EP1778967B1 - Injecteur - Google Patents

Injecteur Download PDF

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Publication number
EP1778967B1
EP1778967B1 EP04762760A EP04762760A EP1778967B1 EP 1778967 B1 EP1778967 B1 EP 1778967B1 EP 04762760 A EP04762760 A EP 04762760A EP 04762760 A EP04762760 A EP 04762760A EP 1778967 B1 EP1778967 B1 EP 1778967B1
Authority
EP
European Patent Office
Prior art keywords
nozzle
needle
control
nozzle needle
pressure
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.)
Not-in-force
Application number
EP04762760A
Other languages
German (de)
English (en)
Other versions
EP1778967A1 (fr
Inventor
Achim Brenk
Martin Kropp
Kilian Bucher
Dietmar Greulich
Matthias Schnell
Elmar Zipperer
Oezguer Tuerker
Reiner Koch
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1778967A1 publication Critical patent/EP1778967A1/fr
Application granted granted Critical
Publication of EP1778967B1 publication Critical patent/EP1778967B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F02M63/0028—Valves characterised by the valve actuating means hydraulic
    • F02M63/0029—Valves characterised by the valve actuating means hydraulic using a pilot valve controlling a hydraulic chamber
    • 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
    • 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
    • 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
    • F02M63/0003—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure
    • F02M63/0005—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure using valves actuated by fluid 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
    • 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, in particular in a motor vehicle, having the features of the independent claim.
  • Such an injection nozzle is off DE 102 21384 A1 and DE 100 58 153 A1 known.
  • the injection nozzle contains in a nozzle body designed as a hollow needle first nozzle needle with which an injection of fuel is controlled by at least one first injection hole. Furthermore, a second nozzle needle is arranged coaxially in the first nozzle needle, with which an injection of fuel through at least one second injection hole is controllable.
  • a nozzle space is formed, which is connectable via a fuel supply line with a high pressure source.
  • the first nozzle needle has at least one first pressure stage, which is arranged in the nozzle chamber or in a communicating with the nozzle chamber space and can be acted upon in the respective space with an injection pressure.
  • a first return spring which acts on the first nozzle needle or on a first needle assembly comprising the first nozzle needle and introduces therein a closing force acting in the closing direction.
  • This first return spring is arranged in a spring chamber which communicates with a relatively pressureless return system.
  • the nozzle chamber is connected to the high pressure source.
  • the injection pressure then building up in the nozzle chamber generates at the first pressure stage the opening forces which the closing forces outweigh and open the first nozzle needle.
  • the first nozzle needle can be closed again. Accordingly, the first nozzle needle is controlled directly by the pressure prevailing in the nozzle chamber injection pressure.
  • a servo device for controlling the second nozzle needle, comprising a control chamber and a control piston mounted in a manner adjustable in stroke, which is drive-coupled to the second nozzle needle or to a second needle assembly containing the second nozzle needle.
  • a control pressure can be adjusted in the control room. As long as the second nozzle needle is to remain closed, a relatively high control pressure is set.
  • the second nozzle needle has at least one second pressure stage, which is arranged in a space which communicates with the first nozzle needle with the nozzle chamber, so that then the second pressure stage is acted upon by the injection pressure to initiate an opening force acting in the opening direction of the second nozzle needle therein , If the second nozzle needle is also to be opened when the first nozzle needle is open, the control pressure in the control chamber is lowered so that the opening forces on the second nozzle needle predominate. To close the second nozzle needle, the control pressure can be increased again in a corresponding manner. The second nozzle needle is thus not controlled directly by the injection pressure, but by the principle independent of the injection pressure control pressure. In that regard, the second nozzle needle is servo-controlled.
  • the injection pressure required for opening is chosen to be comparatively small by a corresponding design of the first return spring in order to achieve a low combustion noise.
  • this has the disadvantage that in the conventional injection nozzle, the injection through the at least one first injection hole can also be terminated only at a comparatively low injection pressure. Accordingly, the injection takes place towards the end with a relatively low injection pressure, which leads to a deteriorated treatment in the respective combustion chamber and accordingly to higher soot emissions.
  • a quick closing of the first nozzle needle at a comparatively high injection pressure could reduce soot emissions.
  • the increase of the closing pressure would automatically lead to an increase of the opening pressure, that is, the first nozzle needle would not until at higher soot emissions.
  • a quick closing of the first nozzle needle at a comparatively high injection pressure could reduce soot emissions.
  • the increase of the closing pressure would automatically lead to an increase of the opening pressure; that is, the first nozzle needle would open only at higher injection pressures. This leads to an increased combustion noise.
  • high closing pressures lead to correspondingly high closing speeds, so that the respective nozzle needle then tends to bounce.
  • a bounce of the first nozzle needle can lead to undesirable post-injection and thus to increased HC emissions.
  • both nozzle needles are controlled separately by means of a servo-valve by depressurizing the respective control room.
  • the injection nozzle according to the invention with the features of the independent. Claim has the advantage that on the one hand already opens the opening process at a comparatively low Eirispritzdruck and on the other hand already closes the closing process at a relatively high injection pressure.
  • This contradictory behavior of the first nozzle needle is achieved in the invention by means of a control chamber which is simultaneously connected to the high pressure source and separated from the nozzle chamber, wherein the pressure build-up and the pressure reduction in the control chamber by means of a corresponding throttling relative to the nozzle chamber in time Delayed.
  • a first control needle associated first control surface is arranged such that the control pressure leads to an additional closing force in the first nozzle needle.
  • the faster increasing injection pressure in the nozzle chamber can initiate sufficiently large opening forces in the first nozzle needle very early. Accordingly, the first nozzle needle already opens at a relatively low Injection pressure.
  • the pressure in the control chamber continues to rise and, depending on the opening duration, can reach or even exceed the pressure level of the injection pressure, since a certain pressure drop occurs in the nozzle chamber through the fuel outlet at the at least one first injection hole.
  • the closing process the injection pressure drops in the nozzle chamber. Accordingly, the opening forces effective at the first nozzle needle also decrease.
  • the control pressure drops significantly slower in the control chamber due to the throttling, so that over the first control surface comparatively large closing forces can be introduced into the first nozzle needle. Accordingly, the closing forces already outweigh even at a relatively high injection pressure and can drive the first nozzle needle in the closing direction. Accordingly, the closing process already takes place at a higher injection pressure.
  • the rapid opening at low injection pressure maintains a low combustion noise.
  • a sufficient mixture preparation and thus a reduced emission of soot is achieved by the correspondingly fast closing at a comparatively high injection pressure until the end of the injection. Since the control pressure decreases when closing, and the risk of bouncing the first nozzle needle can be reduced, so that post-injections can be avoided. It is also important that the control pressure does not have to be permanently provided, which considerably simplifies the construction of the injection nozzle.
  • the throttling of the control line is selected so that at a predetermined opening time of the first nozzle needle, the control pressure in the control chamber exceeds the injection pressure in the nozzle chamber, such that predominate on the first nozzle needle or on the first needle assembly, the closing forces.
  • the first nozzle needle is automatically closed again, regardless of whether the fuel supply line is still connected to the high pressure source or not.
  • the active principle in which the control pressure prevailing in the control chamber is used to increase the closing forces, can also be referred to below as active needle closing.
  • a control line provided for connecting the control chamber to the high-pressure source communicates with the fuel supply line, so that the control line can be connected to the high-pressure source via the power supply line.
  • This design has the advantage that only a single valve is required to connect or disconnect the fuel supply line from the high pressure source. The pressure build-up and the pressure reduction then start simultaneously in this communicating system.
  • the pressure in the control chamber can exceed the pressure in the nozzle chamber when the injection time is sufficiently long since, when the first nozzle needle is open in the nozzle chamber, a certain pressure drop occurs via the at least one first injection hole.
  • control chamber may also be connected via a return line to a relatively pressureless return system, in which case the return line is throttled more than the control line.
  • the return line is throttled more than the control line.
  • a further embodiment provides for controlling an outlet opening of the return line arranged in the control chamber as a function of the stroke of the first nozzle needle in such a way that the mouth opening is more or less closed when the first nozzle needle is open. In this way, the effluent via the return line control losses are minimized, which improves the hydraulic efficiency and allows increased injection pressure.
  • the second nozzle needle or a second needle assembly containing the second nozzle needle having a second control surface which is also arranged in the control chamber and therein acted upon by the control pressure acting in the closing direction.
  • an active needle closing can also be realized for the second nozzle needle. That is, the control pressure prevailing in the control chamber increases when closing even with the second nozzle needle acting in the closing direction closing forces. Accordingly, the second nozzle needle can be closed at a higher injection pressure.
  • an injection nozzle 1 according to the invention comprises a first nozzle needle 2 and a second nozzle needle 3.
  • the first nozzle needle 2 is mounted in a stroke-adjustable manner by means of a first needle guide 4 in a nozzle body not designated in detail.
  • the first nozzle needle 2 serves to control at least one first injection hole 5, which opens into an injection space 6, which is for example a mixture-forming space or a combustion space of a cylinder of an internal combustion engine.
  • a first return spring 8 is provided in the first nozzle needle 2 and is arranged in a first spring chamber 9.
  • the first nozzle needle 2 is usually a component of a first needle assembly 10, which serves for the transmission of compressive forces and forms a common hubver ause unit.
  • the individual components of the first needle assembly 10 can lie loosely in the stroke direction. It is also possible that at least two components of the first needle assembly 10 are attached to each other or made as an integral unit.
  • the nozzle body contains a nozzle chamber 11 in which the first nozzle needle 2 or the first needle assembly 10 has a first pressure stage 12.
  • a pressure prevailing in the nozzle chamber 11 leads via this first pressure stage 12 opening forces into the first nozzle needle 2 and the first needle assembly 10, which act in an opening direction 13 indicated by an arrow.
  • the second nozzle needle 3 is coaxially mounted in a stroke-adjustable manner in the first nozzle needle 2 designed as a hollow needle, for which purpose a second needle guide 14 is formed between the nozzle needles 2, 3.
  • the second nozzle needle 3 serves to control at least one second injection hole 15, which also opens into the spray chamber 6.
  • a plurality of first injection holes 5 and / or a plurality of second injection holes 15 are provided, which are preferably arranged uniformly distributed in each case in the circumferential direction along a ring.
  • the second nozzle needle 3 is usually a part of a second needle assembly 16, the components of which form a stroke-adjustable unit which serves to transmit compressive forces. Again, the individual components of the second needle assembly 16 may rest loosely against each other. It is also possible that at least two of the components of the second needle assembly 16 are attached to each other or are formed by an integrally manufactured one-piece component.
  • the nozzle chamber 12 communicates with an annular space 17, which encloses the first nozzle needle 2 and leads to the spray holes 5, 15.
  • the second nozzle needle 3 moves into a second sealing seat 19, which is likewise arranged in the annular space 17, but downstream of the at least one first injection hole 5 and upstream of the at least one second injection hole 15.
  • the second nozzle needle 3 has at least one second pressure stage 20 in the annular space 17.
  • the subspace of the annular space 17 in which the second pressure stage 20 is arranged communicates with the nozzle space 11 via the remaining annular space 17 20 acting pressure then initiates an opening force acting in the opening direction 13 in the second nozzle needle 3 and in the second needle assembly 16 a.
  • the first pressure stages 12 are formed in that a first guide cross-sectional area 21 of the first needle guide 4 is larger than a first seat cross-sectional area 22 of the first sealing seat 18.
  • the second pressure stage 20 is formed by a second guide cross-sectional area 23 of the second needle guide 14 being larger is as a second seat cross-sectional area 24 of the second sealing seat 19th
  • a second return spring 25 is provided, which is associated with the second nozzle needle 3 and the second needle assembly 16 and initiates closing forces acting in the closing direction 7 therein.
  • the second return spring 25 is arranged in a second spring chamber 26.
  • the two spring chambers 9 and 26 are combined to form a common spring chamber 9, 26.
  • the nozzle chamber 11 can be connected via a fuel supply line 27 to a high-pressure source 28.
  • the high-pressure source 28 is formed here by a common for several such injectors 1 provided high-pressure line 29, so-called “common rail system”.
  • the common high pressure line 29 is fed by a high pressure pump 30. It is also possible to provide a separate high-pressure pump for each injection nozzle 1.
  • a metering valve 31 is arranged in the fuel supply line 27. With the help of the metering valve 31, the fuel supply line 27 can be opened and locked.
  • the metering valve 31 is designed here as a hydraulically actuated valve.
  • a corresponding switching valve 32 is provided, which in turn can be configured, for example, as a magnetically actuated switching valve, that is, as a solenoid valve.
  • the metering valve 31 includes a valve body 33 which is adjustable for opening and closing by pressure forces acting on opposing control surfaces.
  • a pressure drop can be generated on the one surface of the valve body 33 in the metering valve 31, which causes opening of the valve body 33, with the result that the fuel supply line 27 is then connected to the high-pressure point 28.
  • the solenoid valve 31 By closing the solenoid valve 31, the pressure at the respective surface of the Valve body 33 is rebuilt, whereby the metering valve 31 closes and the fuel supply line 27 is again separated from the high-pressure source 28.
  • the metering valve 31 To open and close the fuel supply line 27, the metering valve 31 includes a first control edge 34. Simultaneously, the metering valve 31 according to the preferred embodiment shown here, a second control edge 35 have, via the fuel supply line 27 can be connected to a return system 36.
  • the two control edges 34, 35 are coordinated so that upon opening the first control edge 34 inevitably closes the second control edge 35 and vice versa. This results in the separation of the fuel supply line 27 from the high pressure source 28 quasi simultaneously connecting the fuel supply line 27 with the return system 36.
  • In the return system 36 is usually a relatively low pressure, so that when separating the fuel supply line 27 from the high pressure shaft 28 in the fuel supply line 27 of Pressure can be relaxed immediately in the return system 36.
  • the return system 36 may, as here, contain a pressure-maintaining valve 37 which maintains a minimum pressure in the fuel supply line 27.
  • a control chamber 38 is now provided which can also be connected to the high-pressure source 28 via a control line 39.
  • the control line 39 is throttled more than the fuel supply line 27. This is achieved for example by means of a corresponding control throttle 40.
  • the control line 39 is connected to the fuel supply line 27 downstream of the metering valve 31. This means that with the metering valve 31, the fuel supply line 27 and the control line 39 can be simultaneously connected to the high-pressure source 28 or separated from it.
  • the first nozzle needle 2 or the first needle assembly 10 has a first control surface 41, which is arranged in the control chamber 38 and can be acted upon there by a control pressure prevailing in the control chamber 38.
  • the first control surface 41 is remote from the spray holes 5, 15, so that the control pressure acting on it initiates closing forces in the first nozzle needle 2 and in the first needle assembly 10.
  • the second nozzle needle 3 or the second needle dressing 16 is also equipped with a second control surface 42, which is likewise arranged in the control chamber 38. Also, the second control surface 42 is remote from the spray holes 5, 15, so that pressurization of the second control surface 42 in the control chamber 38 initiates closing forces in the second nozzle needle 3 and the second needle assembly 16.
  • control chamber 38 is formed by the first spring chamber 9 and by the second spring chamber 26 and by the common spring chamber 9, 26.
  • a mouth opening 45 with which the return line 43 opens into the control chamber 38, positioned so that it can be controlled in dependence of the stroke of the first nozzle needle 2.
  • this orifice opening 45 is positioned so that the first nozzle needle 2 and the first needle assembly 10 more or less covers the mouth opening 45 at least when reaching a maximum opening position of the first nozzle needle 2, so that the mouth opening 45 and thus the return line 43 in corresponding extent more or less closed.
  • both nozzle needles 2, 3 are closed. Accordingly, the metering valve 31 and the solenoid valve 32 are closed.
  • a relatively low fuel high pressure is provided in the pressure source 28.
  • the solenoid valve 32 By opening the solenoid valve 32, the metering valve 31 is opened, so that the fuel supply line 27 is connected to the high-pressure source 28. Accordingly, the relatively low injection pressure builds up in the pressure chamber 11 and in the annular space 17.
  • the injection pressure at the first pressure stages 12 reaches a comparatively low opening threshold value, they predominate in the first nozzle needle 2 or in the first needle assembly 10, the opening forces and the first nozzle needle 2 lifts off from the first sealing seat 18.
  • control chamber 38 communicates via the control line 39 with the fuel supply line 27, a control pressure builds up in the control chamber 38. However, takes place in the control chamber 38 in comparison to the nozzle chamber 11, the pressure buildup delayed in time, which is brought about by the targeted throttling 40 of the control line 39. Accordingly, the first nozzle needle 2 can already lift off at the desired relatively low opening pressure and release the at least one first injection hole 5.
  • the pressure in the control chamber 38 can continue to build until it reaches the maximum value of the high pressure source 28 predetermined by the value. Since the opening of the first nozzle needle 2 additional surfaces communicate with the annulus 17, the interpretation can be made so that the first nozzle needle 2 remains open, even if the pressures in the nozzle chamber 11 and the control chamber 38 are more or less balanced.
  • the solenoid valve 32 is now closed again.
  • the metering valve 31 also closes.
  • the fuel supply line 27 is disconnected from the high-pressure source 28 and simultaneously connected to the return system 36, whereby the pressure in the fuel supply line 27 can drop relatively quickly.
  • the throttled control line 39 Due to the throttled control line 39, however, the pressure in the control chamber 38 can last longer, so that very high closing forces can now be introduced into the first nozzle needle 2 or into the first needle dressing 10 at the first control surface 41. These high closing forces generate a pulse-like acceleration of the first nozzle needle 2 in the closing direction.
  • the delayed pressure reduction in the control chamber 38 thus allows a very dynamic overcoming of the inertial forces of the first nozzle needle 2 and the first needle assembly 10, so that the first nozzle needle 2 can be set in motion very quickly. Accordingly, the first nozzle needle 2 already closes at a still prevailing in the nozzle chamber 11 pressure, which may be well above the aforementioned, desired low opening pressure.
  • the injection pressure can also build up at the second pressure stage 20.
  • the high-pressure source 28 provides the relatively low high pressure, the second nozzle needle 3 can not yet open, because the attacking closing forces and the second pressure stage 20 are matched accordingly.
  • a correspondingly increased high pressure is provided.
  • the solenoid valve 32 By opening the solenoid valve 32, the metering valve 31 is driven to open.
  • the fuel supply line 27 is connected to the high-pressure source 28, so that the correspondingly increased injection pressure can initially build up in the nozzle chamber 11 and in the annular space 17 as a result.
  • the first nozzle needle 2 Upon reaching the opening threshold, the first nozzle needle 2 is first opened again. Subsequently, the injection pressure at the second pressure stage 20 can build up. As soon as the intended for the second nozzle needle 3 higher opening pressure is reached, and the second nozzle needle 3 can lift off from the second sealing seat 19, so that the desired fuel injection through all the injection holes 5, 15 can take place.
  • the opening movement of the second nozzle needle 3 and the second needle assembly 16 is braked by the building up in the control chamber 38 pressure.
  • the second control surface 42 is retracted into the second control chamber 38, which is associated with a displacement of hydraulic volume in the control chamber 38. Accordingly, in the control chamber 38, a correspondingly rapid increase in pressure then occurs, which slows down the opening movement of the second needle assembly 16. This is advantageous in the case of the second nozzle needle 3, since in this way a jump in quantity can be reduced when the second nozzle needle 3 is opened.
  • the braking effect by the pressure build-up in the control chamber 38 results in a corresponding manner even in the first nozzle needle 2, where it does not affect so much there, since the first nozzle needle 2 so much earlier penetrates at a significantly lower control pressure in the control chamber 38.
  • the solenoid valve 32 is then closed again, with the result that also the metering valve 31 closes and the fuel supply line 27 separates from the high-pressure source 28.
  • the fuel supply line 27 is connected to the return system 36, so that the pressure in the nozzle chamber 11 and in the annular space 17 may drop. Since the now increased to a relatively high value control pressure degrades only delayed due to the throttling, 38 can now in the control room very high closing forces are introduced to the control surfaces 41 and 42. This results in a strong acceleration of the two nozzle needles 2, 3 or the needle assemblies 10, 16. Accordingly, the nozzle needles 2, 3 are closed very early, so even at a relatively high pressure in the nozzle chamber 11.
  • the return line 43 makes it possible in the in Fig. 1 shown embodiment, the pressure build-up in the control chamber 38 in addition to delay. At the same time this causes a flushing of the control chamber 38. Due to the flow through the control chamber 38, a cooling effect can also be realized.
  • the return line 43 is blocked in the embodiment shown here, since the first nozzle needle 2 or the first needle assembly 10 covers the mouth opening 45 in the control chamber 38. Thus, during fuel injection, control losses can be reduced. At the same time thereby the achievable injection pressure can be increased.
  • the return line 43 is opened again, so that the pressure in the control chamber 38 can then break down faster. This is particularly advantageous when only short time intervals occur between successive injection events, such as multiple injections per stroke in each cylinder.
  • the injection nozzle 1 can do without the return line 43.
  • the charging and relaxation of the control chamber 38 then takes place exclusively via the control line 39.
  • the first control surface 41 is provided, which is associated with the first needle assembly 10.
  • the first needle assembly 10 contains here in addition to the first nozzle needle 2, a control piston 46 which is mounted in the control chamber 38 adjustable in height. On this control piston 46 is supported on a side facing away from the first nozzle needle 2 from a coupling sleeve 47, which is supported at its end remote from the control piston 46 at a first spring plate 48.
  • the first spring plate 48 is mounted in a manner adjustable in stroke in the first spring chamber 9 and receives the closing forces of the first return spring 8. Accordingly, in the embodiment according to Fig. 2 the control chamber 38 is formed separately from the first control chamber 9. The same applies then with regard to the second spring chamber 26, which is still summarized here with the first spring chamber 9 to a common spring chamber 9, 26.
  • the second needle assembly 16 comprises, in addition to the second nozzle needle 3 here a coupling rod 49 which is supported via a punch 50 on a second spring plate 51.
  • the second spring plate 51 is mounted adjustable in stroke in the second spring chamber 46 and receives the closing forces of the second return spring 25.
  • a driver coupling 52 is formed here.
  • This driver coupling 52 is designed so that the first needle assembly 10 when closing the first nozzle needle 2 entrains the second needle assembly 16 or at least the second nozzle needle 3 in the closing direction. This is achieved, for example, in that the control piston 46 protrudes radially inwards beyond an axial end face 53 of the second nozzle needle 3 facing away from the spray holes 5, 15. It may be appropriate that in the closed position of both nozzle needles 2, 3, a slight axial clearance between the control piston 46 and said axial end face 53 of the second nozzle needle 3 is present.
  • the control piston 46 When opening the first nozzle needle 2, the control piston 46 is hineinver Guardian in the control chamber 38 in the opening direction 13.
  • the control piston 46 or the driver coupling 52 form an opening stop for the second nozzle needle 3. That is, when completely open the second nozzle needle 3, this comes to the control piston 46 axially to the plant. If now the nozzle needles 2, 3 are to be closed quickly, the pressure drop in the nozzle chamber 11 in conjunction with the control only in the control room 38 dissipates rapidly reducing control pressure to a strong acceleration of the control piston 46 and thus the entire first needle assembly 10 in the closing direction second nozzle needle 3 is coupled by their abutment on the control piston 46 with the first needle assembly 10, the second needle needle 3 is necessarily taken from the first needle assembly 10 in the closing direction 7.
  • the first control surface 41 formed on the control piston 46 is designed to accelerate both nozzle needles 2, 3.
  • a connection 54 is provided to the return system 36 to dissipate leaks through the first needle guide 4 and / or by a guide of the control piston 46.
  • the separate arrangement of the control chamber 38 makes it possible to manufacture the volume of the control chamber 38 with increased precision.
  • the volume of the control room 38 in the embodiment depends Fig. 2 no longer from the volume of the return springs 8 and 25, which may vary depending on manufacturing tolerances. In the embodiment according to Fig. 2 Thus, the desired opening pressures and closing pressures can be better adjusted.
  • the injector according to the invention thus enables both for the first nozzle needle 2 and for the second nozzle needle 3 an active needle closing, which is supported by the delayed control valve 38 in the control chamber 38.
  • the first nozzle needle 2 can thus be opened at a comparatively low opening pressure, which allows reduced combustion noise.
  • the closing of the first nozzle needle 2 can already be carried out at relatively high pressures, which reduces the formation of soot.
  • the opening movement of the second nozzle needle 3 can be braked, thereby reducing the risk of bouncing of the second nozzle needle 3 when opening.
  • a jump in quantity when opening the second nozzle needle 3 is thereby reduced.
  • the control pressure in the control chamber 38 also reduces the risk of bouncing for the closing nozzle needles 2, 3.
  • the throttling of the control line 39 can be matched to the other parameters that at a predetermined opening time of the first nozzle needle 2 and / or the second nozzle needle 3, the control pressure in the control chamber 38, the injection pressure in the nozzle chamber 11 and thus in the communicating connected other rooms, such as annulus 17, so far exceeds that prevail at the first nozzle needle 2 and the first needle assembly 10, the closing forces.
  • the first nozzle needle 2 is automatically closed.
  • This automatic closing of the first nozzle needle 2 then interrupts the fuel supply to at least one first injection hole 5 and at least one second injection hole 15. Forcibly then falls in the opening direction effective pressure at the second pressure stage 20, so that the second nozzle needle 3 at the latest closes.
  • the second nozzle needle 2 closes earlier accordingly.
  • those disposed within the first sealing seat 18 are also in the opening direction effective areas decoupled from the injection pressure, so that virtually a pressure equilibrium between the nozzle chamber 11 and the control chamber 38 is present.
  • the closing forces so that the nozzle needles remain 2.3 closed.
  • This embodiment thus defines a maximum full load quantity and regulates the fuel supply automatically to avoid damage to the internal combustion engine. If, as in the embodiment according to Fig. 1 the return line 43 is provided, this can be taken into account in the realization of the automatic closing operation in a corresponding manner.

Landscapes

  • 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 (9)

  1. Injecteur de moteur à combustion interne, notamment de véhicule automobile, comprenant :
    - une première aiguille d'injecteur (2) en forme d'aiguille creuse, commandant au moins un premier orifice d'injection (5) pour injecter du carburant,
    - une seconde aiguille d'injecteur (3) coaxiale à la première aiguille d'injecteur (2), commandant l'injection de carburant par au moins un second orifice d'injection (15),
    - une chambre de buse (11) reliée par une conduite d'alimentation en carburant (27) à une source de haute pression (28),
    - la première aiguille d'injecteur (2) ou une première combinaison d'aiguille (10) comprenant la première aiguille d'injecteur (2) comporte au moins un premier épaulement de pression (12) installé dans la chambre de buse (11) ou dans une chambre (17) communiquant avec la chambre de buse (11) pour y être soumis à la pression d'injection qui induit une force d'ouverture agissant sur la première aiguille d'injecteur (2) ou sur la première combinaison d'aiguille (10) dans le sens de l'ouverture (13),
    - une chambre de commande (38) reliant la conduite de commande (39) à la source de haute pression (28),
    - la première aiguille d'injecteur (2) ou la première combinaison d'aiguille (10) a une première surface de commande (41) dans la chambre de commande (38) pour être exposée à la pression de commande qui induit une force de fermeture agissant au niveau de la première aiguille d'injecteur (2) ou de la première combinaison d'aiguille (10) dans le sens de fermeture (7),
    - la seconde aiguille d'injecteur (3) ou une seconde combinaison d'aiguille (16) comprenant la seconde aiguille d'injecteur (3) comporte au moins un second épaulement de pression (20) dans la chambre (17) communiquant avec la chambre de buse (11) lorsque la première aiguille d'injecteur (2) est ouverte, pour recevoir la pression d'injection induisant dans la seconde aiguille d'injecteur (3) ou dans une seconde combinaison d'aiguille (16), une force d'ouverture agissant dans le sens de l'ouverture (13),
    - la seconde aiguille d'injecteur (3) ou la seconde combinaison d'aiguille (16) comporte une seconde surface de commande (42) dans la chambre de commande (38) pour recevoir la pression de commande qui induit une force de fermeture agissant dans le sens de la fermeture (7), dans la seconde aiguille d'injecteur (3) ou dans la seconde combinaison d'aiguille (16),
    - la conduite de commande (39) étant étranglée plus fortement que la conduite d'alimentation en carburant (27),
    caractérisé en ce que
    l'étranglement de la conduite de commande (39) est choisi pour que pour une durée d'ouverture prédéfinie de la première aiguille d'injecteur (2), la pression de commande dans la chambre de commande (38) dépasse la pression d'injection dans la chambre de buse (11) de façon que les forces de fermeture dominent au niveau de la première aiguille d'injecteur (2) ou la première combinaison d'aiguille (10).
  2. Injecteur selon la revendication 1,
    caractérisé en ce que
    la conduite de commande (39) communique avec la conduite d'alimentation en carburant (27) et elle est reliée par la conduite d'alimentation en carburant (27) à la source de haute pression (28).
  3. Injecteur selon la revendication 1 ou 2,
    caractérisé par
    un premier ressort de rappel (8) qui agit sur la première aiguille d'injecteur (2) ou la première combinaison d'aiguille (10) en induisant une force de fermeture agissant dans le sens de la fermeture (7) et ce ressort est logé dans une chambre de ressort (9),
    - la chambre de ressort (9) forme soit la chambre de commande (38) soit est distincte de la chambre de commande (38) en étant pratiquement étanche par rapport à celle-ci.
  4. Injecteur selon l'une des revendications 1 à 3,
    caractérisé en ce que
    la chambre de commande (38) est reliée par une conduite de retour (43) à un système de retour (36) pratiquement sans pression,
    la conduite de retour (43) est étranglée plus fortement que la conduite de commande (39).
  5. Injecteur selon la revendication 4,
    caractérisé en ce que
    la première aiguille d'injecteur (2) ou la première combinaison d'aiguille (10) commande un orifice (45) par lequel la conduite de retour (43) débouche dans la chambre de commande (38), en fonction de la course de la première aiguille d'injecteur (2) pour que cet orifice (45) soit plus ou moins fermé lorsque la première aiguille d'injecteur (2) est ouverte.
  6. Injecteur selon l'une des revendications 1 à 5,
    caractérisé en ce que
    - un second ressort de rappel (25) agit sur la seconde aiguille d'injecteur (3) ou la seconde combinaison d'aiguille (16) et induit une force de fermeture agissant dans le sens de la fermeture (7) et ce ressort est logé dans une chambre à ressort (26),
    - la chambre à ressort (26) forme soit la chambre de commande (38), soit est distincte de celle-ci en étant fermée de manière étanche par rapport à celle-ci.
  7. Injecteur selon l'une des revendications 1 à 6,
    caractérisé par
    un moyen de couplage d'entraînement (52) prévu entre la première aiguille d'injecteur (2) ou la première combinaison d'aiguille (10) et une seconde aiguille d'injecteur (3) ou une seconde combinaison d'aiguille (16), de façon que la première aiguille d'injecteur (2) ou la première combinaison d'aiguille (10) entraîne la seconde aiguille d'injecteur (3) ou la seconde combinaison d'aiguille (16) lors de la fermeture.
  8. Injecteur selon l'une des revendications 1 à 7,
    caractérisé en ce que
    la conduite d'alimentation en carburant (27) est reliée à la source de haute pression (28) par une soupape de dosage (31).
  9. Injecteur selon la revendication 8,
    caractérisé en ce que
    la soupape de dosage (31) est à commande hydraulique et elle est actionnée par une soupape de commutation (32).
EP04762760A 2003-11-28 2004-09-07 Injecteur Not-in-force EP1778967B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10355806A DE10355806A1 (de) 2003-11-28 2003-11-28 Einspritzdüse
PCT/DE2004/001977 WO2005054660A1 (fr) 2003-11-28 2004-09-07 Injecteur

Publications (2)

Publication Number Publication Date
EP1778967A1 EP1778967A1 (fr) 2007-05-02
EP1778967B1 true EP1778967B1 (fr) 2008-02-20

Family

ID=34609386

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04762760A Not-in-force EP1778967B1 (fr) 2003-11-28 2004-09-07 Injecteur

Country Status (4)

Country Link
EP (1) EP1778967B1 (fr)
AT (1) ATE386879T1 (fr)
DE (2) DE10355806A1 (fr)
WO (1) WO2005054660A1 (fr)

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10205970A1 (de) * 2002-02-14 2003-09-04 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
DE10221384A1 (de) * 2002-05-14 2003-11-27 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine
DE10312738B4 (de) * 2003-03-21 2005-02-24 Siemens Ag Einspritzventil mit hydraulisch betätigter Nadel und Hohlnadel und Verfahren zum Steuern einer Einspritzung

Also Published As

Publication number Publication date
EP1778967A1 (fr) 2007-05-02
DE10355806A1 (de) 2005-06-23
ATE386879T1 (de) 2008-03-15
DE502004006282D1 (de) 2008-04-03
WO2005054660A1 (fr) 2005-06-16

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