EP1520096B1 - Systeme a rampe commune comprenant une buse variable et un systeme multiplicateur de pression - Google Patents

Systeme a rampe commune comprenant une buse variable et un systeme multiplicateur de pression Download PDF

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Publication number
EP1520096B1
EP1520096B1 EP03722255A EP03722255A EP1520096B1 EP 1520096 B1 EP1520096 B1 EP 1520096B1 EP 03722255 A EP03722255 A EP 03722255A EP 03722255 A EP03722255 A EP 03722255A EP 1520096 B1 EP1520096 B1 EP 1520096B1
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EP
European Patent Office
Prior art keywords
pressure
nozzle
space
needle part
fuel
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
EP03722255A
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German (de)
English (en)
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EP1520096A1 (fr
Inventor
Hans-Christoph Magel
Andreas Kellner
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Robert Bosch GmbH
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Robert Bosch GmbH
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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
    • 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
    • F02M57/025—Injectors structurally combined with fuel-injection pumps characterised by the pump drive hydraulic, e.g. with pressure amplification
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/08—Injectors peculiar thereto
    • F02M45/086—Having more than one injection-valve controlling discharge orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/105—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive hydraulic drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/46—Valves, e.g. injectors, with concentric valve bodies

Definitions

  • both pressure-controlled and stroke-controlled injection systems can be used.
  • fuel injection systems come next pump-nozzle units, pump-line-nozzle units and accumulator injection systems (common rail) are used.
  • accumulator injection systems make it possible to adjust the injection pressure to the load and speed of the internal combustion engine. Achieving high specific power and reducing emissions generally requires the highest possible injection pressure.
  • EP 0 562 046 B1 discloses a control and valve arrangement with damping for an electronically controlled injection unit.
  • the actuation and valve assembly for a hydraulic unit comprises an electrically energizable solenoid assembly having a fixed stator and a movable armature.
  • the anchor has a first and a second surface.
  • the first and second surfaces of the armature define first and second cavities, with the first surface of the armature facing the stator. It is provided a valve which is connected to the armature.
  • the valve is capable of delivering a hydraulic actuating fluid to the injector from a sump.
  • a damping fluid may be accumulated or drained therefrom with respect to one of the cavities of the solenoid assembly.
  • the flow connection of the damping fluid can be selectively released or closed in proportion to its viscosity.
  • DE 101 23 910.6 relates to a fuel injection device. This is used on an internal combustion engine.
  • the combustion chambers of the internal combustion engine are supplied with fuel via fuel injectors.
  • the fuel injectors are acted upon by a high pressure source;
  • the fuel injection device comprises a pressure booster, which has a movable pressure booster piston, which separates a connectable to the high-pressure source space from a high-pressure chamber connected to the fuel injector.
  • the fuel pressure in the high-pressure chamber can be varied by filling a rear space of the pressure booster device with fuel or by emptying the rear space of the fuel booster from fuel.
  • the fuel injector includes a movable closing piston for opening or closing injection openings.
  • the closing piston protrudes into a closing pressure chamber, so that the closing piston can be pressurized with fuel. As a result, a force acting on the closing piston in the closing direction is achieved.
  • the closing pressure chamber and another space are formed by a common working space, wherein all portions of the working space are permanently connected to each other for the exchange of fuel.
  • Document JP61053455 discloses a fuel injection device according to the preamble of claim 1.
  • a further improvement of the emission values and the noise behavior of a self-igniting Internal combustion engine can be achieved by using a Vario injector.
  • a pressure booster which acts on a nozzle space of the injection nozzle with high pressure fuel, on the one hand can achieve a very high injection pressure, on the other hand, the use of a Vario injector allows the release of different sized injection cross sections.
  • the injection of fuel can be realized via two different injection cross sections formed at the combustion chamber end of the fuel injector.
  • the injection openings are favoring the atomization behavior of the fuel in an advantageous manner, procure as concentric bolt circles.
  • the injection of fuel takes place via an injection cross-section released by a first nozzle needle part. If the injection pressure further increased, can be injected via an additional injection cross-section, which is then released by another nozzle needle part.
  • a smaller quantity of fuel reaches the combustion chamber at a lower injection pressure. This favors the mixture preparation in the combustion chamber of the self-igniting internal combustion engine during a boot phase.
  • the second nozzle needle part opens, so that, in addition to the injection cross-section released by the first nozzle needle part, by releasing a further injection cross-section at a higher pressure level, a larger quantity of fuel enters the combustion chamber of the internal combustion engine.
  • the gas contained in the combustion chamber can be processed by a previous boot injection in a way that promotes combustion of the combustion.
  • the solution according to the invention allows the injection of smallest amounts of fuel with short injection periods and the injection of larger amounts of fuel over longer injection periods; If appropriate, smaller pilot injections can also be realized with the solution proposed according to the invention.
  • Small pilot injections improve the noise performance of a self-igniting internal combustion engine.
  • the use of very small pre-injection quantities into the combustion chamber of the self-igniting internal combustion engine achieves an improvement in exhaust emissions.
  • a noise improvement can be achieved in self-igniting internal combustion engines to the extent that the "nailing" can be largely prevented by the formation of the injection rate.
  • Figure 1 is the hydraulic circuit diagram of a fuel injector with pressure booster, Vario injector and coaxial nozzle needle refer to the closing space from the back space of the pressure booster from fuel can be acted upon.
  • the fuel injection device shown in Figure 1 comprises a fuel injector 1, which is supplied via a high-pressure accumulator chamber 2 (common rail) with fuel under high pressure.
  • the fuel injection device contains in addition to the high-pressure accumulator 2, the fuel injector 1, a pressure booster 5, as well as designated by reference numeral 6 injection valve, via which in a here reproduced only schematically combustion chamber 7 of a self-igniting internal combustion engine at the combustion chamber end of the injection valve 6 fuel is injected into this.
  • high-pressure accumulator space 2 fuel passes through a first throttle point 3 and an adjoining this line 4 in a pressure chamber 11 of the booster 5.
  • the pressure booster 5 includes in addition to the mentioned pressure chamber 11, a rear space 16.
  • a piston 12 is accommodated, which is designed as an axially displaceable stepped piston and comprises a first part piston 13, which is formed in comparison to a second part piston 14 with a guide enabling larger diameter.
  • the piston 12 may consist of two separate components as well as be manufactured as one component.
  • a lug-shaped projection 15 is provided between the first partial piston 13 and the second partial piston 14.
  • the second partial piston 14 defines with its front side a high-pressure chamber 20 of the pressure intensifier. about which u.a. a high pressure line 28 branches off, which acts on a nozzle chamber 29 of the injection valve 6 at very high pressure fuel.
  • a line 18 From the pressure chamber 11 of the pressure booster 5 branches off a line 18 to a magnetic valve 8 designed as a control valve, which is formed in the embodiment of the proposed fuel injection device shown in Figure 1 as a solenoid valve.
  • the supply line 18 from the pressure chamber 11 of the pressure booster 5 is connected to a fuel line 19 in communication, via which the rear space 16 of the booster 5 is supplied with fuel.
  • the check valve 24, which is arranged upstream of the high-pressure chamber 20 of the pressure booster 5, comprises a closing body 26 designed here as a ball, which in turn is acted upon by a spring element 27.
  • a check valve 24 between the high-pressure chamber 20 of the pressure booster 5 and the closing chamber 21 may - as indicated in Figure 1 - and a throttle element 24.1 be included in the line 25, which from the pressure medium, i. the fuel can be flowed through in both directions.
  • the injection valve 6 illustrated in the embodiment variant of the proposed fuel injection device according to FIG. 1 comprises a coaxial nozzle needle 30 which contains a first nozzle needle part 31 and a second nozzle needle part 32.
  • the nozzle needle parts 31 and 32 are guided into each other and operated independently.
  • the first nozzle needle part 31 is movable up and down within the housing of the injection valve 6 in the vertical direction.
  • the stroke limit of the first nozzle needle part 31 is given by a recessed into the closing chamber 21 of the injection valve 6 annular stop 33. By means of the ring-shaped stop 33 in the closing space 21, the maximum stroke is given to the first nozzle needle part 31 and limited.
  • the closing space 21 of the injection valve 6 comprises a pin-shaped stop 34, which serves as a stroke limiter for the first nozzle needle part 31 coaxially guided second nozzle needle part 32 of the coaxial nozzle needle 30.
  • a disc-shaped abutment surface 37 is formed in the upper region of the second nozzle needle part 32, which cooperates with the abutment 34 located within the closing space 21 and serves as a stroke limiter and predetermines its vertical movement within the housing of the injection valve 6 to the second nozzle needle part 32 ,
  • both the first nozzle needle member 31 and the second nozzle needle member 32 are each acted upon by a spring element 38 and 39, respectively.
  • the spring element 38 acting on the first nozzle needle part 31 is supported on an end face 36 of the first nozzle needle part 31, while the spring element 39 surrounding the pin-shaped stop 34 rests against the end face 37 of the second nozzle needle part 32.
  • the closing space 21 shown in FIG. 1 is supplied with fuel from the rear space 16 of the pressure booster 5 via the return space line 22, wherein the return space line 22 may contain a throttle point 23 in the region of its mouth in the closing space 21.
  • the opening from the check valve 24 in the closing chamber 21 line 25 may open into the closing chamber 21, wherein instead of integrated in Figure 1 in the line 25 check valve 24 and the throttle element indicated in Figure 1 24.1 in the line 25 between the high-pressure chamber 20 of the pressure booster. 5 and the closing space 21 can be inserted.
  • first nozzle needle member 31 of the coaxial nozzle needle 30 comprises a hydraulically effective surface 35 which is formed in the illustrated embodiment as a pressure shoulder 35 tapered.
  • the pressure shoulder 35 on the outer peripheral surface of the first nozzle needle part 31 is completely enclosed by the nozzle chamber 29 of the injection valve 6.
  • an annular gap 50 extends to the combustion chamber end of the injection valve 6.
  • the second nozzle needle member 32 also includes a hydraulically effective surface 40 in the form of a pressure shoulder, which is formed at the combustion chamber end of the second nozzle needle portion 32.
  • a switching pressure can be adjusted according to the dimensions, in which the inner nozzle needle portion 31 of the coaxial nozzle needle 30 as shown in FIG 1 opens.
  • the nozzle of the injection valve 6 designed as a vario injection nozzle 41 comprises a first injection cross section 42 and a further, second injection cross section 43.
  • the first injection cross section 42 and the second injection cross section 43 are formed as rows of holes, for example as a concentric hole circles, and contain a variety of smallest holes, which during the injection of fuel into the combustion chamber 7 - here only schematically reproduced - a fine atomization of the fuel during the injection process is achieved, which in turn a favorable combustion process in terms the emission levels and the noise level.
  • the first injection section 42 is released when opening the first nozzle needle member 31 upon application of the nozzle chamber 29 at high pressure.
  • the hydraulically effective surface 40- here designed as a pressure shoulder - and depending on the dimensions of the second nozzle needle part 32 beauf beating spring element 39, opens the second nozzle needle portion 32 of the coaxial nozzle needle 30 at a certain switching pressure and are in addition to the first injection section 42, the further, second injection section 43 free.
  • this switching state-both nozzle needle parts 31 and 32 open-fuel is injected both via the first injection cross-section 42 and additionally via the second, second injection cross-section 43 released by the first nozzle needle part 31 into the combustion chamber 7 of the self-igniting internal combustion engine.
  • the adjusting at the high pressures guide leakage due to the nested needle nozzle parts 31 and 32 of the coaxial nozzle needle 30 via a recess 48 which may be formed, for example, as an annular groove to the outer periphery of the second nozzle needle member 32 via a channel 47, which the first nozzle needle member 31st penetrated, promoted in a surrounding this further annular groove 46, which in turn is on the housing side with a leakage oil passage 49 in communication. Accordingly, the guide leakage can be discharged via the leak oil line 49 into the low-pressure region of the fuel injection system analogously to the low-pressure-side return 9, which is assigned to the solenoid valve 8.
  • the second nozzle needle part 32 closing space is formed on the one hand by the end face 45 of the first nozzle needle member 31 and on the other hand by the conical in the combustion chamber 7 of the self-igniting internal combustion engine projecting nozzle body surface 44 of the injection valve. 6
  • the mode of operation of the embodiment variant shown in FIG. 1 is as follows. Via line 4, the pressure prevailing in the high-pressure reservoir 2 is applied to the fuel injector 1. In the illustrated in Figure 1 basic state, the solenoid valve 8 is not activated and there is no injection instead. The pending in the high-pressure reservoir 2 pressure is therefore in the pressure chamber 11 of the booster 5 and the aforementioned solenoid valve 8. Furthermore, the pending in the high-pressure accumulator 2 pressure on the through-connected solenoid valve 8 and the fuel line 19 in the rear chamber 16 of the booster 5 at.
  • the rail pressure is on the return space line 22 and the throttle body 23 received in this in the closing chamber 21 of the injection valve 6 and flows from the closing chamber 21 of the injection valve 6 in the release direction of the check valve 24 in the high pressure chamber 20 of the booster 5 over.
  • the fuel flows via the high-pressure line 28 into the nozzle chamber 29 of the injection valve 6.
  • all the pressure chambers 11, 16 and 20 of the pressure booster 5 are acted upon by the pressure level prevailing in the high-pressure reservoir 2, wherein the partial pistons 13 and 14 of the pressure booster 5 are pressure-balanced.
  • the pressure booster 5 is deactivated and there is no pressure amplification.
  • the piston 12 of the pressure booster 5 is placed on its associated return spring 17 in its initial position, with a filling of the high-pressure chamber 20 of the booster 5 via the check valve 24 from the closing chamber 21 of the injection valve 6 is made. Due to the pending in the closing chamber 21 pressure is a hydraulic closing force the nozzle needle parts 31 and 32 of the coaxially formed nozzle needle 30 is constructed. In addition, the first nozzle needle part 31 and the second nozzle needle part 32 are acted upon via the closing elements 21 arranged in the spring elements 38 and 39 in the closed position.
  • the pressure level present in the high-pressure accumulator 2 can constantly be present in the nozzle chamber 29 of the injection valve 6 via the high-pressure line 28, without the first nozzle needle part 31 opening onto the pressure shoulder 35 due to the pressure effect of the fuel. Only when the pressure in the nozzle chamber 29 rises above the high-pressure reservoir 2 prevailing pressure, which takes place by connecting the booster 5, opens the first nozzle needle member 31 and the injection begins.
  • the high pressure is in the nozzle chamber 29 as long as the back space 16 is relieved of pressure via the switched solenoid valve 8 in the low-pressure side 9. Due to the pressure relief of the back space 16 and the closing chamber 21 of the injector 6 is relieved via the line 22 in the rear space 16 of the booster 5, which in turn is relieved via the aforementioned line 19 to the low pressure side 9 of the fuel injection system. As long as the rear space 16 of the booster 5 is drukkentlastet, the pressure booster 5 remains activated and compresses the fuel in the high-pressure chamber 20.
  • the compressed fuel is passed through the nozzle chamber 29 along the annular gap 50 to the first injection section 42, due to the vertical movement on the first Düsennadelteils 31 is released, so that the inflowing over the annular gap 50 fuel is injected via the first injection section 42 into the combustion chamber 7 of the self-igniting internal combustion engine. Due to the pressure relief of the rear space 16 of the pressure booster 5, the closing chamber 21 of the injection valve 6 is pressure relieved.
  • a switching pressure can be adjusted, from which the coaxially guided in the first nozzle needle part 31 second nozzle needle member 32 opens and this associated further, second injection section 43 releases. Accordingly, at a pressure level below the adjustable switching pressure of the second nozzle needle part 32, both the first nozzle needle part 31 can be opened and thereby the first injection cross section 42 can be released, while the second nozzle needle part 32 remains closed. In this state, an injection of fuel via the first injection cross-section 42.
  • the solenoid valve 8 is switched, so that the rear space 16 of the pressure booster 5 and the closing chamber 21, connected to the rear space 16 via the line 22, are separated from the low pressure side 9 of the solenoid valve 8.
  • the return chamber 16 is acted upon via the supply line 18 from the pressure chamber 11 of the pressure booster 5 with the pressure level prevailing in the high-pressure storage space 2, so that the rail pressure level builds up again in the rear space 16. Due to this, the pressure in the high-pressure chamber 20 of the pressure booster 5 decreases to the pressure level prevailing in the high-pressure reservoir 2.
  • both the first nozzle needle part 31 and the second nozzle needle part 32 of the coaxial nozzle needle 30 are pressure-balanced. Due to the loading of the first nozzle needle part 31 and the second nozzle needle part 32 with spring elements 38 and 39, the nozzle needle parts 31, 32 of the coaxial nozzle needle 30 are placed in their closed position. Then the injection is finished.
  • the closing speed, with which the first nozzle needle part 31 and the second nozzle needle part 32 are pressed into their closed positions, can be influenced via the inlet throttle 23, which is received in the return chamber line 22 from the rear space 16 to the closing space 21 of the injection valve 6.
  • the piston 12 comprising a first sub-piston 13 and a sub-piston 14, in one-piece or in a separate embodiment by the return spring 17 returned to its original position.
  • a relief 46, 47, 48 in a leak oil line 49 is provided on the coaxial nozzle needle 30 according to the embodiment in FIG. 1, via which the guide leak can be discharged into the low-pressure region of the fuel injection system.
  • FIG. 2 shows the hydraulic circuit diagram of a fuel injector with a pressure booster, a Vario injection nozzle and a closing space of an injection valve of the fuel injector which can be directly acted upon via a high-pressure reservoir.
  • the variant shown in Figure 2 differs from the variant shown in Figure 1 in that the closing chamber 21 of the injector 6 via a branching off from the line 4 Hoch Kunststoffabzweig 60 directly bypassing the solenoid valve 8 and the rear chamber 16 of the booster 5 with the in the high-pressure reservoir 2 pending pressure level can be acted upon.
  • Another difference from the embodiment of Figure 1 is that according to the embodiment shown in Figure 2, only the first nozzle needle member 31 of the coaxial nozzle needle 30 is acted upon by acting as a closing spring spring element 38 on the end face 36.
  • the embodiment shown in Figure 2 is identical to the embodiment which has already been described in connection with Figure 1.
  • the solenoid valve 8 which may be formed as a piezoelectric actuator or may be designed as a direct-operated valve or servo valve, switched so that the pressure in the space 11 of the booster 5 pending pressure corresponding to the pressure in the high-pressure reservoir 2 , via the fuel line 19 in the rear space 16 is present. Furthermore, the pressure level in the high-pressure reservoir 2 via the line 4 to the branch 60 in the closing chamber 21 of the injection valve 6. About the outgoing from the closing chamber 21 check valve line 25, the high-pressure chamber 20 of the pressure booster 5 with rail pressure level, i. the pressure level, which prevails in the high-pressure accumulator space 2, acted upon. Furthermore, via the high-pressure line 28, which starts from the high-pressure chamber 20 of the pressure booster 5, the pressure level prevailing in the high-pressure reservoir 2 is also present in the nozzle chamber 29 of the injection valve 6.
  • the metering of the fuel to the combustion chamber end of the injection valve 6 is effected by a pressure relief of the back space 16 of the pressure booster 5 by activating the example designed as a 3/2-way valve solenoid valve 8.
  • the back space 16 is thereby separated from the Systemtikbeaufschlagung and the low pressure line 9, which emanates from the solenoid valve 8, connected.
  • the pressure booster 5 is activated, ie the piston 12 moves due to the pressure prevailing in the pressure chamber 11, the pressure level of the high pressure accumulator chamber 2 corresponding pressure down, whereby the pressure in the high pressure chamber 20 and the high pressure line 28 also in the control chamber 29 of the injection valve 6 increases.
  • the first nozzle needle part 31 is designed so that its opening occurs when in the nozzle chamber 29, a first opening pressure p ö, 1 is reached. As long as the rear space 16 of the pressure booster 5 remains depressurized, the pressure booster 5 is activated. The pressure in the nozzle chamber 29 and at the needle tip of the second nozzle needle part 32 is increased in the further course of the injection up to a maximum pressure level p max .
  • the second nozzle needle part 32 opens, whereby the further, second injection cross section 43 is opened and now an injection of fuel into the combustion space 7 of the self-igniting internal combustion engine via both the first injection cross section 42, the one from first nozzle needle part 31 is released, as well as via the further, second injection cross-section 43 takes place, which is released by the second nozzle needle part 32.
  • the first opening pressure p ö, 1 is essentially determined by the hydraulically effective surfaces, ie the design of the pressure shoulder 35 in the nozzle chamber 29, as well as the dimensioning of the end face 36 of the first nozzle needle member 31 and thus directly proportional to the pressure prevailing in the high-pressure reservoir 2 pressure level.
  • the second opening pressure p ö, 2 is also essentially determined by the hydraulic pressure surface 40 at the needle tip of the second nozzle needle part 32 and the dimensioning of the end face 37, which assigns the closing space 21 of the injection valve 6. Also, the second opening pressure p ö, 2 is proportional to the pressure prevailing in the high-pressure accumulator 2 pressure level.
  • the return space 16 of the pressure booster 5 is pressurized by the solenoid valve 8 with system pressure, i. the high-pressure accumulator 2, connected.
  • the closing speed can be influenced by the dimensioning of the throttle point 23, which is pre-connected to the closing space 21 and received in the branch 60.
  • the guide leakage abhnende designed as annular grooves recesses 46 and 48, for example, which are in communication with a drain line 49, which the discharged guide leakage for example, returns to a fuel tank, not shown here.
  • the piston 12 of the pressure intensifier 5 can be designed in one or in several parts.
  • the return spring 17, which is received in the rear space 16 of the booster 5, can be arranged both in the pressure chamber 11 of the booster 5 and in the high-pressure chamber 12 of the booster 5.
  • FIG. 3 shows the pressure curves in the nozzle chamber, high-pressure chamber and in the closing space as well as the needle stroke movement and the flow cross-sections corresponding to the needle stroke paths on the vario nozzle of the embodiment according to FIG.
  • the rail pressure level p rail is present in the high-pressure reservoir 2.
  • the first opening pressure p ö, 1 is reached, so that the first nozzle needle part 31 opens due to the force acting in the control chamber 29 on the pressure shoulder 35 of the first nozzle needle member 31 hydraulic force.
  • a first injection quantity 74 sets, which arrives during the opening phase between t 2 and t 3 of the first nozzle needle part 31 in the combustion chamber 7 of the self-igniting internal combustion engine.
  • the amount of fuel injected into the combustion chamber 7 of the self-igniting internal combustion engine increases according to the quantity indicated by reference numeral 75, ie, in addition to the first injection cross section 42, released by the first nozzle needle part 31, an injection of fuel into the combustion chamber 7 of the internal combustion engine takes place via the first injection cross-section 42 as well as over the other, second injection cross-section 43, which is now released due to the lifting movement of the second nozzle needle part 32.
  • the back space 16 of the booster 5 is again connected to the system pressure by means of the solenoid valve 8, so that a pressure reduction in the control chamber 29 and in the high-pressure chamber 20 of the booster 5 adjusts according to a pressure build-up in the back space 16 and therefore, as above described, the forces acting on the first nozzle needle portion 31 and the second nozzle needle member 32 opening forces on the hydraulic surfaces 35 and 40 and the closing forces in the closing chamber 21 closing forces, ie the first nozzle needle member 31 acting spring, and in the closing space 21 on the Lines 4 and 60 pending pressure level of the first nozzle needle member 31 is transferred to its closed position, whereby the injection finds its end.
  • FIG. 4 shows an embodiment variant of a fuel injector with pressure booster and vario-injection nozzle with optimized pilot leakage.
  • a regulated high-pressure delivery unit 81 delivers fuel from a fuel tank 80 into a high-pressure storage space 2.
  • a throttle point 3 containing line 4 in the pressure chamber 11 of the booster 5 at.
  • From the line 4 branches off in front of the pressure chamber 11 from a line 18, via which the solenoid valve 8 is acted upon.
  • From the solenoid valve 8 from the pressure level of the high-pressure accumulator 2 is in the switching position shown in Figure 4 in the rear space 16 of the booster 5, in which analogous to the embodiments shown in Figure 1 and 2 of the invention proposed solution, a return spring 17 is added.
  • the return spring 17 is supported on the housing side in the rear space 16 of the booster 5 and acts on a diameter enlarged first part piston 13 of a two-part piston 12, which with his second sub-piston region 14 a high-pressure chamber 20 - analogously to the illustrations according to Figures 1 and 2 - acted upon.
  • the injection valve 6 according to the embodiment in Figure 4 comprises a coaxial nozzle needle 30 having a first nozzle needle portion 31 and a further, inner nozzle needle portion 32.
  • the inner, second nozzle needle part 32 of the coaxial nozzle needle 30 is associated with a separately pressure-relieving nozzle spring chamber 83 which is depressurized via interposition of a throttle point 86 in the low pressure lines 9 and from there into the fuel tank low pressure side.
  • a further throttling point 85 containing supply line from the high pressure line 19 to the rear space 16
  • a first nozzle spring chamber 82 which acts on the first nozzle needle part 31, filled.
  • a sleeve-shaped body 89 with a shoulder serves to seal the second nozzle control chamber 83 with respect to the first nozzle control chamber 82.
  • the sleeve-shaped body 89 has a high pressure-tight guide relative to the second nozzle needle part 32 and a flat sealing seat with respect to the injector body.
  • the sleeve-shaped body 89 may be pressurized from the first nozzle control chamber 82, which acts vertically upward to produce an additional sealing force.
  • both the first spring element 38 and the second spring element 39 is supported.
  • the spring element 39 assigned to the second nozzle needle part 32 acts on a stop 87 formed on the circumference of the second nozzle needle part 32, while the spring element designated by reference numeral 38 acts directly on the end face 36 of the first, outer nozzle needle part 31.
  • the second nozzle needle part 32 is provided for discharging the guide leakage with a longitudinal bore 84, via which a recess 48 provided on the outer circumference of the second nozzle needle part 32 is in communication with the second nozzle spring chamber 83 which can be depressurized on the low-pressure side.
  • the pressure level prevailing in the high-pressure reservoir 2 lies in the pressure chamber 11 of the pressure booster 5 on the solenoid valve 8 the line 19 in the rear space 16 of the pressure booster 5 in the first nozzle spring chamber 82 of the injection valve 6 and via the check valve 24 in the high-pressure chamber 20 of the pressure booster 5 and in over the fuel supply line 28 can be acted upon by high pressure nozzle chamber 29 of the injector.
  • the pressure-relieving second nozzle spring chamber 83 above the end face 37 of the second nozzle needle part 32 is connected via the throttle point 86 and the discharge line 88, bypassing the solenoid valve 8 directly to the return line 9 in the fuel tank 80 of the fuel injection system.
  • a closing spring force acts on the first nozzle needle part 31 and the other, second nozzle needle part 32 via the spring elements 38 and 39 respectively. For this reason, the pressure level prevailing in the high-pressure reservoir 2 can always be present in the nozzle chamber 29 without an opening of the first nozzle needle part 31 sets. Only when the pressure within the nozzle chamber 29 rises above the pressure level of the high-pressure reservoir 2, which is achieved by connecting the pressure booster 5, does the first nozzle needle part 31 open and the injection begins.
  • the metering of the fuel by the pressure relief of the back space 16 is analogous to the embodiments in Figures 1 and 2. This is done by a circuit of the example designed as a 3/2-way control valve solenoid valve 8. It is a separation of the back space 16 of Pressure booster 5 and the system pressure, ie the pressure prevailing in the high-pressure accumulator 2 pressure level, and a connection of the back space 16 with the return line 9 to the fuel tank 80, ie with the low pressure side.
  • the pressure in the rear chamber 16 drops, whereby the pressure booster 5 is activated and an increase in the pressure level in the high-pressure chamber 20, an increase in the pressure in the nozzle chamber 29, which in turn acts on the hydraulic surface 35 of the first nozzle needle member 31 and its Auffahrschul against the spring force causes the spring element 38 in the opening direction.
  • the pressure booster 5 remains activated and compresses the fuel in the high-pressure chamber 20.
  • the compressed fuel flows from there to the nozzle needle, ie the nozzle chamber 29, and from there via the annular gap 50 in the direction of the combustion chamber end the first and second nozzle needle parts 31 and 32, respectively.
  • the first one Nozzle spring chamber 82 remains relieved of pressure, but at the needle tip of the second nozzle needle part 32, an injection pressure level builds up.
  • a pressure force acting on the hydraulically effective surface 40 (pressure shoulder) in the opening direction of the second nozzle needle part 32 adjusts at the tip of the second nozzle needle part 32.
  • the second nozzle spring chamber 83 associated with the second nozzle needle part 32 is still relieved of pressure, follows as closing force on the second nozzle needle member 32, the spring elements 39.
  • About a suitable dimensioning of the pressure shoulder 80 with respect to the closing force of the spring element 39 can be analogous to the representation of the embodiment set according to Figure 1, a switching pressure, from which the internally guided in the coaxial nozzle needle 30 second nozzle needle part 32 opens.
  • the first nozzle needle part 31 opens, while the second nozzle needle part 32 remains closed. Accordingly, injection takes place via the first injection cross-section 42.
  • the second nozzle needle part 32 opens in addition to the already open first nozzle needle part 31, whereby an injection into the combustion chamber 7 of the internal combustion engine both via the first injection cross-section 42 also takes place via the further, second injection cross section 43.
  • the termination of the injection is effected by means of the solenoid valve 8, via which the rear space 16 of the pressure booster 5 and the first nozzle spring chamber 82 separated from the return side 9 of the solenoid valve 8 and with the supply pressure, i. be connected to the pressure prevailing in the high-pressure reservoir 2 pressure level.
  • the pressure level prevailing in the high-pressure reservoir 2 builds up in the rear space 16, whereby a pressure relief in the high-pressure chamber 20 of the pressure booster 5 is set to the rail pressure level.
  • the first nozzle needle member 31 is now balanced in terms of hydraulic forces and is actuated only by the spring force of the spring element 39, i. closed.
  • the self-adjusting closing speed with respect to the second nozzle needle part 32 can be influenced by the design of the throttle bodies 85 and 86, respectively.
  • a relief line in the form of a bore 84 is guided through the second nozzle needle part 32, which extends from a recess 48 into the second nozzle control chamber 83.
  • the following three foundedsleckageströme set in the idle state ie at applied rail pressure level in the closing chamber 21 and the nozzle control chamber 29 on.
  • the second nozzle needle part 32 is formed in a diameter d 2 , which may be between 2 to 2.5 mm, while the first nozzle needle part 31 is formed in an outer diameter d 1 , which may be between 4 and 4.5 mm.
  • d 1 an outer diameter
  • d 2 an outer diameter
  • d 1 a guide leakage flow on a small diameter d 2 . 4
  • a leakage oil groove 48 is likewise received in an analogous manner, which communicates with the longitudinal bore 84, via which the leak oil can be removed.
  • a second pilot leakage flow with a small diameter d 2 occurs between the nozzle control chamber 82 and the leak oil groove 48. Due to the smaller diameter of the second nozzle needle part 32 of 2 to 2.5 mm can be achieved with this embodiment, a significant reduction of previous leakage oil volume flows into the leak.

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

Claims (24)

  1. Installation d'injection de carburant pour des moteurs à combustion interne, comportant un injecteur de carburant (1) alimenté par une source de carburant à haute pression (2, 81), avec :
    - entre la soupape d'injection (6) et la source de carburant à haute pression (2, 81) un amplificateur de pression (5) comportant un piston démultiplicateur (12) séparant une chambre de pression (11) reliée à la source de carburant à haute pression (2, 81) d'une chambre haute pression (20) alimentant la chambre de buse (29) de l'injecteur (1), une variation de pression dans une chambre de retour (16) de l'amplificateur de pression (5) produisant une variation de pression dans la chambre haute pression (20), et
    - la soupape d'injection (6) ayant une aiguille d'injecteur (30) libérant ou fermant les orifices d'injection dirigés vers la chambre de combustion (7), l'aiguille d'injecteur (30) ayant une première partie (31) et une seconde partie (32) commandées en fonction de la pression et libérant ou fermant des sections d'injection différentes (42, 43) de la buse d'injection (41),
    caractérisée en ce que
    les parties (31, 32) de l'aiguille d'injecteur (30) sont guidées l'une dans l'autre, et
    la première partie (31) et la seconde partie (32) de l'aiguille d'injecteur sont sollicitées contre l'action de ressorts de fermeture (38, 39) par la pression du carburant dans une première chambre de commande de buse (82), avec interposition d'un point d'étranglement (85).
  2. Installation d'injection de carburant selon la revendication 1,
    caractérisée en ce que
    les parties (31, 32) de l'aiguille d'injecteur (30) ont des surfaces (35, 40) sollicitées pour l'actionnement par la pression hydraulique.
  3. Installation d'injection de carburant selon la revendication 2,
    caractérisée en ce que
    la première partie (31) de la buse comporte un épaulement de pression (35) sollicité par le carburant à haute pression arrivant dans la chambre de buse (29).
  4. Installation d'injection de carburant selon la revendication 2,
    caractérisée en ce que
    la seconde partie (32) de l'aiguille d'injecteur comporte un épaulement de pression (40) prévu à son extrémité située du côté de la chambre de combustion.
  5. Installation d'injection de carburant selon la revendication 2,
    caractérisée en ce qu'
    une chambre hydraulique actionnant la seconde partie (32) de l'aiguille de buse par l'intermédiaire d'un épaulement de pression (40) est délimitée par une surface frontale (45) de la première partie d'aiguille (31) et par une surface de corps de buse (44) du côté de la chambre de combustion.
  6. Installation d'injection de carburant selon la revendication 5,
    caractérisée en ce que
    la surface du corps de buse (44) située du côté de la chambre de combustion a une forme conique.
  7. Installation d'injection de carburant selon la revendication 5,
    caractérisée en ce que
    la chambre hydraulique entourant l'épaulement de pression (40) dans la seconde partie (32) de l'aiguille de buse est sollicitée par le carburant de la chambre de buse (29) par l'intermédiaire d'un intervalle annulaire (50) lorsque la première partie (31) de l'aiguille de buse est actionnée dans le sens de l'ouverture.
  8. Installation d'injection de carburant selon la revendication 1,
    caractérisée en ce que
    des butées de limitation de course (33, 34) installées dans une chambre de fermeture (21) sont associées à la première partie (31) et à la seconde partie (32) de l'aiguille de buse, et au moins l'une des parties d'aiguille de buse (31, 32) est sollicitée par un élément de ressort de fermeture (38, 39).
  9. Installation d'injection de carburant selon la revendication 1,
    caractérisée en ce que
    la première partie (31) de l'aiguille de buse libère ou ferme une première section d'injection (42) et la seconde partie d'aiguille de buse (32) libère ou ferme une seconde section d'injection (43).
  10. Installation d'injection de carburant selon la revendication 9,
    caractérisée en ce qu'
    après libération de la première section d'injection (42) par la première partie d'aiguille de buse (31) pour une commande dépendant de la pression de la seconde partie d'aiguille de buse (32), la seconde section d'injection (43) est libérée en complément de la première section d'injection (42).
  11. Installation d'injection de carburant selon la revendication 9,
    caractérisée en ce que
    la première et la seconde section d'injection (42, 43) sont des cercles à trous concentriques à l'extrémité côté chambre de combustion d'un corps de buse (44) de l'injecteur de carburant (1).
  12. Installation d'injection de carburant selon la revendication 1,
    caractérisée en ce que
    la première partie (31) de l'aiguille de buse et la seconde partie (32) de l'aiguille de buse ont à leur périphérie chaque fois des cavités d'évacuation du carburant de fuite (46, 48).
  13. Installation d'injection de carburant selon la revendication 12,
    caractérisée en ce que
    les cavités (46, 48) d'évacuation du carburant de fuite sont reliées par l'intermédiaire d'un canal de fuite (47) prévu dans les parties d'aiguille de buse (31, 32) et débouchent dans une conduite de carburant de fuite (49) située du côté du boîtier.
  14. Installation d'injection de carburant selon la revendication 1,
    caractérisée en ce que
    l'amplificateur de pression (5) comporte la chambre de pression (11) sollicitée par une conduite (4) par la source de carburant à haute pression (2, 81), ainsi que la chambre de retour (16) reliée par l'intermédiaire d'une électrovanne (8) aux conduites (18, 19) et à la source de carburant à haute pression (2, 81), ainsi que la chambre haute pression (20) appliquant une haute pression à la chambre de buse (29) entourant coaxialement l'aiguille de buse (30).
  15. Installation d'injection de carburant selon la revendication 14,
    caractérisée en ce que
    la chambre de retour (16) de l'amplificateur de pression (5) est reliée à la chambre de fermeture (21) de la soupape d'injection (6).
  16. Installation d'injection de carburant selon la revendication 14,
    caractérisée en ce que
    la chambre de fermeture (21) de la soupape d'injection (6) est sollicitée directement à partir de la source de carburant à haute pression (2, 81) par une conduite (4, 60).
  17. Installation d'injection de carburant selon la revendication 14,
    caractérisée en ce que
    la chambre de fermeture (21) de la soupape d'injection (6) est sollicitée en pression, parallèlement à une conduite (22) à partir de la chambre de retour (16), ou parallèlement à une conduite (60) à partir de la source de pression de carburant (2, 81) par une conduite (25) comportant un clapet anti-retour/point d'étranglement (24) de la conduite (25) alimentée à partir de la chambre à haute pression (20).
  18. Installation d'injection de carburant selon les revendications 1 et 15 à 17,
    caractérisée en ce que
    lorsqu'on neutralise la soupape (8), on établit une liaison électrique (4, 18, 19, 22, 60, 23, 85) entre la source de haute pression (2, 81) et la chambre de fermeture (21, 82).
  19. Installation d'injection de carburant selon la revendication 1 ainsi que les revendications 15 à 17,
    caractérisée en ce que
    lorsqu'on neutralise la soupape (8), on réalise une liaison de communication de liquide (4, 18, 19, 22 ; 60, 23, 85, 25, 28) entre la source de haute pression (2) et la chambre de buse (29).
  20. Installation d'injection de carburant selon la revendication 5,
    caractérisée en ce qu'
    au moins la première partie d'aiguille de buse (31) peut être sollicitée par la pression générée dans une chambre de pression de fermeture (21, 82).
  21. Installation d'injection de carburant selon la revendication 1,
    caractérisée en ce que
    la seconde partie (32) de l'aiguille de buse est actionnée indépendamment de la sollicitation en pression d'une seconde chambre de commande de buse (83).
  22. Installation d'injection de carburant selon la revendication 21,
    caractérisée en ce que
    la seconde chambre de commande de buse (83) est séparée de manière étanche de la chambre de commande de buse (82) par un corps (89) en forme de manchon.
  23. Installation d'injection de carburant selon la revendication 21,
    caractérisée en ce que
    la seconde partie (32) de l'aiguille de buse comporte un canal longitudinal (84) par lequel les fuites de guidage sont évacuées de façon commandée dans la seconde chambre de commande de buse (83) et dans une conduite de décharge (88).
  24. Installation d'injection de carburant selon la revendication 22,
    caractérisée en ce que
    les fuites de guidage entre la première et la seconde partie d'aiguille (31, 32) sont évacuées par l'intermédiaire du canal longitudinal (84) entre le corps (89) en forme de buse et la partie intérieure (31) en aiguille pour passer dans la chambre de commande de buse (83).
EP03722255A 2002-06-29 2003-04-03 Systeme a rampe commune comprenant une buse variable et un systeme multiplicateur de pression Expired - Lifetime EP1520096B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10229417 2002-06-29
DE10229417A DE10229417A1 (de) 2002-06-29 2002-06-29 Speichereinspritzsystem mit Variodüse und Druckübersetzungseinrichtung
PCT/DE2003/001099 WO2004003374A1 (fr) 2002-06-29 2003-04-03 Systeme a rampe commune comprenant une buse variable et un systeme multiplicateur de pression

Publications (2)

Publication Number Publication Date
EP1520096A1 EP1520096A1 (fr) 2005-04-06
EP1520096B1 true EP1520096B1 (fr) 2006-06-14

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EP03722255A Expired - Lifetime EP1520096B1 (fr) 2002-06-29 2003-04-03 Systeme a rampe commune comprenant une buse variable et un systeme multiplicateur de pression

Country Status (5)

Country Link
US (1) US20050172935A1 (fr)
EP (1) EP1520096B1 (fr)
JP (1) JP2005531713A (fr)
DE (2) DE10229417A1 (fr)
WO (1) WO2004003374A1 (fr)

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DE10337609A1 (de) * 2003-08-16 2005-03-10 Bosch Gmbh Robert Kraftstoff-Einspritzvorrichtung, insbesondere für eine Brennkraftmaschine mit Direkteinspritzung
DE10342567A1 (de) * 2003-09-15 2005-04-14 Robert Bosch Gmbh Vorrichtung zum Einspritzen von Kraftstoff
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EP2602476A1 (fr) * 2011-12-07 2013-06-12 Continental Automotive GmbH Moyen d'ensemble formant soupape pour soupape d'injection et soupape d'injection
CN102678409B (zh) * 2012-05-21 2014-03-26 哈尔滨工程大学 相继增压式电控共轨喷油***
EP2674608B1 (fr) * 2012-06-13 2015-08-12 Delphi International Operations Luxembourg S.à r.l. Injecteur à carburant
JP6826371B2 (ja) * 2016-03-24 2021-02-03 三菱重工業株式会社 液圧駆動ピストン装置及びクロスヘッド式内燃機関
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Also Published As

Publication number Publication date
US20050172935A1 (en) 2005-08-11
DE10229417A1 (de) 2004-01-15
WO2004003374A1 (fr) 2004-01-08
JP2005531713A (ja) 2005-10-20
DE50303852D1 (de) 2006-07-27
EP1520096A1 (fr) 2005-04-06

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