 6 connected.
  • a pressure-dependent dynamic guidance of the opening movement of the nozzle needle 9 possible.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)
EP00988800A 2000-01-18 2000-12-15 Direktgesteuerte kraftstoffeinspritzeinrichtung für eine kolbenbrennkraftmaschine Expired - Lifetime EP1252432B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10001828A DE10001828A1 (de) 2000-01-18 2000-01-18 Direktgesteuerte Kraftstoffeinspritzeinrichtung für eine Kolbenbrennkraftmaschine
DE10001828 2000-01-18
PCT/EP2000/012777 WO2001053688A2 (de) 2000-01-18 2000-12-15 Direktgesteuerte kraftstoffeinspritzeinrichtung für eine kolbenbrennkraftmaschine

Publications (2)

Publication Number Publication Date
EP1252432A2 EP1252432A2 (de) 2002-10-30
EP1252432B1 true EP1252432B1 (de) 2005-11-09

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Application Number Title Priority Date Filing Date
EP00988800A Expired - Lifetime EP1252432B1 (de) 2000-01-18 2000-12-15 Direktgesteuerte kraftstoffeinspritzeinrichtung für eine kolbenbrennkraftmaschine

Country Status (6)

Country Link
US (1) US6811103B2 (ja)
EP (1) EP1252432B1 (ja)
JP (1) JP2003520325A (ja)
AT (1) ATE309461T1 (ja)
DE (2) DE10001828A1 (ja)
WO (1) WO2001053688A2 (ja)

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JP2003520325A (ja) 2003-07-02
WO2001053688A3 (de) 2002-05-23
DE50011592D1 (de) 2005-12-15
ATE309461T1 (de) 2005-11-15
EP1252432A2 (de) 2002-10-30
US6811103B2 (en) 2004-11-02
WO2001053688A2 (de) 2001-07-26
DE10001828A1 (de) 2001-07-19
US20030146305A1 (en) 2003-08-07

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