EP1344929B1 - Injecteur de combustible pour moteurs à combustion interne - Google Patents

Injecteur de combustible pour moteurs à combustion interne Download PDF

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Publication number
EP1344929B1
EP1344929B1 EP03003081A EP03003081A EP1344929B1 EP 1344929 B1 EP1344929 B1 EP 1344929B1 EP 03003081 A EP03003081 A EP 03003081A EP 03003081 A EP03003081 A EP 03003081A EP 1344929 B1 EP1344929 B1 EP 1344929B1
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EP
European Patent Office
Prior art keywords
valve
external
control
space
needle
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
EP03003081A
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German (de)
English (en)
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EP1344929A1 (fr
Inventor
Friedrich Boecking
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Filing date
Publication date
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Publication of EP1344929A1 publication Critical patent/EP1344929A1/fr
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Publication of EP1344929B1 publication Critical patent/EP1344929B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—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
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • 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

  • the invention relates to a fuel injection valve for Internal combustion engines from, as is the genus of the claim 1 corresponds and for example from the published patent application DE 41 15 477 A1 is known.
  • the one shown there Fuel injection valve has a housing in which a Bore is formed. At the end of the bore on the combustion chamber side is formed a valve seat in which two rows of Injection openings are formed, each in one Radial plane to the longitudinal axis of the bore are arranged. In the bore is an outer valve needle and one in it guided inner valve needle arranged, both valve needles are longitudinally displaceable.
  • the outer valve needle points a valve sealing surface on its combustion chamber end, with which they use the valve seat to control the outer Injection opening row cooperates in that at Valve seat lifted valve sealing surface fuel from a between the outer valve needle and the wall of the bore formed pressure space between the valve sealing surface and the valve seat through the first row of injection openings accrues.
  • the valve sealing surface of the outer valve needle lies on the other hand at the valve seat, this is the fuel flow interrupted:, the outer row of injection openings is closed.
  • the movement of the outer valve needle is hereby by a force ratio of an opening and a Closing force controlled, the opening force by the Pressurizing a pressure shoulder on the outer valve needle is applied by the fuel pressure in the pressure chamber is acted upon.
  • This hydraulic opening force opposing closing force is provided by a separate Device generated, for example a spring. about the control of the pressure in the pressure chamber or through The force ratio can be changed by changing the closing force change between the opening force and the closing force and thereby a movement of the outer valve needle in the longitudinal direction produce.
  • the inner valve needle also points a pressure shoulder on that from the fuel pressure in the pressure chamber however, fuel pressure is only applied when the outer valve needle has lifted off the valve seat.
  • a closing force acts on the inner valve needle, and as soon as the hydraulic opening force on the inner valve needle exceeds the closing force, the inner valve needle moves away from the valve seat and gives the inner row of injectors free.
  • the interaction between the at the inner valve needle trained valve sealing surface and The valve seat is analogous to the outer valve needle.
  • the closing force on the inner valve needle is determined by the hydraulic pressure generated in a control room that in the housing of the fuel injection valve is formed.
  • the Pressure in the control room acts either directly or indirectly via connecting elements on the inner valve needle, see above that the closing force is set via the pressure in the control room can be.
  • the known fuel injection valve has in particular the disadvantage that the closing force on the outside Valve needle is generated by a spring.
  • the closing movement the outer valve needle takes place relatively slowly, since the balance of forces is the opening force of the hydraulic force and constant closing force through the Spring changes only by lowering the opening force.
  • short-term injections in particular with a small amount of fuel not or not with the necessary Realize precision. But this is critical, though Fuel injectors for quiet engine running, one low fuel consumption and low pollutant emissions should be optimized.
  • the fuel injector according to the invention with the characteristic Features of claim 1, however, points the advantage that the closing force on the outside Valve needle also hydraulic by pressure in one Control room is generated and that to end the injection Fuel under high pressure in both control rooms is initiated so that the closing force on the valve needles rises very quickly and therefore quick needle closing is made possible.
  • This allows very short-term Injections with very small injection quantities with high ones Realize precision and thereby in particular injections, which is divided into a pre, a main and a post injection divided.
  • a control valve is arranged in the housing, the one Control room and a control valve member movably arranged therein having.
  • the valve control room is via an outlet throttle with the outer control room and over another Flow restrictor connected to the inner control room.
  • the valve control chamber also has an inlet throttle, which the valve control room with the high pressure fuel chamber connects and a valve drain channel that connects to the control room connects with a leak oil chamber.
  • valve member closes the valve outlet throttle in one end position and leaves all other connections of the valve control room open. hereby can fuel in the valve inlet throttle Flow valve control chamber of the control valve and from there the two flow restrictors in the inner and outer Control room, so that there is quickly a high fuel pressure builds up and thus a high closing force the inner or outer valve needle results.
  • the subject of Invention closes the valve member in the second end position the outlet throttle of the inner control chamber while the valve drain channel of the valve control room is opened.
  • the pressure drops through the open valve drain channel in the valve control room and thus also in the outer control room. Because the inner drain throttle that the valve control room with connects the inner control room, closed by the valve member the pressure in the inner control room is maintained, so the inner valve needle is not off the valve seat takes off. In this way it can be achieved that only the outer Valve needle opens while the inner valve needle is in its The closed position remains.
  • valve member in the second end position the valve inlet throttle of the valve control chamber, while the valve outlet throttle of the valve control room is opened.
  • This will both control rooms, both the inner control room, the inner one Valve needle, as well as the outer control chamber, which creates the closing force on the outer valve needle relieved at the same time so that both valve needles open at the same time.
  • valve member moves when moving in the valve control chamber Longitudinal movement and arrives in one end position a first valve seat and in the second end position a second valve seat opposite the first valve seat to the system so that both valve seats face each other.
  • first valve seat is conical
  • second Valve seat is designed as a flat seat.
  • a spherical valve sealing surface on the valve member is formed with the conical valve seat cooperates while the valve sealing surface that with the flat seat interacts, is just trained. Thereby a good seal can be achieved on both valve seats.
  • this is Valve member connected to an actuator which is the valve member moved in the valve control room.
  • the actuator preferably designed as an electrical actuator, the electrical actuator being particularly advantageous to train as a piezo actuator. This makes it possible Valve element very quickly and with very low power in the Move the valve control room and it is also possible to move along the two end positions of the valve member any intermediate positions of the valve member between these two end positions to approach.
  • FIG 1 is a longitudinal section through an inventive Fuel injector with its essential components shown.
  • the fuel injection valve has a housing 1, which has a valve holding body 3 and a valve body 5 comprises, the valve body 5 by means of a Clamping nut 2 is clamped against the valve holding body 3.
  • a bore 9 is formed, on the Combustion chamber end formed a conical valve seat 21 is.
  • Figure 2 shows an enlargement of the designated II Detail in the area of the valve seat 23.
  • the outer row of injection ports 120 further from Combustion chamber is located remotely as the inner row of injectors 220.
  • Both rows of injection openings 120, 220 consist of several, preferably evenly over the Scope of the fuel injector is distributed Injection ports.
  • an outer valve needle 10 arranged in a section facing away from the combustion chamber is sealingly guided in the bore 9.
  • the outer Valve needle 10 is designed as a hollow needle and has a conical outer end at the combustion chamber Valve sealing surface 24.
  • the outer valve sealing surface 24 has an opening angle that is greater than the opening angle of the conical valve seat 23. This is the outer edge of the outer valve sealing surface 24 as the outer Sealing edge 25 formed in the closed position of the outer Valve needle 10 comes to rest on valve seat 23.
  • the outer valve needle 10 tapers, starting from it guided section, forming a pressure shoulder 16 the valve seat 23. This will between the wall Bore 9 and the outer valve needle 10 a pressure chamber 14 formed over one in the valve body 5 and in the valve holding body 3 running high pressure channel 7 with fuel under high pressure can be filled.
  • the high pressure channel 7 opens thereby in a radial expansion of the pressure chamber 14 which Height of the pressure shoulder 16 of the outer valve needle 10 is formed is.
  • An inner valve needle 12 is located in the outer valve needle 10 arranged longitudinally displaceable on its combustion chamber side End a conical inner valve sealing surface 26 and one also has conical end surface 33, at the transition the inner valve sealing surface 26 to the end surface 33 an inner Sealing edge 27 is formed. In the closed position of the inner Valve needle 12 on valve seat 23 comes this inner Sealing edge 27 on the valve seat 23 to the system, so that a Fuel flow to the inner row of injection openings 220 is prevented becomes.
  • a central bore 18 is formed in the valve holding body 3, in which a guide piston 40 is arranged to be longitudinally displaceable is.
  • the guide piston 40 is located on the side facing away from the combustion chamber End of the outer valve needle 10 and moves thus in synchronism with the outer valve needle 10 in Longitudinal direction.
  • Between the end face 50 of the guide piston 40 and the end of the central one designed as a blind bore Bore 18 has an outer control chamber 55, by its pressure a hydraulic force on the face 50 of the guide piston 40 is exercised and thus also on the outer valve needle 10.
  • a closing spring 57 is arranged under pressure, which the guide piston 40 and thus the outer valve needle 10 always subjected to a closing force, the force the closing spring 57 only serves the outer valve needle 10 with the internal combustion engine switched off in their Hold closed position.
  • the outer control room 55 is over an inlet throttle 62 with the inlet channel 7 High pressure chamber connected and via an external outlet throttle 60 with a valve control chamber 77, which is further below is described.
  • the guide piston 40 has a piston bore 21, in which a pressure piston 20 is arranged to be longitudinally displaceable.
  • the Pressure piston 20 lies on inner valve needle 12 on and moves synchronously with it in the longitudinal direction.
  • an inner control chamber 42 formed by the pressure of a hydraulic Force on the end face 22 of the pressure piston 20 and thus is also exerted on the inner valve needle 12.
  • the inner one Control chamber 42 is formed in a guide piston 40 Cross bore 44 with an inner channel Outlet throttle 46 connected and via an inner inlet throttle 48 with the high pressure duct 7.
  • the mode of operation of the two valve needles and the associated one Control rooms is as follows: At the beginning of the injection cycle prevails both in the inner control room 42 and in the outer Control room 55 a high fuel pressure. Because the face 50 of the guide piston 40 is significantly larger than the pressure shoulder 16 of the outer valve needle 10, the predominates Closing force on the outer valve needle 10, and the outer Valve sealing surface 24 is pressed against the valve seat 23. Similar conditions result for the inner valve needle 12, since the end face 22 of the pressure piston 20 from the pressure is acted upon in the control room 42 and no corresponding one Counteracts opening force on the inner valve needle 12. If an injection is to take place, the pressure in the outside Control room 55 lowered, which also means the hydraulic Force on the end face 50 of the guide piston 40 is reduced.
  • the pressure control in the outside is schematic Control room 55 and shown in the inner control room 42, the with the help of a control valve 74.
  • the control valve 74 is integrated in the housing 1 of the fuel injection valve and has a valve control space 77 in which a Valve member 75 is slidably disposed.
  • the outer outlet throttle 65 connects the outer control room 55 and the inner outlet throttle 67, the inner control chamber 42 with the Valve control room 77. It opens into valve control room 77
  • a valve inlet throttle 68, the valve control room 77 always connects to a high-pressure fuel chamber, for example with the high pressure duct 7.
  • valve control room 77 also opens a valve drain channel 79, that connects the valve control chamber 77 to a leakage oil chamber, in which there is always a very low fuel pressure and which is not shown in the drawing.
  • a first valve seat 80 is formed which has a conical shape and on which the valve member 75 with a first valve sealing surface 84 cooperates.
  • the first Valve sealing surface 84 is spherical or hemispherical educated.
  • second valve sealing surface 86 is formed, which is flat and cooperates with a second valve seat 82, which is formed in the valve control chamber 77 and the Shape of a flat seat.
  • the valve member 75 is through a valve spring 88 in arranged in the valve control chamber 77 Directed the first valve seat 80 to at switched off internal combustion engine, the valve member in the first end position, i.e. in contact with the first valve seat 80 bring.
  • the valve member 75 is with an electrical actuator 70 connected, which is preferably designed as a piezo actuator is so that by an appropriately applied voltage a longitudinal movement of the valve member 75 in the valve control chamber 77 can be achieved.
  • the valve member 75 from the first end position, i.e. from the plant on the first Valve seat 80, in the second end position, that is the system at the second valve seat 82.
  • a piezo actuator it is also possible to valve member 75 in any intermediate position between the two end positions bring to.
  • valve 74 The operation of the control valve 74 is as follows: At the beginning of the injection, the valve member 75 is in the first End position, i.e. in contact with the first valve seat 80, and thus closes the valve drain channel 79 against the Valve control room 77. Through the connection via the valve inlet throttle 68 is the same in the valve control room 77 High pressure as in the high pressure room and therefore the same pressure as in the outer control room 55 and in the inner control room 42. Should an injection only through the outer row of injection openings 120 take place, the valve member 75 moves from the electrical actuator 70 from the first end position to the second end position, i.e. in attachment to the second Valve seat 82.
  • valve outlet channel 79 is opened and the inner drain restrictor 67 of the inner control space 42 closed.
  • valve outlet channel 79 and the valve inlet throttle 68 in connection with the dimensioning of the outer outlet throttle 65 a pressure drop is achieved in the valve control room 77, which is so strong that despite the external inlet throttle 62 also the pressure in the outer control chamber 55 drops.
  • This opens the in the manner described above outer valve needle 10 and gives the outer row of injection openings 120 free. This ends when the injection ends Valve member 75 again in the first end position, so that by the through the valve inlet throttle 68 and the outer Inlet throttle 62 fuel flowing in again the high pressure in the valve control room 77 and in the outer control room 55 builds.
  • valve member 75 is going out from the first end position on the first valve seat 80, into a Intermediate position moved between the two end positions.
  • the valve drain channel 79 is thereby opened and closed a suitable dimensioning of all inlet and outlet throttles a pressure drop is achieved in the valve control chamber 77 and thus, through the connection via the outer outlet throttle 65 and the inner outlet throttle 67 of the outer control chamber 55 or the inner control room 42, too in the outer control room 55 and 42 in the inner control room open both the inner valve needle 12 and the outer one Valve needle 10 in the manner described above.
  • valve drain channel 79 is closed and due to the fuel flowing in through the valve inlet throttle 68 rebuilds itself very quickly in the valve control room 77 the old high fuel pressure.
  • the fuel pressure in the outer control room 55 and in the inner control room 42 now both through the fuel flowing through the outer inlet throttle 62 or the inner inlet throttle 48 in the control rooms flow in as well as through the fuel, from the valve control chamber 77 via the outer flow restrictor 65 or the inner outlet throttle 67 the outer Control room 55 or the inner control room 42 inflows, rebuilt. This gives you a faster one Pressure build-up in the control rooms 42, 55 than this alone due to the fuel flowing in through the inlet throttles 62, 48 would be possible.
  • FIG. 4 is another embodiment of the Control valve for the fuel injection valve according to the invention shown.
  • the structure corresponds essentially to that Structure of the control valve 74 shown in FIG. 3 with the difference that the control valve member 75 compared to that in Figure 3 shown control valve is rotated by 180 °.
  • the electrical actuator 70 is now on the first Valve sealing surface 84 opposite side of the valve member 75 and is shown in FIG. 4 for the sake of clarity not shown. Because the operation of the control valve 74 in Figure 4 exactly the operation of that shown in Figure 3 Control valve 74 corresponds to a detailed Description to be omitted here.
  • FIG 5 is another embodiment of the control valve 74 shown.
  • the control of the outer control room 55 and the inner control chamber 42 via the flow restrictors 65, 67 and the inlet throttles 62, 48 is analogous to that in Figure 3 or control valve shown in Figure 4 74.
  • the control valve 74 also has a valve control chamber here 77, which has a first conical valve seat 80 and a second valve seat 82 designed as a flat seat having.
  • the valve inlet throttle opens into the valve control chamber 77 68 and the valve drain channel 79.
  • Both the outer Flow restrictor 65 and the inner flow restrictor 67 open into the valve control chamber 77, the inlet of which in the Valve control chamber 77 cannot be closed by valve member 75 is.
  • valve drain channel 79 In contact with the valve member 75 on the first valve seat 80, the valve drain channel 79 is closed, and in the opposite end position of the valve member 75 closes this by contacting the second valve seat 82 Valve inlet throttle 68.Should both valve needles 10, 12 are opened, the valve member 75 moves from the first Valve seat 80 in contact with the second valve seat 82 and thus closes the valve inlet throttle 68. By opening of the valve drain channel 79, the pressure in the valve control chamber drops 77 from and thus also in the outer control room 55 and in the inner control room 42. Thereupon both the inner open Valve needle 12 and the outer valve needle 10 and give both rows of injection openings 120, 220 free.
  • valve member 75 moves back into contact to the first valve seat 80, so that via the valve inlet throttle 68 fuel flows into the valve control chamber 77 and from the valve control chamber 77 via the valve flow restrictors 65, 67 into the control rooms 55, 42.
  • the rapid achieved thereby Pressure build-up in both control rooms 55, 42 causes quick needle closing.
  • an intermediate position possible. In this Fall can be done by appropriate dimensioning of the inlet throttles 62, 48 or the flow restrictors 65, 67 achieved that the two valve needles open successively.
  • valve member 75 moves into an intermediate position the first valve seat 80 and the second valve seat 82, the pressure in the control chamber 77 falls despite the valve inlet throttle 68 from. This also reduces the pressure on the outside Control room 55, so that the outer valve needle 10 opens.
  • By appropriately dimensioning the internal discharge throttle 67 is achieved that the pressure in the inner control room 42 only drops with a certain delay to such an extent that the inner valve needle 12 opens.
  • FIG. 6 shows a variant of the control valve shown in FIG. 5 74, with the first valve seat 80 here and second valve seat 82 are interchanged and so is the location of the control valve member 75.
  • the electric actuator 70 is located thus on the opposite side of the first valve sealing surface 84 Side of the valve member 75 and is the clarity not shown in Figure 6.

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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 (10)

  1. Injecteur de carburant comportant
    un boítier (1) et un alésage (9) formé à l'intérieur de celui-ci, l'alésage étant limité à son extrémité du côté de la chambre de combustion par un siège de soupape (23), une rangée d'ouvertures d'injection intérieure (220) et une rangée d'ouvertures d'injection extérieure (120) étant formées dans le siège de soupape (23),
    une aiguille de soupape externe (10) montée mobile longitudinalement dans l'alésage (9), présente à son extrémité du côté de la chambre de combustion une surface d'étanchéité de soupape extérieure (24) qui coopère avec le siège de soupape (23) pour commander la rangée d'ouverture d'injection extérieure (120), dans la mesure où, lorsque la surface d'étanchéité de soupape extérieure (24) est soulevée par le siège de soupape (23), la rangée d'ouverture d'injection extérieure (120) est reliée à une chambre de pression (14) formée entre la paroi de l'alésage (9) et l'aiguille externe (10), alors que lorsque la surface d'étanchéité de soupape extérieure (24) est posée sur le siège de soupape (23), la rangée d'ouverture d'injection extérieure (120) est bloquée ; et comportant
    une aiguille de soupape interne (12) guidée dans l'aiguille externe (10), et dont une surface d'étanchéité de soupape intérieure (26) coopère de la même manière que l'aiguille externe (10) avec le siège de soupape (23) pour commander la rangée d'ouverture d'injection intérieure (220), l'aiguille interne (12) aussi bien que l'aiguille externe (10) étant pressées par une force de serrage dans la direction du siège de soupape (23) alors que les deux aiguilles (10, 12) présentent des surfaces de pression pouvant être contraintes par la pression du carburant dans la chambre de pression (14), et subissent ainsi une force d'ouverture dirigée en sens inverse de la force de serrage,
    caractérisé en ce que
    le boítier (1) comporte une chambre de commande intérieure (42) dont la pression exerce au moins indirectement une force de serrage sur l'aiguille interne (12), et une chambre de commande extérieure (55) dont la pression exerce au moins indirectement une force de serrage sur l'aiguille externe (10), les deux chambres de commande (42, 55) étant reliées respectivement par un étranglement d'entrée (62, 48) doté d'une chambre haute pression du carburant (7), et une soupape de commande (74) disposée dans le boítier (1) présente une chambre de commande de soupape (77), reliée à la chambre de commande extérieure (55) à l'aide d'un étranglement de sortie extérieur (65), et pouvant être reliée à la chambre de commande intérieure (42) à l'aide d'un étranglement de sortie extérieur (67), un étranglement d'entrée de soupape (68) relie la chambre de commande de soupape (77) à la chambre haute pression du carburant (7), et un étranglement de sortie de soupape relie la chambre de commande de soupape (77) à une chambre d'huile de fuite, alors qu'un organe de soupape (75) disposé dans la chambre de commande de la soupape (77) est déplaçable entre deux positions terminales et, dans une position terminale, ferme l'étranglement de sortie de soupape (79) et laisse ouvertes toutes les autres liaisons de la chambre de commande de la soupape (77).
  2. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    l'organe de soupape (75), dans la deuxième position terminale, ferme l'étranglement de sortie intérieur (67) de la chambre de commande intérieure (42), et ouvre l'étranglement de sortie de soupape (79) de la chambre de commande de la soupape (77).
  3. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    l'organe de soupape (75), dans la deuxième position terminale, ferme l'étranglement d'entrée de soupape (68) de la chambre de commande de soupape (77), et ouvre l'étranglement de sortie de la soupape (79) de la chambre de commande de la soupape (77).
  4. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    l'organe de soupape (75) exécute un mouvement longitudinal entre ses deux positions terminales et prend appui respectivement sur un premier siège de soupape (80) et sur un deuxième siège de soupape (82) dans la chambre de commande de soupape (77), les deux sièges de soupape (80, 82) se faisant face.
  5. Injecteur de carburant selon la revendication 4,
    caractérisé en ce que
    le premier siège de soupape (80) est formé de manière conique et coopère avec une première surface d'étanchéité de soupape (84) bombée, formée sur l'organe de soupape (75), et le deuxième siège de soupape (82) est formé comme siège plat et coopère avec une deuxième surface d'étanchéité de soupape (86) plane, formée sur l'organe de soupape (75).
  6. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    l'organe de soupape (75) est relié à un actionneur (70), qui déplace l'organe de soupape (75) dans la chambre de commande de soupape (77).
  7. Injecteur de carburant selon la revendication 6,
    caractérisé en ce que
    l'actionneur est un actionneur électrique (70).
  8. Injecteur de carburant selon la revendication 7,
    caractérisé en ce que
    l'actionneur électrique est un piézo-actionneur (70).
  9. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    la chambre haute pression (7) dans le boítier (1) est formée comme un canal haute pression, par lequel le carburant est amené sous haute pression à la chambre de pression (14).
  10. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    l'organe de soupape (75) peut être maintenu entre les deux positions terminales dans une position intermédiaire, dans laquelle aucune des entrées de la chambre de commande de soupape (77) n'est fermée.
EP03003081A 2002-03-13 2003-02-13 Injecteur de combustible pour moteurs à combustion interne Expired - Lifetime EP1344929B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10210927 2002-03-13
DE10210927A DE10210927A1 (de) 2002-03-13 2002-03-13 Kraftstoffeinspritzventil für Brennkraftmaschinen

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EP1344929A1 EP1344929A1 (fr) 2003-09-17
EP1344929B1 true EP1344929B1 (fr) 2004-12-01

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JP (1) JP2003269282A (fr)
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Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10304605A1 (de) * 2003-02-05 2004-08-19 Robert Bosch Gmbh Kraftstoffeinspritzventil mit zwei koaxialen Ventilnadeln
DE10334209A1 (de) * 2003-07-26 2005-02-10 Robert Bosch Gmbh Kraftstoff-Einspritzvorrichtung für eine Brennkraftmaschine
DE10338228A1 (de) * 2003-08-20 2005-03-10 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
DE10348925A1 (de) * 2003-10-18 2005-05-12 Bosch Gmbh Robert Kraftstoffinjektor mit mehrteiligem, direktgesteuertem Einspritzventilglied
DE10348923A1 (de) * 2003-10-18 2005-05-19 Robert Bosch Gmbh Ventil zum Steuern von Flüssigkeiten
DE102004028521A1 (de) * 2004-06-11 2005-12-29 Robert Bosch Gmbh Kraftstoffinjektor mit mehrteiligem Einspritzventilglied und mit Druckverstärker
DE102004055267A1 (de) * 2004-11-17 2006-05-18 Robert Bosch Gmbh Kraftstoffeinspitzvorrichtung
EP1693561B1 (fr) * 2005-01-19 2008-03-05 Delphi Technologies, Inc. Soupape d'injection de carburant
DE602005001261T2 (de) 2005-01-19 2008-01-31 Delphi Technologies, Inc., Troy Brennstoffeinspritzventil
JP4239995B2 (ja) * 2005-03-28 2009-03-18 トヨタ自動車株式会社 内燃機関の燃料噴射装置
JP6828443B2 (ja) * 2017-01-10 2021-02-10 株式会社デンソー 燃料噴射装置

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3824467A1 (de) * 1988-07-19 1990-01-25 Man B & W Diesel Ag Einspritzventil
DE4115477C2 (de) * 1990-05-17 2003-02-06 Avl Verbrennungskraft Messtech Einspritzdüse für eine Brennkraftmaschine
AT3763U3 (de) * 1999-08-05 2000-12-27 Avl List Gmbh Nockenbetätigte einspritzeinrichtung für eine brennkraftmaschine
GB0021296D0 (en) * 2000-08-30 2000-10-18 Ricardo Consulting Eng A dual mode fuel injector

Also Published As

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DE10210927A1 (de) 2003-10-02
DE50300174D1 (de) 2005-01-05
JP2003269282A (ja) 2003-09-25
EP1344929A1 (fr) 2003-09-17

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