WO2005038230A1 - Gicleur pour un moteur a combustion interne - Google Patents

Gicleur pour un moteur a combustion interne Download PDF

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Publication number
WO2005038230A1
WO2005038230A1 PCT/DE2004/001713 DE2004001713W WO2005038230A1 WO 2005038230 A1 WO2005038230 A1 WO 2005038230A1 DE 2004001713 W DE2004001713 W DE 2004001713W WO 2005038230 A1 WO2005038230 A1 WO 2005038230A1
Authority
WO
WIPO (PCT)
Prior art keywords
nozzle needle
pressure
control
nozzle
force
Prior art date
Application number
PCT/DE2004/001713
Other languages
German (de)
English (en)
Inventor
Matthias Schnell
Original Assignee
Robert Bosch Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Publication of WO2005038230A1 publication Critical patent/WO2005038230A1/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
    • 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
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • F02M61/205—Means specially adapted for varying the spring tension or assisting the spring force to close the injection-valve, e.g. with damping of valve lift
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/46—Valves, e.g. injectors, with concentric valve bodies

Definitions

  • the present invention relates to an injection nozzle for an internal combustion engine with the features of the preamble of claim 1.
  • Such an injection nozzle is known from DE 100 58 153 AI, which has a nozzle body which is equipped with at least one first spray hole and with at least one second spray hole.
  • a first nozzle needle designed as a hollow needle is mounted in a stroke-adjustable manner in the nozzle body and can be used to control the injection of fuel through the at least one first spray hole.
  • a second nozzle needle is mounted coaxially to the stroke nozzle in the first nozzle needle, with which the injection of fuel through the at least one second spray hole can be controlled. With the help of a first spring, a first closing force is applied in the closing direction of the first
  • Nozzle needle acts, introduced into the first nozzle needle.
  • a second closing force which acts in the closing direction of the second nozzle needle, is introduced into the second nozzle needle with the aid of a second spring.
  • a section of a fuel supply line is also formed in the nozzle body, which connects a nozzle space formed in the nozzle body to a high-pressure line.
  • the first nozzle needle has a pressure stage which, when the nozzle space is pressurized, has a pressure level Direction of opening of the first nozzle needle acting force introduces into the first nozzle needle.
  • the first closing force can thus be overcome, as a result of which the first nozzle needle lifts off its seat and enables the at least one first spray hole to be supplied with fuel.
  • the first nozzle needle is pressure-controlled.
  • the second nozzle needle is drive-coupled to a control piston.
  • the control piston is arranged in a control chamber in which a pressure can be set by means of a suitable device.
  • the pressure prevailing in the control chamber generates at the control piston an effective force in the closing direction of the second nozzle needle, which force from the control piston to the second
  • Nozzle needle is transferred. Furthermore, the second nozzle needle downstream of the at least one first spray hole also has a compression stage. When the first nozzle needle is open, a force acting in the opening direction of the second nozzle needle acts on the second nozzle needle at the pressure stage of the second nozzle needle. This opening force is greater than the second closing force of the second spring.
  • the balance of forces of the second nozzle needle and thus the opening and closing of the second nozzle needle can be controlled by adjusting the pressure in the control chamber. At a relatively high pressure in the control room, the closing forces predominate, while at a relatively low pressure in the control room, the opening force predominates.
  • the second nozzle needle is not directly pressure-controlled, but rather indirectly and thus servo-controlled. The effort required to achieve such a servo control is comparatively large. Accordingly, there is an interest in an injection nozzle that can be produced comparatively cheaply.
  • the injection nozzle according to the invention with the features of the independent claim has the advantage over the fact that, with the aid of the force generator proposed according to the invention, the second closing force of the second spring acting on the second nozzle needle can be reduced or even eliminated as required.
  • the second nozzle needle opens almost simultaneously with the first nozzle needle if the second nozzle needle is equipped with a corresponding pressure stage which, when the first nozzle needle is opened, introduces a force acting in the opening direction of the second nozzle needle into the second nozzle needle.
  • a fuel supply line is provided, which one
  • the internal combustion engine is permanently under high pressure in the high pressure line.
  • the control valve is opened, as a result of which the high pressure also prevails in the nozzle chamber. If the first nozzle needle is equipped with a corresponding first pressure stage, effective opening forces that exceed the first closing force of the first spring can be introduced into the first nozzle needle in the opening direction of the first nozzle needle, so that the first nozzle needle is controlled by the pressure in the first pressure stage Nozzle room opens.
  • the high pressure in the high-pressure line can be varied, for example depending on the operating state (e.g. speed and / or load) of the internal combustion engine. While a smaller one
  • High pressure usually involves fuel injection through the at least one first spray hole is sufficient, a fuel injection through both the at least one first spray hole and the at least one second spray hole is desired for a greater high pressure.
  • the second closing force is selected such that it exceeds an opening force introduced into the second nozzle needle by the lower high pressure via a second pressure stage formed on the second nozzle needle. So that the second nozzle needle opens at higher high pressure, however, the second closing force can also be dimensioned such that it is overcome by an opening force that is introduced into the second nozzle needle at the second pressure stage when the first nozzle needle is open, so that the second nozzle needle also opens.
  • opening the control valve leads to a corresponding pressure increase in the fuel supply line or in the nozzle chamber.
  • this pressure increase does not occur suddenly, but along a time axis.
  • the pressure building up in the nozzle space thus first reaches the lower high pressure, at which the first nozzle needle opens, and only after a time delay does the higher high pressure, at which the second nozzle needle then also opens.
  • the second closing force can be reduced with the aid of the force generator according to the invention to such an extent that the second nozzle needle opens as soon as the lower high pressure is reached or at even lower pressures as soon as the first nozzle needle lifts out of its seat and the Can build up pressure at the second pressure stage.
  • a control line can be provided which connects the power generator directly to the; High-pressure line connects, the power generator then being designed so that it works in a controlled manner via the high pressure prevailing in the control line.
  • the force generator can be controlled by the high pressure of the high-pressure line, such that it is deactivated on the one hand at the lower high pressure and accordingly does not reduce the second closing force of the second spring, while on the other hand it is activated on the higher high pressure and accordingly the desired reduction or cancellation the second closing force.
  • the pressure prevailing in the high-pressure line is thus used directly to actuate the force generator, which automatically and without additional control or servo valve arrangements achieves largely delay-free opening of the second nozzle needle when the control valve is actuated to open the nozzle needles.
  • the control line connects the power generator directly to the high pressure line, i.e. independently of the
  • the force generator can have a control pressure stage which is arranged in a control room which communicates with the high-pressure line via the control line.
  • This pressure level is chosen so that it is dependent on the in the control room prevailing high pressure more or less reduces the second closing force. With a smaller high pressure there is no or only a small influence on the second closing force. In the case of larger high pressure, on the other hand, the second closing force is reduced to the desired extent, in particular completely eliminated.
  • the force generator has a particularly simple structure, which is advantageous for the adjustment of the switching point at high pressures.
  • Fig. 4 is a detailed view of the injection nozzle according to the invention, but in a further embodiment.
  • an injection nozzle 1 has a nozzle body 2, which with a Tip 3 protrudes into a mixture formation chamber or combustion chamber 4 of an internal combustion engine, which is otherwise not shown.
  • the nozzle body 2 is provided with at least one first spray hole 5 and with at least one second spray hole 6.
  • first ones there are several first ones
  • Spray holes 5 are provided, which are distributed along a ring arranged concentrically to a longitudinal axis 7.
  • a plurality of second spray holes 6 are usually also provided, which are likewise arranged along a ring which runs concentrically to the longitudinal axis 7.
  • a first nozzle needle 8 is mounted in a stroke-adjustable manner coaxial to the longitudinal axis 7.
  • the first nozzle needle 8 is designed as a hollow needle and contains coaxially a second nozzle needle 9, which is also mounted so as to be stroke-adjustable.
  • the nozzle body 2 contains a fuel supply line 10 or a section thereof.
  • the fuel supply line 10 is connected at one end to a high-pressure line 11 and at the other end to a nozzle chamber 12.
  • the high-pressure line 11 usually feeds several such injection nozzles 1 at the same time, the so-called "Comon-Rail principle".
  • An embodiment is also possible in which each injection nozzle 1 has a separate high-pressure line 11 fed by means of a corresponding injection pump.
  • control valve 13 is arranged, which is designed here as a 3/2-way valve and in the first switching position shown the branch connected to the nozzle chamber 12
  • Fuel supply line 10 connects to a return 14, which is relatively depressurized and can be formed, for example, by a fuel tank. In this first switching position, the branch of the fuel supply line 10 leading to the high pressure line 11 is blocked. in the In contrast to this, in the second switching position of the control valve 13, the fuel supply line 10 is activated, so that the high-pressure line 11 is connected to the nozzle chamber 12.
  • the nozzle chamber 12 communicates with the spray holes 5, 6 via an annular space 15.
  • the first nozzle needle 8 has a first sealing seat 16, which is arranged upstream of the spray holes 5, 6, so that the closed first nozzle needle 8 communicates the spray holes 5, 6 from
  • Nozzle space 12 separates. Furthermore, the first nozzle needle 8 is at least provided with a first pressure stage 17, which communicates with the nozzle chamber 12 via the annular space 15.
  • the first pressure stage 17 is formed in that a first seat cross section 18 in the first sealing seat 17 is smaller than a first guide cross section 19 of the first nozzle needle 8, with which the first nozzle needle 8 is guided in a first needle guide 20 so as to be stroke-adjustable.
  • a second sealing seat 21 of the second nozzle needle 9 is arranged between the at least one first spray hole 5 and the at least one second spray hole 6.
  • the second nozzle needle 9 is equipped with a second pressure stage 22 upstream of the second sealing seat 21 and downstream of the first sealing seat 16.
  • the second pressure stage 22 is formed in that a second seat cross section 23 in the second sealing seat 21 is smaller than a second guide cross section 24 of a second needle guide 25, in which the second nozzle needle 9 is mounted in the first nozzle needle 8.
  • the first nozzle needle 8 is drive-coupled to a first spring 26, which introduces a first closing force into the first nozzle needle 8.
  • the first closing force works the first spring 26 is dimensioned such that the first closing force is greater than the force acting on the first nozzle needle 8 due to the return pressure via the first pressure stage 17, which in
  • the first spring 26 is not supported directly on the first nozzle needle 8, but indirectly via a coupling element 27, which is formed by a centrally perforated disk in the embodiments of FIGS. 1 and 2 and in the embodiment of FIG. 3 on one of the First nozzle needle 8 facing end of a pressure sleeve 28 can be formed.
  • a second spring 29 is provided which generates a second closing force which acts on the second nozzle needle 9 in the closing direction.
  • the second spring 29 is not supported directly on the second nozzle needle 9, but on a push rod 30, which in turn is located on the second
  • Nozzle needle 9 is supported.
  • the push rod 30 could be firmly connected to the second nozzle needle 9.
  • an embodiment is preferred in which the push rod 30 and the second nozzle needle 9 merely abut one another at the ends which adjoin one another. In this way, compressive forces can be transmitted between the second nozzle needle 9 and the push rod 30.
  • the injection nozzle 1 is also equipped with a force generator 34 which can be activated and deactivated hydraulically in the present case.
  • This Force generator 34 is designed such that in the activated state it reduces or cancels the second closing force acting in second nozzle needle 9. In contrast to this, in the deactivated state, the second closing force can act on the second nozzle needle 9 essentially without restriction.
  • the hydraulically switchable force generator 34 shown here is connected to a control line 31, which connects the force generator 34 directly to the high-pressure line 11. It is particularly important here that the control line 31 is independent of the
  • Fuel supply line 10 is connected to the high pressure line 11.
  • the pressure prevailing in the high-pressure line 11 can be provided directly at the force generator 34.
  • the power generator 34 can be designed such that it operates in a pressure-controlled manner via the high pressure prevailing in the control line 31, that is to say via the high pressure prevailing in the high-pressure line 11.
  • the force generator 34 has a control pressure stage 32.
  • This control pressure stage 32 is arranged in a control chamber 33.
  • the control line 31 is connected to this control room 33, so that the control room 33 communicates with the high-pressure line 11 via the control line 31. Accordingly, the high pressure prevailing in the high-pressure line 11 is always present at the control pressure stage 32.
  • the control pressure stage 32 is formed on a control sleeve 35.
  • the control sleeve 35 is mounted here coaxially adjustable on the push rod 30.
  • the control sleeve 35 is equipped with a driver 36 which cooperates with a shoulder 37 formed on the push rod 30. If the driver 36 rests on the shoulder 37, one causes by the high pressure at the control pressure stage 32 in the Control ulse 35 force introduced the introduction of a force opposing the second closing force generated by the second spring 29.
  • the force balance of the second nozzle needle 9 is changed in such a way that the second closing force within the second nozzle needle 9 is reduced or - depending on the high pressure prevailing in the high pressure line 11 - completely eliminated.
  • a control spring 38 is also provided, which introduces a predetermined control force into the control sleeve 35.
  • the control spring 38 is matched to the control pressure stage 32 in such a way that the control sleeve 35 only reduces the second closing force in the second nozzle needle 9 from a predetermined high pressure set in the high pressure line 11.
  • the control sleeve 35 only when the pressure in the high-pressure line 11 exceeds a predetermined limit value or threshold value, can the control sleeve 35 reduce the force effect of the first spring 29, i.e., from this predetermined limit pressure, the force generator 34 is activated.
  • control sleeve 35 is arranged such that a distance 39 is formed between the driver 36 and the shoulder 37 in the deactivated state of the force generator 34 in the stroke direction of the control sleeve 35. This measure ensures that there is no interaction between the control sleeve 35 and the push rod 30 until contact is made with the driver 36 on the shoulder 37. Furthermore, smaller pressure fluctuations in the high-pressure line 11 can also be absorbed by the control sleeve 35 without this immediately reducing the second closing force.
  • control sleeve 35 can also be omitted, for example if the control pressure stage 32 is formed directly on the push rod 30 or alternatively directly on the second nozzle needle 9.
  • the first spring 26 is arranged in a first spring chamber 40, which communicates with the return 14 in a manner not shown. In this way, leakages can be removed.
  • the second spring 29 is also arranged in a second spring chamber 41, which is connected to the return 14 in a suitable manner, not shown.
  • control pressure stage 32 is on an axial end face 42 of the
  • Control sleeve 35 formed which faces away from the driver 36. That is, this axial end face 42 forms the control pressure stage 32, which is exposed to the control chamber 33.
  • the axial end face 42 of the control sleeve 35 facing away from the driver 36 is arranged in a return space 43, which is connected to the return 14 in a suitable manner.
  • the return space 43 communicates along the push rod 30 with the first spring space 40 and / or with the second spring space 41.
  • the control pressure stage 32 is arranged axially between the axial ends of the control sleeve 35, for which purpose the control line 31 is connected here a corresponding annular space 44 is connected. This annular space 44 forms the control space 33.
  • the control pressure stage 32 can be relatively small are dimensioned, which simplifies or enables the adjustment of the switching point of the control sleeve 35 or the force generator 34 at the relatively large high pressures that can be set in the high-pressure line 11.
  • the embodiment shown in FIG. 3 is also equipped with a closing force generator 45 which increases the first closing force when the fuel supply line 10 is blocked, that is to say when the control valve 13 is switched into the blocking position shown.
  • a closing force generator 45 which increases the first closing force when the fuel supply line 10 is blocked, that is to say when the control valve 13 is switched into the blocking position shown.
  • Closing force generator 45 a closing pressure stage 46, which is arranged in a closing pressure chamber 47.
  • This closing pressure chamber 47 communicates via a throttle line 48 with the high-pressure fuel line 10, specifically with the branch connected to the nozzle chamber 12.
  • the closing pressure stage 46 is formed on an axial end of the pressure sleeve 28 facing away from the first nozzle needle 8.
  • the pressure sleeve 28 corresponds to the pressure rod 30, but cooperates with the first nozzle needle 8 in order to transmit pressure forces between the first nozzle needle 8 and the pressure sleeve 28.
  • the coupling element 27 or the section of the pressure sleeve 28 serving as a coupling element overlaps in the radial direction the axial end of the second nozzle needle 9 facing away from the spray holes 5, 6. In this way, the coupling element 27 can take the second nozzle needle 9 with it when the first nozzle needle 8 is closed , An axial play 49 is expediently provided between the coupling element 27 and the second nozzle needle 9, which simplifies the manufacture of the injection nozzle 1.
  • the force generator 34 according to the invention or the injection nozzle 1 equipped with it operates as follows: In the initial position shown in FIGS. 1 to 3, both nozzle needles 8, 9 are closed and the control valve 13 interrupts the connection of the fuel supply line 10 to the high-pressure line 11. Accordingly, there is a comparatively low pressure in the nozzle space 12, so that the force balance at the first nozzle needle 8 leads to a closing force acting in the closing direction.
  • This closing force is generated in the embodiments of FIGS. 1 and 2 exclusively by the first spring 26, while in the embodiment according to FIG. 3 also the im
  • Closing pressure chamber 47 prevailing pressure can introduce an additional closing force on the pressure sleeve 28 and thus on the first nozzle needle 8.
  • the return pressure is usually comparatively low. Since the second pressure stage 22 of the second nozzle needle 9 is decoupled from the nozzle chamber 12 when the first nozzle needle 8 is closed, there are no opening forces for the second nozzle needle 9 at the second pressure stage 22. If there is a relatively low first high pressure in the high pressure line 11, the control sleeve predominates 35 generated by the control spring 38
  • the control valve 13 opens the connection of the fuel supply line 10 to the high pressure line 11. Accordingly, the smaller first high pressure builds up in the nozzle chamber 12 and thus at the first pressure stage 17 of the first nozzle needle 9.
  • the first spring 26 is dimensioned such that the smaller first high pressure acting on the first pressure stage 17 is sufficient to lift the first nozzle needle 8 out of its first sealing seat 16.
  • the first nozzle needle 8 and fuel open can be sprayed into the combustion chamber 4 through the at least one first spray hole 5.
  • the relatively small first high pressure is also present at the second pressure stage 22.
  • the second spring 29 is dimensioned such that the smaller first high pressure acting on the second pressure stage 22 is not sufficient to lift the second nozzle needle 9 out of its second sealing seat 21. Accordingly, in the case of the smaller first high pressure, the at least one second spray hole 6 remains closed.
  • the control valve 13 is again moved into the first closed position shown.
  • the nozzle chamber 12 is connected to the return 14, as a result of which the pressure in the nozzle chamber 12 drops. Accordingly, the pressure at the first pressure stage 17 also drops, so that the force balance at the first nozzle needle 8 is reversed again and the closing forces predominate.
  • the first nozzle needle 8 then moves into its first sealing seat 16.
  • the pressure in the high-pressure line 11 is first increased to a relatively large second high pressure. Because of the control line 31, this larger second high pressure is also present at the control pressure stage 32.
  • the control spring 38 is dimensioned such that the larger second high pressure adjusts the control sleeve 35. As a result, the driver 36 comes to rest on the shoulder 37 and can thereby relieve the pressure rod 30 of the force of the second spring 29 more or less. In principle, it is even possible that the control sleeve 35 lifts the push rod 30, whereby the second nozzle needle 9 is completely relieved.
  • the control valve 13 is now adjusted to its open position at this larger second high pressure in the high pressure line 11, the larger second high pressure builds up in a corresponding manner in the nozzle chamber 12, which is then also present at the first pressure stage 17. Accordingly, the first nozzle needle 8 lifts off the first sealing seat 16 again. As soon as the first nozzle needle 8 lifts from its first sealing seat 16, pressure builds up at the second pressure stage 22 of the second nozzle needle 9. Since the second nozzle needle 9 is only seated in its second sealing seat 21 with reduced closing force or without closing force, the second nozzle needle 9 can lift out of its second sealing seat 22 even at relatively small pressures acting on the second pressure stage 22. Accordingly, the second nozzle needle 9 opens almost without delay with the first nozzle needle 8. As a result, all of the spray holes 5, 6 communicate with the nozzle chamber 12, so that the desired injection into the combustion chamber 4 takes place through all the spray holes 5, 6.
  • the control valve 13 is brought back into the closed position shown.
  • the pressure in the nozzle chamber 12 can relax via the return 14.
  • the large restoring forces of the first nozzle needle 8 become effective again and drive the first nozzle needle 8 back into its closed position.
  • the coupling element 27 can take the second nozzle needle 9 with it, provided that the closing forces acting on the second nozzle needle 9 are not sufficient to close the second nozzle needle 9 sufficiently quickly.
  • the mode of operation of the closing pressure generator 45 is explained in more detail below:
  • the nozzle needles 8, 9 are closed and the control valve 13 connects the branch of the fuel supply line 10 that communicates with the nozzle chamber 12 to the return line 14. Accordingly, the return pressure prevails in this branch of the fuel supply line 10. This return pressure consequently also prevails in the closing pressure chamber 47 via the throttle line 48.
  • Fuel supply line 10 the respective high pressure of the high pressure line 11. Because of the throttling effect of the throttle line 48, this pressure can also build up in the closing pressure chamber 47 only with a delay. However, the opening movement of the first nozzle needle 8, which the pressure sleeve 28 inevitably follows, nevertheless leads to a strong pressure increase in the closing pressure space 47. When the first nozzle needle 9 is open, the respective high pressure of the high-pressure line 11 is then set via the throttle line 48 in the closing pressure chamber 47.
  • the throttle line 48 hinders the pressure reduction in the closing pressure chamber 47, so that there is still a relatively high pressure for a short time.
  • This high pressure leads into the closing pressure stage 46 a relatively large closing force into the pressure sleeve 28 and via this into the first nozzle needle 9, which supports the closing force of the first spring 26.
  • Pressure in the closing pressure chamber 47 thus generates an impulse Closing force, which significantly increases the acceleration of the pressure sleeve 28 and the first nozzle needle 8 in the closing direction. In this way, the closing process can be shortened. It is clear that by adjusting the pressure sleeve 28 in the direction of the spray hole 5, 6, the pressure in the closing pressure chamber 47 quickly decreases.
  • the control sleeve 35 can lift the push rod 30 slightly off the second nozzle needle 9. So that the second nozzle needle 9 still remains in its second sealing seat 21, at least one coupling spring 50 can be provided according to FIG. 4. This coupling spring 50 is supported on the one hand on the second nozzle needle 9 and on the other
  • Coupling element 27 Coupling element 27.
  • a further coupling spring 50 ⁇ can be provided, which is also supported on the one hand on the second nozzle needle 9 but on the other hand on the push rod 30.
  • the respective coupling spring produces 50 or 50 ⁇ still remaining, relatively small closing force, which drives the second nozzle needle 9 in the closing direction against its second sealing seat 21st In this way, premature, undesired lifting of the second nozzle needle 9 can be avoided even when the force of the second spring 29 is completely eliminated.

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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)

Abstract

L'invention concerne un gicleur (1) destiné à un moteur à combustion interne et comprenant un corps de gicleur (2) pourvu d'au moins un premier trou d'injection (5) et d'au moins un deuxième trou d'injection (6), une première aiguille de gicleur (8) servant à commander l'injection de carburant à travers le premier trou d'injection (5), une deuxième aiguille de gicleur (9) placée dans la première aiguille de gicleur (8) et servant à commander l'injection de carburant à travers le deuxième trou d'injection (6), un premier ressort (26) servant à appliquer à la première aiguille de gicleur (8) une première force de fermeture agissant dans le sens de fermeture de la première aiguille de gicleur (8), ainsi qu'un deuxième ressort (29) servant à appliquer à la deuxième aiguille de gicleur (9) une deuxième force de fermeture agissant dans le sens de fermeture de la deuxième aiguille de gicleur (9). L'invention vise à améliorer la structure du gicleur (1) selon l'invention. A cet effet, le gicleur selon l'invention comprend également un générateur de force (34) qui, à l'état activé, réduit ou élimine la deuxième force de fermeture.
PCT/DE2004/001713 2003-09-23 2004-07-30 Gicleur pour un moteur a combustion interne WO2005038230A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10344000.3 2003-09-23
DE2003144000 DE10344000A1 (de) 2003-09-23 2003-09-23 Einspritzdüse für eine Brennkraftmaschine

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WO2005038230A1 true WO2005038230A1 (fr) 2005-04-28

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Publication number Priority date Publication date Assignee Title
CN104533684B (zh) * 2014-11-26 2017-07-28 中国北方发动机研究所(天津) 一种双控制阀多密封带燃油喷嘴
DE102020212697B4 (de) 2020-10-08 2022-08-25 Ford Global Technologies, Llc Injektor, Dieselmotor und Kraftfahrzeug

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JPS59147862A (ja) * 1983-02-12 1984-08-24 Toyota Motor Corp デイ−ゼルエンジンの燃料噴射弁
JPS60228766A (ja) * 1984-04-26 1985-11-14 Nissan Motor Co Ltd 直噴式デイ−ゼル機関の燃料噴射ノズル
US5899389A (en) * 1997-06-02 1999-05-04 Cummins Engine Company, Inc. Two stage fuel injector nozzle assembly
US20030038185A1 (en) * 2001-08-22 2003-02-27 Carrol John T. Variable pressure fuel injection system with dual flow rate injector
DE10141679A1 (de) * 2001-08-25 2003-03-06 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine
DE10141678A1 (de) * 2001-08-25 2003-05-08 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59147862A (ja) * 1983-02-12 1984-08-24 Toyota Motor Corp デイ−ゼルエンジンの燃料噴射弁
JPS60228766A (ja) * 1984-04-26 1985-11-14 Nissan Motor Co Ltd 直噴式デイ−ゼル機関の燃料噴射ノズル
US5899389A (en) * 1997-06-02 1999-05-04 Cummins Engine Company, Inc. Two stage fuel injector nozzle assembly
US20030038185A1 (en) * 2001-08-22 2003-02-27 Carrol John T. Variable pressure fuel injection system with dual flow rate injector
DE10141679A1 (de) * 2001-08-25 2003-03-06 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine
DE10141678A1 (de) * 2001-08-25 2003-05-08 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine

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