EP1574703B1 - Système d'injection de combustible pour un moteur à combustion interne - Google Patents

Système d'injection de combustible pour un moteur à combustion interne Download PDF

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Publication number
EP1574703B1
EP1574703B1 EP20050100178 EP05100178A EP1574703B1 EP 1574703 B1 EP1574703 B1 EP 1574703B1 EP 20050100178 EP20050100178 EP 20050100178 EP 05100178 A EP05100178 A EP 05100178A EP 1574703 B1 EP1574703 B1 EP 1574703B1
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EP
European Patent Office
Prior art keywords
pump
injection
pressure
valve
control
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 - Fee Related
Application number
EP20050100178
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German (de)
English (en)
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EP1574703A1 (fr
Inventor
Peter Boehland
Francois Rossignol
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP1574703A1 publication Critical patent/EP1574703A1/fr
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Publication of EP1574703B1 publication Critical patent/EP1574703B1/fr
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M45/00Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02Fuel-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
    • F02M45/04Fuel-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
    • F02M45/08Injectors peculiar thereto
    • F02M45/086Having more than one injection-valve controlling discharge orifices
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02Fuel-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
    • F02M47/027Electrically actuated valves draining the chamber to release the closing pressure
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M57/00Fuel-injectors combined or associated with other devices
    • F02M57/02Injectors structurally combined with fuel-injection pumps
    • F02M57/022Injectors structurally combined with fuel-injection pumps characterised by the pump drive
    • F02M57/023Injectors structurally combined with fuel-injection pumps characterised by the pump drive mechanical
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1806Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
    • F02M61/182Discharge orifices being situated in different transversal planes with respect to valve member direction of movement
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/46Valves, e.g. injectors, with concentric valve bodies
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20Varying fuel delivery in quantity or timing
    • F02M59/36Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366Valves being actuated electrically

Definitions

  • the invention relates to a fuel injection device for an internal combustion engine according to the preamble of claim 1.
  • Such a fuel injection device is known from DE 101 62 384 A1.
  • This fuel injection device has a high-pressure fuel pump and a fuel injection valve connected thereto for each cylinder of the internal combustion engine.
  • the high-pressure fuel pump has a pump piston driven by the internal combustion engine in a lifting movement, which limits a pump working space, which is connected to a pressure chamber of the fuel injection valve.
  • An electrically operated control valve is provided by which a connection of the pump working space to a discharge area is controlled.
  • the fuel injection valve has two injection valve members, through which at least one injection opening is controlled in each case. In this case, a second injection valve member is slidably disposed within a hollow first injection valve member.
  • the two injection valve members are each acted upon by the pressure prevailing in the pressure chamber in the opening direction against a respective closing force in an opening direction.
  • only the first injection valve member can be opened and thus only the at least one first injection opening can be released, or both injection valve members can be opened and all injection openings can be released. This allows, depending on the operating conditions of the internal combustion engine, an adaptation of the injection cross-section, in order to ensure an optimal injection of the fuel and thus the lowest possible fuel consumption and the lowest possible pollutant emissions. In certain operating conditions of the internal combustion engine, it is necessary that only the first injection valve member opens, while the second injection valve member must remain in its closed position.
  • the second injection valve member is acted upon by the pressure prevailing in a control chamber in a closing direction, wherein an additional control valve, a connection of the control chamber is controlled with the pump working space and thus the pressure prevailing in the control chamber pressure can be adjusted.
  • this requires a lot of effort.
  • the fuel injection device according to the invention with the features of claim 1 has the advantage that it is simple in construction, since no additional control valve is required.
  • the required pressure is generated at low stroke of the pump piston by closing the control valve, this increased pressure is fed via the first connection in the control chamber and is stored by the first check valve in the control chamber.
  • the control room can be specifically relieved, wherein a leakage of fuel from the pump working space is prevented by the second check valve in the control chamber, so that no undesirable pressure increase occurs in the control chamber, through which the opening behavior of the second injection valve member would be influenced uncontrollably.
  • control chamber Since the control chamber is separated from the pump working chamber with a large stroke of the pump piston, no further pressure buildup takes place in the control chamber and the pressure buildup in the pump working chamber can be freely selected for the requirements of the fuel injection. If the second injection valve member should not be kept closed but should open, so the control valve is not closed with a small stroke of the pump piston, so that no pressure build-up in the pump working chamber and in the control area.
  • the embodiment according to claim 2 ensures that during the delivery stroke of the pump piston, the second connection is first closed and fuel can be stored under pressure in the control room via the first connection still open.
  • the embodiment according to claim 3 ensures that the pump piston is pressed to the side of the cylinder bore, on which the first connection opens, so that the leakage of fuel via the first connection from the pump working space can be kept low.
  • the embodiment according to claim 4 ensures that as a result of leakage between the pump piston and the cylinder bore from the pump working chamber via the first connection flowing fuel does not lead to an influence of the pressure in the control chamber and thus the opening behavior of the second injection valve member.
  • FIG. 1 shows a fuel injection device for an internal combustion engine in a schematic representation in a longitudinal section
  • Figure 2 shows an enlarged view of a designated II in Figure 1 section of the fuel injector
  • Figure 3 shows a detail of the fuel injection device in an enlarged view in a section along line III-III in Figure 1
  • Figure 4 shows a detail of Figure 3 with a modified embodiment of a check valve.
  • FIGS. 1 to 4 show a fuel injection device for an internal combustion engine of a motor vehicle.
  • the internal combustion engine is preferably a self-igniting internal combustion engine.
  • the fuel injection device is designed as a so-called pump-nozzle system or as a pump-line-nozzle system and has for each cylinder of the internal combustion engine in each case a high-pressure fuel pump 10 and connected thereto fuel injection valve 12.
  • the high-pressure fuel pump 10 is disposed away from the fuel injection valve 12 and connected thereto via a line.
  • the fuel injector is formed as a pump-nozzle system, wherein the high-pressure fuel pump 10 and the fuel injection valve 12 are directly connected to each other and form a structural unit.
  • the high-pressure fuel pump 10 has a in one Cylinder bore 16 in a pump body 14 tightly guided pump piston 18 which is driven by a cam 20 of a camshaft of the internal combustion engine against the force of a return spring 19 in a lifting movement.
  • the pump piston 18 defines in the cylinder 16 a pump working chamber 22 in which the delivery stroke of the pump piston 18 compresses fuel under high pressure.
  • the pump working chamber 22 is supplied with fuel from a fuel tank 24 of the motor vehicle during the suction stroke of the pump piston 18 by a feed pump 21.
  • the fuel injection valve 12 has a valve body 26, which may be designed in several parts, in which a first injection valve member 28 is guided longitudinally displaceably in a bore 30.
  • the valve body 26 at its end facing the combustion chamber of the cylinder of the internal combustion engine end portion at least a first, preferably a plurality of first injection openings 32 which are distributed over the circumference of the valve body 26.
  • the first injection valve member 28 has, at its end region facing the combustion chamber, an approximately conical sealing surface 34, for example, which cooperates with a valve seat 36 formed in the valve body 26 in its end region facing the combustion chamber, from or after which the first injection openings 32 are discharged.
  • annular space 38 is present between the injection valve member 28 and the bore 30 toward the valve seat 36, which merges in its end region remote from the valve seat 36 by a radial widening of the bore 30 into a pressure chamber 40 surrounding the first injection valve member 28.
  • the first injection valve member 28 has at the level of the pressure chamber 40 by a cross-sectional reduction on a pressure shoulder 42.
  • a first biased closing spring 44 At the end of the combustion chamber facing away from the first injection valve member 28 engages a first biased closing spring 44, through which the first injection valve member 28 is pressed to the valve seat 36 back.
  • the first closing spring 44 is arranged in a first spring chamber 46 of the valve body 26, which adjoins the bore 30.
  • the first injection valve member 28 of the fuel injection valve 12 is hollow and in this a second injection valve member 128 is slidably guided in a bore formed coaxially in the injection valve member 28.
  • a second injection valve member 128 is slidably guided in a bore formed coaxially in the injection valve member 28.
  • the second injection valve member 128, at least one second injection port 132 in the valve body 26 is controlled.
  • the at least one second injection opening 132 is arranged offset in the direction of the longitudinal axis of the injection valve members 28, 128 to the at least one first injection opening 32 towards the combustion chamber.
  • the second injection valve member 128 has, at its end region facing the combustion chamber, an approximately conical sealing surface 134, for example, which cooperates with a valve seat 136 formed in the valve body 26 in its end region facing the combustion chamber, from or after which the second injection openings 132 are discharged.
  • the second injection valve member 128 may be formed in two parts and having a sealing surface 134, the combustion chamber facing part and a combustion chamber adjacent to the first part second part. Near the combustion chamber end of the second injection valve member 128, a pressure surface 142 is formed on this, acts on the pressure prevailing in the pressure chamber 40 when the first injection valve member 28 is open.
  • a second spring chamber 54 is formed on the first spring chamber 46 away from the combustion chamber, as shown in FIG second injection valve member 128 acting closing spring 144 is arranged.
  • the first injection valve member 28 is supported on the first closing spring 44 via a spring plate 45 projecting into the first spring chamber 46.
  • the second injection valve member 128 or a pressure rod 47 supported thereon passes through the first spring chamber 46 and protrudes into the second spring chamber 54 and is supported by a spring plate 145 on the second closing spring 144.
  • the second closing spring 144 is supported, with its end facing away from the second valve member 128, at least indirectly at the bottom of the second spring chamber 54.
  • an electrically operated control valve 23 a compound of the pump working chamber 22 is controlled with a discharge space, as for example, at least indirectly, the fuel tank 24 or the feed from the feed pump 21 can serve forth, in which by the feed pump 21, a relation to the fuel tank 24 slightly increased pressure is generated.
  • the control valve 23 is actuated by an electronic control device 25, wherein the pressure buildup in the pump working chamber 22 and thus the timing of the fuel injection and the injected fuel quantity is controlled by the control valve 23.
  • the control valve 23 may comprise an electromagnetic actuator or a piezoelectric actuator.
  • the control valve 23 is formed for example as a 2/2-way valve and switchable between an open and a closed switching position.
  • FIG 3 a section III of the fuel injection device is shown enlarged.
  • the second injection valve member 128 or the pressure rod 47 supported thereon projects into the second spring chamber 54 into it.
  • the second spring chamber 54 can be connected to the pump working chamber 22 via a line 56 which represents a first connection.
  • the second spring chamber 54 forms a control chamber, wherein the push rod 47 and the spring plate 145 form a control piston, by the pressure prevailing in the spring chamber 54 a force in the closing direction to the second injection valve member 128 is generated.
  • the line 56 runs, starting from the control chamber 54, first in a between the valve body 26 and the pump body 14 arranged washer 27 and then through the pump body 14, where the end portion of the line 56 opens approximately radially on the circumference of the cylinder bore 16.
  • the line 56 is formed by bores in the intermediate plate 27 and the pump body 14.
  • the intermediate plate 27 is on the control chamber 54 side facing a spring chamber 54 towards open recess 58 is formed, into which the line 56 opens.
  • the recess 58 in this case has a slightly smaller cross section than the control chamber 54, so that the intermediate plate 27 has a recess 58 surrounding the control chamber 54 defining annular shoulder 60.
  • a spring plate 62 is arranged, on which the second closing spring 144 is supported towards the intermediate plate 27.
  • the spring plate 62 is slidably disposed in the control chamber 54 and between the circumference and the control chamber 54 forming bore a flow cross-section is present, the spring plate 62 may be arranged to form the flow cross-section with radial clearance in the control chamber 54 or the spring plate 62 in its periphery a or preferably may have a plurality of recesses.
  • the second closing spring 144 also forms the Closing spring of the check valve 64.
  • the check valve 64 When the spring plate 62 rests against the annular shoulder 60, the check valve 64 is closed, so that the control chamber 54 is separated from the line 56. When the spring plate 62 is lifted off the annular shoulder 60, the check valve 64 is opened, so that the control chamber 54 is connected to the line 56 via the flow cross-section released between the spring plate 62 and the control chamber 54. The check valve 64 opens to the control chamber 54, so that this allows for a corresponding pressure difference, a flow of fuel from the line 56 into the control chamber 54, but prevents outflow of fuel from the control chamber 54 into the conduit 56.
  • the control chamber 54 is also connectable via a second connection line 66 with the pump working chamber 22.
  • the line 56 extends from the circumference of the control chamber 54 first in the valve body 26, then in between the valve body 26 and the pump body 14 arranged washer 27 and then through the pump body 14, where the end portion of the conduit 66 at the periphery of the cylinder bore 16 opens approximately radially ,
  • the conduit 66 is formed by bores in the valve body 26, in the intermediate disk 27 and in the pump body 14.
  • a second check valve 68 is arranged, which opens to the pump working chamber 22 through.
  • the second check valve 68 is arranged for example in the intermediate plate 27 and has a valve member 70 which cooperates with a valve seat 72.
  • the valve seat 72 may in this case be formed on the valve body 26, for example in the form of a flat annular shoulder surrounding the conduit 66 in the valve body 26.
  • the valve member 70 may be formed plate-shaped as shown in Figure 3 and is pressed by a closing spring 74 to the valve seat 72 out.
  • the Closing spring 74 is clamped between the valve member 70 and the pump body 14.
  • the valve member 70 may be formed spherical as shown in Figure 4, wherein any other forms of the valve member 70 are possible.
  • the pump piston 18 is located at the beginning of its delivery stroke in its outer dead center, in which this has the lowest immersion depth in the cylinder bore 16. When it is caused by the cam 20 delivery stroke, the pump piston 18 moves into the cylinder bore 16, to its inner dead center. If the pump piston 18 is arranged in its outer dead center or has executed only a small stroke, starting from its outer dead center, the mouths of the lines 56 and 66 are released in the cylinder bore 16, so that the control chamber 54 is connected to the pump working chamber 22.
  • the pump piston 18 If the pump piston 18 has carried out a large stroke from its outer dead center, it initially covers the mouth of the conduit 66 in the cylinder bore 16, so that the control chamber 54 is then connected only via the first line 56 to the pump working chamber 22 and fuel from the pump working chamber 22 can flow into the control chamber 54, but no fuel can flow out of the control chamber 54 via the second line 66 into the pump working chamber 22. Upon further delivery stroke of the pump piston 18, the mouth of the first line 56 is closed by the latter in the cylinder bore 16, so that the control chamber 54 is completely separated from the pump working chamber 22.
  • the mouths of the two lines 56,66 in the cylinder bore 16 can in the direction of the longitudinal axis 17 of the cylinder bore 16 may be arranged offset from one another to achieve that the mouth of the second line 66 and only at a larger stroke, the mouth of the first line 56 is closed by the pump piston 18 at its delivery stroke first.
  • the lines 56,66 at least in the region of their mouths in the cylinder bore 16 have different diameters, wherein the second conduit 66 has a small diameter and thus first closed by the pump piston 18 in the delivery stroke, while the first line 56 has a large diameter has and is closed only at a larger stroke of the pump piston 18.
  • the mouths of the two lines 56,66 can be arranged coaxially and thus easily manufactured in the same manufacturing facility with drilling tools with different diameters.
  • the mouths of the two lines 56 and 66 in the cylinder bore 16 are preferably arranged in opposite circumferential regions of the cylinder bore 16, as shown in Figure 3.
  • first line 56 leads between the first check valve 64 and the pump working chamber 22 from a discharge line 76 into a low pressure region.
  • a throttle point 77 is preferably arranged to limit the flow.
  • the relief line 76 may, for example, as shown in Figure 3 in the washer 27 from the line 56 dissipate.
  • the control valve 23 In operating conditions of the internal combustion engine in which the second injection valve member 128 is not intended to open, but only the first injection valve member 28 to open, the control valve 23 by the control device 25 during the outgoing from its outer dead center stroke of the pump piston 18 at a certain time closed, so that in the pump working chamber 22, a pressure buildup occurs.
  • the time of closing the control valve 23 the pressure build-up in the pump working space can be influenced. The earlier the control valve 23 is closed, the higher the pressure generated in the pump working chamber 22. As long as the mouth of the first line 56 is released into the cylinder bore 16 by the pump piston 18 at its low stroke pressure is fed into the line 56 and the control chamber 54.
  • the mouth of the second line 66 is first closed by the pump piston 18 into the cylinder bore 16, so that no more fuel can flow back into the pump working chamber 22 from the control chamber 54.
  • the mouth of the first line 56 is closed by this and the mouth of the first bore 56, wherein in the control chamber 54 by the first check valve 64 fuel is stored under pressure.
  • the control valve 23 can be opened again by the control device 25, so that the pressure in the pump working chamber 22 drops again or does not rise any further.
  • the second injection valve member 128 By the pressure stored in the control chamber 54, the second injection valve member 128 is acted upon by the push rod 47 and the spring plate 145 in addition to the force of the second closing spring 144 in the closing direction, so that it does not open.
  • the fuel injection taking place only by opening the first injection valve member 28 is subsequently controlled by the control valve 23 which is closed at a certain time.
  • the pressure in the pump working chamber 22 and thus in the pressure chamber 40 of the fuel injection valve 12 is so high that the pressure generated by this on the pressure shoulder 42 on the first injection valve member 28 is greater than the force of the first closing spring 44, so opens Fuel injection valve 12 by the first injection valve member 28 lifts off with its sealing surface 34 from the valve seat 36 and the at least one first injection port 32 releases.
  • Leakage in the second line 66 may also not lead to an increase in pressure in the spring chamber 54 because of the spring chamber 54 towards closing second check valve 68.
  • the pressure prevailing in the spring chamber 54 pressure is not affected by leakage from the pump working chamber 22.
  • leakage builds up due to the closed check valve 68, an increased pressure by which the pump piston 18 is pressed to the opposite peripheral region of the cylinder bore 16, in which the mouth of the first conduit 56 is arranged, whereby the leakage from the pump working space 22 is reduced in the first line 56.
  • the control valve 23 In operating conditions of the internal combustion engine in which the second injection valve member 128 is to open, the control valve 23 is not closed by the control device 25 at the beginning of the stroke of the pump piston 18 from its outer dead center, so that in Pump working space 22 no pressure build-up takes place until the mouth of the line 56 is closed by the pump piston 18.
  • the control chamber 54 In the control chamber 54, no elevated pressure is present, so that the second injection valve member 128 is acted upon at least substantially only by the second closing spring 144 in the closing direction.
  • no increase in the pressure in the spring chamber 54 occurs even in the case of leakage from the pump working chamber 22, so that the opening behavior of the second injection valve member 128 is not influenced uncontrollably.
  • the pressure buildup and thus the timing of the fuel injection is determined by the closing of the control valve 23 by the controller 25. If the pressure in the pump working chamber 22 and thus in the pressure chamber 40 is so high that the force acting in the opening direction on the pressure shoulder 42 on the first injection valve member 28 is greater than the force generated in the closing direction by the first closing spring 44, the first injection valve member 28 opens and fuel is injected through the at least one first injection port 32. After the first injection valve member 28 and the second injection valve member 128 opens when the pressure prevailing in the pressure chamber 40 is so high that this on the pressure surface 142 to the second injection valve member 128 generates a higher force in the opening direction than that on the second injection valve member 128 by the closing spring 144 generated closing force, and releases the second injection openings 132. Thus, the entire injection cross section is released at the fuel injection valve 12 and it can be injected a larger amount of fuel.
  • a fuel injection cycle is terminated by the control valve 23 being opened by the control device 25, so that the pump working space 22 is relieved.
  • the pump piston 18 moves out of the Cylinder bore 16 out, the mouths of the two lines 56,66 are opened in the cylinder bore 16 through the pump piston 18.
  • the control chamber 54 is connected via the second line 66 and the second check valve 68 with the pump working chamber 22 and thus relieved, so that in the control chamber 54, no increased pressure prevails.
  • the injection cross sections formed by the first injection openings 32 and the second injection openings 132 are at least approximately equal, so that when opening only the first injection valve member 28 of half the entire injection cross section is released.
  • the first injection openings 32 form a larger or smaller injection cross section than the second injection openings 132.

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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)

Claims (4)

  1. Dispositif d'injection de carburant pour un moteur à combustion interne comportant une pompe à carburant haute pression (10) et un injecteur de carburant (12) relié à celle-ci pour chaque cylindre du moteur à combustion interne, la pompe à carburant haute pression (10) dont le piston (18), entraîné dans un mouvement de levée par le moteur à combustion limite, dans un alésage du cylindre (16), une chambre de travail (22) de la pompe, reliée à une chambre de pression (40) de l'injecteur de carburant (12), comportant une soupape de commande (23) électrique qui commande une liaison entre la chambre de travail (22) et une zone de décharge, l'injecteur de carburant (12) présentant deux éléments d'injecteur (28, 128) permettant la commande respective d'au moins un orifice d'injection (32, 132), le deuxième élément d'injecteur (128) étant mobile à l'intérieur du premier élément d'injecteur (28), les deux éléments d'injecteur (28, 128), alimentés par la pression régnant dans la chambre de pression (40), pouvant être déplacés respectivement contre une force de fermeture dans la direction d'ouverture afin de libérer au moins un orifice d'injection (32, 132), le deuxième élément d'injecteur (128) pouvant être immobilisé dans une position de fermeture en fonction de la pression régnant dans une chambre de commande (54) pouvant être reliée à la chambre de travail (22),
    caractérisé en ce que
    la chambre de commande (54) a une première liaison (56), commandée par le piston de pompe (18), avec la chambre de travail (22) munie d'un premier clapet antiretour (64) s'ouvrant en direction de la chambre de commande (54),
    et une deuxième liaison (66), commandée par le piston (18), avec la chambre de travail (22) munie d'un deuxième clapet antiretour (68) s'ouvrant en direction de la chambre de travail (22),
    les deux liaisons (56, 66) s'ouvrent grâce au piston de pompe (18) à partir de son point mort où il se trouve au début de sa course de refoulement, en cas de course faible du piston de pompe (18), et se ferment en cas de course importante du piston de pompe (23), et
    la soupape de commande (23) peut se fermer, du moins temporairement, lors de la course faible du piston (18), afin d'introduire, dans la chambre de commande (54) une pression accrue et de maintenir le deuxième élément d'injecteur (128) dans sa position de fermeture.
  2. Dispositif d'injection de carburant selon la revendication 1,
    caractérisé en ce que
    la deuxième liaison (66) de la chambre de commande (54) avec la chambre de travail (22) se ferme déjà en cas de course du piston (18) plus faible que la première liaison (56) à partir de son point mort, où se trouve le piston au début de sa course de refoulement.
  3. Dispositif d'injection de carburant selon la revendication 1 ou 2,
    caractérisé en ce que
    les embouchures des deux liaisons (56, 66) de la chambre de commande (54) avec la chambre de travail (22) sont disposées sur des zones périphériques se faisant face de l'alésage du cylindre (16).
  4. Dispositif d'injection de carburant selon l'une des revendications 1 à 3,
    caractérisé en ce que
    une liaison de décharge (76) part de la première liaison (56) de la chambre de commande (54) avec la chambre de travail (22) entre le premier clapet antiretour (64) et la chambre de travail (22), vers une zone de basse pression dans laquelle est disposé, de préférence, un point d'étranglement (77).
EP20050100178 2004-03-09 2005-01-13 Système d'injection de combustible pour un moteur à combustion interne Expired - Fee Related EP1574703B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004011283 2004-03-09
DE200410011283 DE102004011283A1 (de) 2004-03-09 2004-03-09 Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine

Publications (2)

Publication Number Publication Date
EP1574703A1 EP1574703A1 (fr) 2005-09-14
EP1574703B1 true EP1574703B1 (fr) 2006-11-15

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EP20050100178 Expired - Fee Related EP1574703B1 (fr) 2004-03-09 2005-01-13 Système d'injection de combustible pour un moteur à combustion interne

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DE (2) DE102004011283A1 (fr)

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DE10162384A1 (de) * 2001-12-19 2003-07-03 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine
DE10233099A1 (de) * 2002-07-20 2004-02-05 Robert Bosch Gmbh Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine
DE10237585A1 (de) * 2002-08-16 2004-02-26 Robert Bosch Gmbh Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine

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EP1574703A1 (fr) 2005-09-14
DE502005000179D1 (de) 2006-12-28

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