EP0939857B1 - Kraftstoffeinspritzventil - Google Patents

Kraftstoffeinspritzventil Download PDF

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Publication number
EP0939857B1
EP0939857B1 EP98925392A EP98925392A EP0939857B1 EP 0939857 B1 EP0939857 B1 EP 0939857B1 EP 98925392 A EP98925392 A EP 98925392A EP 98925392 A EP98925392 A EP 98925392A EP 0939857 B1 EP0939857 B1 EP 0939857B1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
control
fuel injection
space
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
EP98925392A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0939857A1 (de
Inventor
Rudolf Heinz
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 EP0939857A1 publication Critical patent/EP0939857A1/de
Application granted granted Critical
Publication of EP0939857B1 publication Critical patent/EP0939857B1/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
    • F02M63/0059—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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/50—Arrangements of springs for valves used in fuel injectors or fuel injection pumps
    • F02M2200/502—Springs biasing the valve member to the open position
    • 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
    • F02M2200/701—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger mechanical

Definitions

  • the invention relates to a fuel injection valve the genus of claim 1.
  • a fuel injection valve the genus of claim 1.
  • the fuel injector known from DE-43 41 739 A.
  • the first and the second 2/2-way valve each as Solenoid valves formed, their valve members by each an electromagnet are operated. That means one higher effort for the control of the fuel injector.
  • it may be due to different magnet coil configurations and positioning paths for deviations in the Switching times come from each other, so with a different Response behavior of the solenoid valves is, in turn, an exact simultaneous control of the valve members the solenoid valves oppose.
  • the fuel injector according to the invention with the characteristic in contrast, features of claim 1 the advantage that a safety valve is provided, the synchronous to the control of the pressure in the control room and synchronous is controlled to the desired injection such that a Connection between the high pressure fuel accumulator and the Pressure chamber only at the time of the actual injection consists. It is a major advantage that both the 2/2 control valve and the 2/2 safety valve at the same time with just one drive are operated, the movement transmission by a hydraulic translator is done. This guarantees that the start of movement for the valve members of both valves can actually be done simultaneously and it has the further Advantage that the effort compared to separately controlled and valve elements to be actuated are eliminated.
  • a hydraulic translator with a mechanical bridge via the one actuating force hydraulically on the control valve and safety valve is transmitted.
  • the hydraulic boom can also be between the actuator and the valve members of the control valve and safety valve be arranged. The valve springs of these two valves both when the actuator is actuated opened as well, alternatively, with this control run closed.
  • the safety valve is dependent is controlled by the pressure in the control room. That enables one Cost savings when operating the two valves, the Control valve and the safety valve.
  • Another advantageous one Further development of the invention exists according to claim 15 in that the valve member with its valve body controls two valve seats, being in the passage of the valve body from one valve seat to the other a brief one Relief of the control room occurs, which is a very short Injection results.
  • a piezo actuator arrangement according to Claim 16 provided. With such an actuation arrangement can in particular very fast switching sequences can be achieved combined with a highly precise dosage of fuel injection quantity and fuel injection time.
  • Figure 1 shows a fuel injector 1 in a simplified Representation, which has an injection valve housing 2 with a bore 3 in which an injection valve member 5 is led. It has a conical shape at one end Sealing surface 6 on that with a conical valve seat 7 cooperates at the end of the hole. downstream of the valve seat 7, fuel injection openings 8 are arranged, that when the sealing surface 6 is placed on the valve seat 7 be separated from a pressure chamber 9.
  • the pressure room 9 extends over an annular space 10 around which the sealing surface 6 adjoining upstream, with a smaller one Diameter provided part 13 of the injection valve member towards valve seat 7.
  • the pressure chamber 9 is via a pressure line 12 with a high-pressure fuel source in the form of a High-pressure fuel accumulator 14 connectable, which e.g.
  • the piston-like end 20 delimits an end face 24, whose area is larger than that of the pressure shoulder 16, in the housing 2 of the fuel injection valve, a control chamber 25, which is in constant communication with a first throttle 26 the high-pressure fuel reservoir 14 and a second throttle 27 arranged in a drain channel 28 to a relief space 29 is connected.
  • the passage of the sewer 28 is controlled by a control valve 31 with which the drainage channel is either opened or closed.
  • the connection of the pressure chamber 9 to the high-pressure fuel accumulator 14 is controlled by a safety valve 32, the valve member 33 as well as the valve member 34 of the control valve 31 by a common actuating device 36 be moved to the open or closed position.
  • the Actuator 36 is operated by an electrical control unit 37 controlled according to operating parameters.
  • control valve 31 and safety valve 32 are used to control the injection quantity and injection timing of fuel in the combustion chambers of an associated Internal combustion engine, in particular a diesel internal combustion engine.
  • control valve 31 When the control valve 31 is closed because of permanent connection of the control chamber 25 with the high-pressure fuel accumulator 14 the high pressure prevailing there Level. With the safety valve still closed is the connection between high-pressure fuel accumulator 14 and the pressure chamber 9 prevented, so that even in the event of malfunction of the fuel injector no high fuel pressure is available to take off fuel injection Injector member 18 to effect.
  • the balance of power on the fuel injection valve 18 is such that at Pressure chamber 9 prevailing high fuel pressure the area of Pressure shoulder that is smaller than the area of the face 24, a smaller force in the opening direction of the injection valve member transmits as the prevailing in the control room 25 Pressure of the same amount from the fuel reservoir.
  • the prestressed acts in the closing direction Compression spring 21 so that the fuel injector is safe closed is.
  • valve member 34 of the to trigger an injection Control valve 31 brought into the open position, so the Control room 25 to the relief chamber 29 are relieved, so that decoupled by the first throttle 26 from the high-pressure fuel accumulator a pressure lower in the control room 25 Levels.
  • control valve 31 also opened the safety valve so that the connection produced between high-pressure fuel accumulator 14 and pressure chamber 9 is. Because of the different pressures, that act on the fuel injector member predominates the resulting from the load on the pressure shoulder 16 Force in the opening direction. The fuel injector member is subsequently opened and there may be a fuel injection through the injection openings 8. This happens until the control valve 31 closes again and the relief of the control room 28 is prevented.
  • the safety valve 32 ensures that in addition to control the fuel injection valve member 5 in Aufund Delivery another control of the fuel flow controlled in the high-pressure fuel reservoir 14 to the pressure chamber 9 becomes. This is done synchronously with the control of the control valve 31. However, it is not necessary that the safety valve is controlled with the accuracy as with Control valve 31 is required. With this solution is one Security against failure of such a fuel injector given. Should the control valve malfunction 31 are or should be the function of the fuel injection valve member can be impaired with help of the safety valve that is supplied to the fuel injection valve The amount of fuel can be limited so that In the event of failure of the above links, not too high Fuel injection quantity supplied to the internal combustion engine that would otherwise cause the engine to spin and would destroy them.
  • valves In the design according to Figure 1 are both valves, the Control valve 31 and the safety valve 32 as in the same Sensed seat valves executed so that when the valve members 33 and 34 are moved downwards in FIG. 1, fuel injection is prevented while, if they are moved in the opposite direction, a fuel injection he follows.
  • the control or the actuation the valve members 33 and 34 by the actuator 36 is not shown in detail in FIG. 1.
  • the Actuator for the valve members can either have individual actuators or one for both valve members have a common actuator.
  • Such Embodiment is shown for example in Figure 2.
  • Force generator for the actuators is here, in figure 2, a piezo actuation arrangement 39 is particularly advantageous provided that acts on an actuating piston 40 and thereby a very high force in a very short period of time can transmit.
  • the actuating piston delimits at the front a hydraulic space 42 to which in turn coaxial with Actuating piston a transmission piston 43 with its end face borders.
  • Actuating piston, hydraulic space 42 and Transfer pistons 43 together form a hydraulic one Translators because of the different diameters of the two pistons 40 and 43 via the hydraulic space 42 a force path transmission ratio will be set can.
  • the transmission piston 43 acts on a mechanical one Bridge 45, which adjusts the valve members 33 and 34 together.
  • the above-mentioned movable walls can of course also indirectly to the links 40, 33 mentioned and 43 act.
  • the actuating piston 40 is in turn by the piezo actuator assembly 39 moves.
  • a hydraulic translator is implemented, which guarantees that at the same time and without tolerance and friction losses the triggering force of the piezo actuator assembly 39 via the actuating piston 40 on the Valve members 33 and 34 is transmitted.
  • Figure 4 shows a modification of the embodiment of the valve members of the control valve 31 and the safety valve 32.
  • the valve members 33 and 34 instead of as in Figure 1, in which the valve members 33 and 34 each had a conical sealing surface, which cooperated with a corresponding conical valve seat, and with the actuating force exerted by the actuating arrangement 39 have been brought into the closed position, the valve members 33 'and 34' in the embodiment according to FIG. 4 are simultaneously moved into the open position when the transfer piston 43 is actuated.
  • the actuating piston 40 is again provided, which acts on the transmission piston 43 via the hydraulic space 42, which in turn adjusts the mechanical bridge 45 on which the valve members 33 'and 34' under the influence of not shown here Springs F are in the system.
  • the spring F 1 moves the valve member 33 'with a sealing surface 52 attached to a closing body 51 to bear against a safety valve seat 50.
  • the valve member 34' is also actuated by a spring F 2 with a sealing surface 54 on a closing body 55 held in contact with a control valve seat 56.
  • the closing body 51 of the valve member 33 ' is located at the end of a plunger 57 which is guided in a guide bore 58 and whose end opposite the closing body 51 is brought into contact with the mechanical bridge 45 under spring force.
  • the plunger 57 Adjacent to the sealing surface 52, the plunger 57 has an annular groove 59 which, in the closed position of the valve member 33 'shown in FIG.
  • valve body 51 defines an annular space which connects to the high-pressure fuel store via a part 12a of the pressure line 12 opening into the guide bore 58 with the high-pressure fuel store 14 is.
  • the valve body 51 can be moved back and forth in a valve chamber 60, from which the pressure line 12 leads to the pressure chamber 9. In the position shown in FIG. 4 when the piezo actuation arrangement is not energized, the connection between the high-pressure fuel accumulator 14 and the pressure chamber 9 is therefore prevented. Irrespective of this, the high-pressure fuel accumulator 14 is connected to the control chamber 25 via another line in an embodiment as shown in FIG. 1.
  • the valve member 34 'of the control valve is configured in the same way as the valve member 33'.
  • valve body 55 is adjustable in a valve chamber 62 and attached to the end of a tappet 63 guided in a guide bore 48. Between the sealing surface 54 and the adjacent part of the tappet 63 and the guide bore 48, an annular space 64 is also formed here, which is in constant communication with a part 28a of the drain channel 28.
  • the discharge channel 28 opens into the valve chamber 62 from the control chamber 25. When the valve member 34 is open, it is connected to the part 28a which leads further to the relief chamber 29.
  • valve spring of the control valve 31 and the safety valve 32 can, however, also be designed differently, as can be seen in FIG. 5, and the valve member 534 can be designed in the same way as the valve member 34 ', while the valve member 533 can be designed in the same way as the valve member 33 of Figure 1.
  • This valve member 533 then has a sealing surface 66 in the shape of a cone at the end of the valve member, which sealing surface interacts with a valve seat 67 which limits the entry into the pressure line 12, which leads to the pressure chamber 9.
  • the part 12a of the pressure line leading to the high-pressure fuel reservoir 14 opens into a valve chamber 68, into which the end of the valve member 533 projects.
  • a balance beam 70 which can be pivoted about a fixed axis 71 and on whose other lever arm the end of the valve member 534 rests and faces it the transmitting piston 43 to which, as in FIG. 4, the hydraulic chamber 42 and the actuating piston 40 and the piezo-actuating arrangement 39 are connected. If the latter is energized, the transmitter piston 43 adjusts the balance beam 70 such that the valve member 543 is moved into the open position against the force of the spring F and at the same time the valve member 533 is also moved in the open position following the balance beam 70 under the action of the spring F 1 .
  • the spring F 1 which is arranged on the valve member 534, causes the valve member 534 in the closed position and at the same time, via the balance beam 70, the valve member 533 also in the closed position against the force of the spring F 2 . This requires careful coordination of the spring forces and the actuation forces.
  • a hydraulic space 642 is again provided, which is delimited on one side by the tappet 663 of the valve member 634 and on the other side by the transmission piston 43.
  • valve member 633 For actuating the analogue from FIG. 5 executed valve member 633 this has at its end a connecting part in the form of a coupling pin 72 which dips into the hydraulic space 642 and is connected at its end to an actuating piston 73 which is guided in the housing of the fuel injector and with its end face 74 a pressurized movable wall forms, at the same time the valve member 633 is also adjusted.
  • the actuating piston borders on a pressure-relieved space 49.
  • a relief space 75 is provided, via which the leakage quantity can be discharged and which provides the necessary space for the valve element 633.
  • This is loaded in the closing direction by a spring F 2 , which holds the valve member 633 with its sealing surface 66 on the valve seat 67 when the hydraulic space 642 is not loaded.
  • the transfer piston 43 is moved when the piezo actuation arrangement 39 is excited, the pressure in the hydraulic space 642 increases, which results in a displacement of the valve member 663 by the pressurized actuating piston 73 in the opening direction against the force of the spring F 2 in the opening direction.
  • the increased pressure in the hydraulic space 642 causes a displacement of the tappet 663 and thus an opening of the control valve.
  • the valve member 634 is designed as in the corresponding valve member 43 'of FIG. 4, but with the difference that the drive here takes place directly hydraulically via the hydraulic space 692 and against the closing force of the spring F 1 .
  • valve chamber 68 on the one side over part 12a of the pressure line at all times the high-pressure fuel reservoir is connected and that of the pressure line 12 to the valve chamber 68 via the valve seat 67 leads to the pressure chamber 9.
  • the valve chamber 68 the control chamber 25 is constantly connected via the first throttle 26.
  • the control room is still analogous to the second one Throttle 27 in the drain channel 28 with the valve chamber 62 of the Control valve connected and when moved in the open position Valve member 634 connectable to the further part 28a. Control is also carried out in this exemplary embodiment to actuate the piezo actuation arrangement 39 only in the Times when fuel injection should take place.
  • valve member formed in the same way 734 as the valve member 634, 534 or 34 '.
  • Can drive one of the drives provided in FIGS. 4 to 6 becomes.
  • a safety valve with a valve element 733 provided that initially in an analogous manner as in 6 shows a conical sealing surface 766 at the end of a in the Valve chamber 768 projecting in a guide bore 95 in the injector housing 2 tightly guided plunger 757 of the valve member 733 has.
  • the sealing surface 766 acts as in FIG. 6 with the conical valve seat 67 together.
  • valve room 768 is in turn via the pressure line part 12a the fuel high pressure accumulator constantly connected and over the throttle 26 with the control chamber 25 in constant communication.
  • the pressure line 12 leads from the valve seat 67 to Print room 9.
  • the rear end face 77 of the tappet now borders 757 as a second pressure surface of the valve member 733 to one Safety valve pressure chamber 96, the one with the valve chamber 762 is connected and exposed to the pressure of the valve chamber 762 is, which is also the pressure in the control room 25, there both rooms constantly with each other via the second throttle 27 are connected.
  • the end face 77 acts a compression spring 78 which the valve member 733 in the closing direction applied.
  • Valve member 734 of the control valve 31 in the shown Closed position so has in the control room 25 on the Throttle 26 supplied high fuel pressure of the high-pressure fuel accumulator set.
  • the safety valve is advantageous switched automatically without special actuation device.
  • the safety valve always opens when the required low pressure prevails in the control chamber 25 and sufficiently high pressure for the injection stands. This can also be achieved if instead of controlling the control room pressure via the 2/2 control valve in a relief line and a throttled High pressure connection to the control room through the control a 3/2-way valve takes place, which either connects the control room with the High pressure accumulator 14 or connects to the relief chamber 29.
  • valve member 733 from FIG. 7, as in FIG 8 can be removed, a seat valve can be realized.
  • the valve member has a ball 79 which is tapered Seat 80 at the mouth of the drain channel 28 with the Valve chamber 862 interacts.
  • Figure 2 to 6 can be used.
  • valve member 733 of the safety valve in the same configuration as in FIG. 4 provided to 7.
  • the valve member 733 thus has a valve body 955 with a sealing surface 54 that with the valve seat 56 interacts. Deviating from the configuration according to the figure 4 to 7 is on the valve body 955 of the sealing surface 54 a second sealing surface 81 is provided opposite the cooperates with a second valve seat 82. This second Valve seat 82 limits the outlet of the drain channel 28 in the valve chamber 962.
  • valve member 934 When the valve member 934 is actuated due to the piezo actuation arrangement, this lifts with his Sealing surface 54 from the valve seat 56 and thus represents the Connection between drain channel 28 and drain channel part 28a via the valve chamber 962, as in the above exemplary embodiments according to Figures 4 to 7.
  • the valve member 934 moves however under the influence of the piezo actuation arrangement continue until it is with the sealing surface 81 on the second Valve seat 82 comes to rest and thus the drain channel 28 again closes.
  • the control room 25 again build up the high pressure that the fuel injector member 5 brings in the closing direction.
  • the valve member 733 is now still relieved on its end face 77, since the valve chamber 962 over the now open valve seat 56 has connection to the drain channel part 28a.
  • valve member 733 will therefore remain in the open position long until the valve member 934 of the control valve is in again Closing direction.
  • the Piezo actuation arrangement partially de-energized, so that the valve body 955 in an intermediate position in the valve chamber 962 remains, in which both valve seats 56 and 82 are open and thus the control chamber 25 is relieved.
  • the valve member 733 is then still in the open position because the End face 77 is relieved.
  • the valve member 934 is turned on again brought the valve seat 56.
  • FIG. 10 A last exemplary embodiment is shown in FIG. 10 with a modified one Shape of the safety valve.
  • the safety valve is there 833 designed as a 3/2-way valve.
  • the safety valve member 833 in turn has a tappet 857 on that in a bore of the fuel injector housing is guided and ends in a valve head 84.
  • This is adjustable in a valve chamber 85, which over the Pressure line part 12a in constant communication with the high-pressure fuel accumulator 14 is.
  • the valve chamber 85 is opened one side through a first valve seat 86 at the transition limited to the bore 57 leading to the plunger 57 and this Valve seat opposite to a second valve seat 88, formed on the discharge pressure line 12 becomes.
  • the valve head has a first one, for example a conical one Sealing surface 89 which interacts with the first valve seat 86 and on this first sealing surface 89 opposite Side a second conical sealing surface 90, the cooperates with the second valve seat 88.
  • a first sealing surface 59 and the guided part of the plunger 857 an annular groove 91 is incorporated, one Annulus 92 together with the wall of bore 87 forms the again via a pressure line 93 in which the first throttle 26 is arranged, is connected to the control room 25.
  • a safety valve element 833 equipped in this way can occur at times when fuel is to be injected at the same time, the connection from the high-pressure fuel accumulator 14 to the control chamber 25, which is relieved by the control valve was interrupted.
  • This safety valve member 833 through a corresponding drive with its valve head 84 brought into a middle position, so the Control room 25 brought to a pressure level that between the Maximum pressure and the completely relieved pressure is.
  • This medium pressure causes the fuel injector member to open less 12 such that over a short Time a small amount of fuel injection for the purpose of Pre-injection can be introduced. This is done by the small opening of the fuel injector also one Formatting of the fuel injection jet possible with a Throttling the fuel supply to the fuel injection ports.
  • the safety valve designed according to FIG. 10 can thereby both by a separate piezo actuator arrangement as also operated via a jointly translated actuation arrangement be the valve member of the control valve controls.
  • a separate piezo actuator arrangement assigned to the safety valve Control by a piezo actuator arrangement required, which with partial excitation also partial paths of adjustment can perform.
  • the control valve can in this case can also be operated by an electromagnet.

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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)
EP98925392A 1997-09-25 1998-03-14 Kraftstoffeinspritzventil Expired - Lifetime EP0939857B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19742320A DE19742320A1 (de) 1997-09-25 1997-09-25 Kraftstoffeinspritzventil
DE19742320 1997-09-25
PCT/DE1998/000766 WO1999015778A1 (de) 1997-09-25 1998-03-14 Kraftstoffeinspritzventil

Publications (2)

Publication Number Publication Date
EP0939857A1 EP0939857A1 (de) 1999-09-08
EP0939857B1 true EP0939857B1 (de) 2003-08-20

Family

ID=7843589

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98925392A Expired - Lifetime EP0939857B1 (de) 1997-09-25 1998-03-14 Kraftstoffeinspritzventil

Country Status (9)

Country Link
US (1) US6328017B1 (zh)
EP (1) EP0939857B1 (zh)
JP (1) JP2001505975A (zh)
KR (1) KR20000069030A (zh)
CN (1) CN1114757C (zh)
DE (2) DE19742320A1 (zh)
ES (1) ES2206937T3 (zh)
RU (1) RU2222709C2 (zh)
WO (1) WO1999015778A1 (zh)

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DE59809337D1 (de) 2003-09-25
ES2206937T3 (es) 2004-05-16
JP2001505975A (ja) 2001-05-08
RU2222709C2 (ru) 2004-01-27
US6328017B1 (en) 2001-12-11
CN1241240A (zh) 2000-01-12
DE19742320A1 (de) 1999-04-01
CN1114757C (zh) 2003-07-16
EP0939857A1 (de) 1999-09-08
WO1999015778A1 (de) 1999-04-01

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