EP1778967A1 - Einspritzdüse - Google Patents
EinspritzdüseInfo
- Publication number
- EP1778967A1 EP1778967A1 EP04762760A EP04762760A EP1778967A1 EP 1778967 A1 EP1778967 A1 EP 1778967A1 EP 04762760 A EP04762760 A EP 04762760A EP 04762760 A EP04762760 A EP 04762760A EP 1778967 A1 EP1778967 A1 EP 1778967A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- nozzle
- needle
- control
- nozzle needle
- chamber
- 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.)
- Granted
Links
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
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- 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
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- 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
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- 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
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- 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, with the features of the independent claim.
- Such an injection nozzle is known for example from DE 100 58 153 AI and contains in a nozzle body a first nozzle needle designed as a hollow needle, with which an injection of fuel through at least one first spray hole can be controlled.
- a second nozzle needle is arranged coaxially in the first nozzle needle, with which an injection of fuel through at least one second spray hole can be controlled.
- a nozzle chamber is formed in the nozzle body and can be connected to a high-pressure source via a fuel supply line.
- the first nozzle needle has at least one first pressure stage, which is arranged in the nozzle chamber or in a chamber communicating with the nozzle chamber and can be subjected to an injection pressure in the respective chamber. The injection pressure acting on the respective first pressure stage then introduces an opening force acting in the opening direction into the first nozzle needle.
- a first return spring is provided, which is on the first nozzle needle or on a first one which comprises the first nozzle needle
- This first return spring is arranged in a spring chamber that communicates with a relatively depressurized return system.
- the closing forces then predominate on the first nozzle needle or on the first needle assembly, so that the first nozzle needle is closed.
- the nozzle chamber is connected to the high pressure source.
- the injection pressure that then builds up in the nozzle chamber generates the opening forces at the first pressure stage, which the closing forces predominate and open the first nozzle needle.
- the first nozzle needle can be closed again by lowering the pressure in the nozzle chamber. Accordingly, the first nozzle needle is controlled directly by the injection pressure prevailing in the nozzle chamber.
- a servo device comprising a control chamber and a control piston which is mounted in a stroke-adjustable manner and 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 set in the control room.
- the second nozzle needle has at least one second pressure stage, which is arranged in a space that communicates with the nozzle chamber when the first nozzle needle is open, so that the injection pressure is then also applied to the second pressure stage in order to introduce 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 reduced 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 therefore not controlled directly by the injection pressure, but rather by the control pressure, which is fundamentally independent of the injection pressure. In this respect, the second nozzle needle is servo-controlled.
- the injection pressure required for opening is selected 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 likewise only be ended at a comparatively low injection pressure. Accordingly, the injection is carried out towards the end with a relatively low injection pressure, which leads to a deteriorated preparation in the respective combustion chamber and accordingly to higher soot emissions. Closing the first nozzle needle quickly at a comparatively high injection pressure could reduce the soot emissions.
- the injection nozzle according to the invention with the features of the independent claim has the advantage in comparison that on the one hand it opens at a comparatively low injection pressure during the opening process and on the other hand it closes at a relatively high injection pressure during the closing process.
- This contradictory behavior of the first nozzle needle is achieved in the invention with the aid of a control chamber which is connected to or separated from the high pressure source simultaneously with the nozzle chamber, the pressure build-up and the pressure reduction in the control chamber using a corresponding throttling relative to the nozzle chamber delayed.
- a first control surface assigned to the first nozzle needle is also arranged in this control chamber, such that the control pressure leads to an additional closing force in the first nozzle needle. Since the control pressure at
- the opening process is only delayed, i.e. builds up more slowly, and the rapidly increasing injection pressure in the nozzle area can introduce sufficiently large opening forces into the first nozzle needle very early on. Accordingly, the first nozzle needle opens at a relatively low injection pressure.
- the pressure in the control room continues to rise and - depending on the duration of the opening - the pressure level of the
- the operating principle in which the control pressure prevailing in the control room is used to increase the closing forces can also be referred to as active needle closing in the following.
- High-pressure source control line provided with the fuel supply line, so that the control line can be connected to the high-pressure source via the fuel supply line.
- the advantage of this design is that only a single valve is required to connect or disconnect the fuel supply line to 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, since when the first nozzle needle is open, a certain amount of air is passed through the at least one first spray hole
- the throttling of the control line is selected such that the control pressure in the control chamber exceeds the injection pressure in the nozzle chamber at a predetermined opening time of the control nozzle, in such a way that the closing forces at the first nozzle needle or at the first needle assembly predominate. In other words, after a predetermined opening time, the first one
- Nozzle needle automatically closes again, regardless of whether the fuel supply line is still connected to the high pressure source or not.
- a full load quantity for the injected fuel is thus limited by design measures, which increases the operational safety of the internal combustion engine.
- the control chamber can also be connected via a return line to a relatively depressurized return system, in which case the return line is throttled more than the control line. This measure ensures a permanent exchange of the fuel volume in the control room.
- the temperature level in the control room can be reduced by a targeted flow through the control room.
- a flushing of the control room is achieved at the same time.
- the control chamber can be relieved more quickly when the nozzle needle is closed via the return line, which enables smaller intervals between successive injection processes.
- a further development provides for a mouth opening of the return line arranged in the control chamber to be controlled as a function of the stroke of the first nozzle needle such that the mouth opening is more or less closed when the first nozzle needle is open. In this way, the control losses flowing off via the return line are minimized, which improves the hydraulic efficiency and increases it
- the second nozzle needle or a second needle assembly containing the second nozzle needle can have a second control surface, which is likewise arranged in the control chamber and can be acted upon therein by the control pressure acting in the closing direction.
- active needle closing can also be implemented for the second nozzle needle.
- the control pressure prevailing in the control chamber also increases the closing forces acting in the closing direction when the second nozzle needle is closing. Accordingly, the second nozzle needle can also be closed at a higher injection pressure.
- FIG. 2 shows a section of a longitudinal section as in FIG. 1, but in a different embodiment
- an injection nozzle 1 according to the invention comprises a first one
- Nozzle needle 2 as well as a second nozzle needle 3.
- the first nozzle needle 2 is mounted by means of a first needle guide 4 in a nozzle body (not shown in more detail) in a stroke-adjustable manner.
- the first nozzle needle 2 is used to control at least one first spray hole 5, which opens into an injection chamber 6, which is, for example, a mixture formation chamber or a combustion chamber of a cylinder of an internal combustion engine.
- the first nozzle needle 2 is usually part of a first needle assembly 10, which is used for the transfer of
- the individual components of the first needle assembly 10 can be loosely attached to one another in the stroke direction! ying. It is also possible for at least two components of the first needle assembly 10 to be attached to one another or to be manufactured 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 introduces opening forces into the first nozzle needle 2 or the first needle assembly 10 via this first pressure stage 12, which forces act in an opening direction 13 indicated by an arrow.
- the second nozzle needle 3 is coaxially supported 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 spray hole 15, which likewise opens into the spray chamber 6.
- first spray holes 5 and / or a plurality of second spray holes 15 are provided, which are preferably each arranged uniformly distributed in the circumferential direction along a ring.
- the second nozzle needle 3 is also usually part of a second one
- Needle dressing 16 the components of which form a stroke-adjustable unit which is used to transmit pressure forces.
- the individual components of the second needle assembly 16 can lie loosely against one another. It is also possible that at least two of the components of the second needle assembly 16 are attached to one another or are formed by an integrally produced one-piece component.
- the nozzle chamber 12 communicates with an annular chamber 17, which envelops the first nozzle needle 2 and leads to the spray holes 5, 15.
- the first nozzle needle 2 has a further first pressure stage 12 in this annular space 17.
- the second nozzle needle 3 moves into a second sealing seat 19, which is also in the annular space 17, but downstream of the at least one first spray hole 5 and upstream of the at least one second
- Spray hole 15 is arranged.
- the second nozzle needle 3 has at least one second pressure stage 20 in the annular space 17.
- the partial space 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.
- One at the second pressure stage 20 attacking pressure then introduces an opening force acting in the opening direction 13 into the second nozzle needle 3 or into the second needle assembly 16.
- 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 in that a second guide cross-sectional area 23 of the second needle guide 14 is larger is as a second seat cross-sectional area 24 of the second sealing seat 19.
- a second return spring 25 is provided, which is assigned to the second nozzle needle 3 or 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 spaces 9 and 26 are combined to form a common spring space 9, 26.
- the nozzle chamber 11 can be connected to a high-pressure source 28 via a fuel supply line 27.
- the high-pressure source 28 is formed here by a high-pressure line 29 which is provided jointly for a plurality of such injection nozzles 1, a so-called “common rail system”.
- the common high-pressure line 29 is fed by a high-pressure pump 30. It is also possible to have a separate high-pressure pump for each injection nozzle 1
- a metering valve 31 is arranged in the fuel supply line 27.
- the fuel supply line 27 can be opened and blocked with the aid of the metering valve 31.
- the metering valve 31 is designed as a hydraulically actuated valve
- the metering valve 31 contains a valve body 33 which, by means of pressure forces which act on opposing control surfaces, ver for opening and closing
- a pressure drop can be generated on one surface of the valve body 33 in the metering valve 31, which causes the valve body 33 to open, 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 on 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 contains a first control edge 34.
- the metering valve 31 can have a second control edge 35, via which the fuel supply line 27 can be connected to a return system 36.
- the two control edges 34, 35 are matched to one another such that when the first control edge 34 is opened, the second control edge 35 inevitably closes and vice versa.
- the return system 36 can, as here, contain a pressure holding 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. It is of crucial importance here that 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 are simultaneously connected to the high-pressure source 28 or can be separated therefrom.
- 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 faces away from the spray holes 5, 15, so that the control pressure acting thereon initiates closing forces into the first nozzle needle 2 or into the first needle assembly 10.
- the second nozzle needle 3 or the second needle assembly 16 is also equipped with a second control surface 42, which is also arranged in the control chamber 38.
- the second control surface 42 also faces away from the spray holes 5, 15, so that pressurization of the second control surface 42 in the control chamber 38 introduces closing forces into the second nozzle needle 3 or the second needle assembly 16.
- control chamber 38 is formed by the first spring chamber 9 or by the second spring chamber 26 or by the common spring chamber 9, 26.
- a further special feature in the embodiment according to FIG. 1 is also seen in the fact that the control chamber 38 is also connected to the return system 36 via a return line 43.
- the return line 43 is throttled more than the control line 39, which is achieved for example with a corresponding return throttle 44.
- a mouth opening 45, with which the return line 43 opens into the control chamber 38, is expediently positioned such that it can be controlled as a function of the stroke of the first nozzle needle 2.
- this orifice 45 is positioned such that the first nozzle needle 2 or the first needle assembly 10 covers the orifice 45 more or less at least when a maximum opening position of the first nozzle needle 2 is reached, so that the orifice 45 and thus the return line 43 in correspondingly more or less closed.
- the embodiment of the injector 1 shown in FIG. 1 works as follows:
- both nozzle needles 2, 3 are closed. Accordingly, the metering valve 31 and the solenoid valve 32 are closed.
- a relatively low high fuel 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 chamber 17.
- the injection pressure at the first pressure stages 12 reaches a comparatively low opening threshold, predominate in the the first nozzle needle 2 or in the first needle assembly 10 the opening forces and the first nozzle needle 2 lifts from the first sealing seat 18.
- the control chamber 38 communicates with the fuel supply line 27 via the control line 39, a control pressure also builds up in the control chamber 38. However, the pressure build-up is delayed in the control chamber 38 compared to the nozzle chamber 11, which is due to the targeted
- Throttling 40 of the control line 39 is brought about. Accordingly, the first nozzle needle 2 can lift off at the desired relatively low opening pressure and open the at least one first spray hole 5.
- control chamber 38 can continue to build up until it reaches the maximum value of the high pressure specified by high pressure source 28. Since additional surfaces communicate with the annular space 17 when the first nozzle needle 2 is opened, the design can be such that the first nozzle needle 2 remains open, even if the pressures in the nozzle space 11 and in the control space 38 are more or less balanced.
- the solenoid valve 32 is now closed again.
- the metering valve 31 also closes. This separates the fuel supply line 27 from the high-pressure source 28 and at the same time connects it to the return system 36, as a result of which the pressure in the
- Fuel supply line 27 can drop relatively quickly.
- the throttled control line 39 allows the pressure in the control chamber 38 to last longer, so that very high closing forces can now be introduced into the first nozzle needle 2 or into the first needle assembly 10 on the first control surface 41. These high closing forces generate a pulse-like acceleration of the first nozzle needle 2 in the latter
- the delayed pressure reduction in the control chamber 38 thus enables the inertial forces of the first nozzle needle 2 or the first needle assembly 10 to be overcome very dynamically, so that the first nozzle needle 2 can be set in motion very quickly. Accordingly, the first nozzle needle 2 closes at a pressure which is still present in the nozzle chamber 11 and which can be significantly above the previously 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 cannot open yet, because of that attacking closing forces and the second pressure stage 20 are coordinated accordingly.
- a correspondingly increased high pressure is first provided in the high pressure source 28.
- the solenoid valve 32 By opening the solenoid valve 32, the metering valve 31 is controlled 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 chamber 17.
- the first nozzle needle 2 is opened again.
- the injection pressure can then also build up at the second pressure stage 20.
- the second nozzle needle 3 can also lift off the second sealing seat 19, so that the desired fuel injection can take place through all the spray holes 5, 15.
- the opening movement of the second nozzle needle 3 or the second needle assembly 16 is braked by the pressure building up in the control chamber 38.
- the second control surface 42 is moved into the second control chamber 38, which is accompanied by a displacement of the hydraulic volume in the control chamber 38. Accordingly, there is a correspondingly rapid pressure rise in the control chamber 38, which slows down the opening movement of the second needle assembly 16. This is advantageous in the second nozzle needle 3, since in this way a jump in volume when opening the second nozzle needle 3 can be reduced.
- the braking effect due to the pressure build-up in the control chamber 38 also results in a corresponding manner in the first nozzle needle 2, although it does not have such a strong effect there, since the first nozzle needle 2 penetrates into the control chamber 38 considerably earlier at a significantly lower control pressure.
- the fuel supply line 27 Separates fuel supply line 27 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 chamber 17 can drop. Since the control pressure, which has meanwhile risen to a comparatively high value, is reduced only with a delay due to the throttling, very high closing forces can now occur in the control chamber 38 be introduced to the control surfaces 41 and 42. This results in a strong acceleration of the two nozzle needles 2, 3 or the needle groups 10, 16. Accordingly, the nozzle needles 2, 3 can be closed particularly early, that is to say even at a relatively high pressure in the nozzle chamber 11.
- the return line 43 makes it possible in the embodiment shown in FIG. 1 to additionally delay the pressure build-up in the control chamber 38. At the same time, this causes the control chamber 38 to be flushed. 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 opening 45 in the control chamber 38. Control losses can thus be reduced during fuel injection. At the same time, the injection pressure that can be achieved can be increased.
- the return line 43 is opened again, so that the pressure in the control chamber 38 can then decrease more quickly. This is particularly advantageous if there are only short time intervals between successive injection processes, for example in the case of multiple injections per work cycle in the respective cylinder.
- the injector 1 can do without the return line 43 in another embodiment.
- the control chamber 38 is then charged and relaxed exclusively via the control line 39.
- only the first control surface 41 is provided, which is the first
- Needle dressing 10 is assigned.
- the first needle assembly 10 here contains a control piston 46 which is mounted in the control chamber 38 so as to be stroke-adjustable.
- On this control piston 46 is supported on a side facing away from the first nozzle needle 2, a coupling sleeve 47, which is supported on its end facing away from the control piston 46 on a first spring plate 48.
- the first spring plate 48 is mounted in a stroke-adjustable manner in the first spring chamber 9 and absorbs the closing forces of the first return spring 8.
- the control room 38 is formed separately from the first control room 9. The same applies accordingly with regard to the second spring chamber 26, which is still combined here with the first spring chamber 9 to form a common spring chamber 9, 26.
- the second needle assembly 16 here comprises a coupling rod 49 which is supported on a second spring plate 51 by means of a plunger 50.
- the second spring plate 51 is mounted in a stroke-adjustable manner in the second spring chamber 46 and absorbs the closing forces of the second return spring 25.
- a driver coupling 52 is formed here between the first nozzle needle 2 or the first needle assembly 10 and the second nozzle needle 3 or the second needle assembly 16.
- This driver coupling 52 is designed in such a way that the first needle assembly 10 takes the second needle assembly 16 or at least its second nozzle needle 3 in the closing direction when the first nozzle needle 2 is closed. This is achieved, for example, in that the control piston 46 projects radially inward beyond an axial end face 53 of the second nozzle needle 3 facing away from the spray holes 5, 15. It can be expedient that in the closed position of both nozzle needles 2, 3 there is a slight axial play between the control piston 46 and the mentioned axial end face 53 of the second nozzle needle 3.
- the control piston 46 When the first nozzle needle 2 is opened, the control piston 46 is moved into the control chamber 38 in the opening direction 13. When opening the second nozzle needle 3, the control piston 46 or the driver coupling 52 can form an opening stop for the second nozzle needle 3. This means that when the second nozzle needle 3 is fully open, it comes to rest axially on the control piston 46. If the nozzle needles 2, 3 are now to be closed quickly, the pressure drop in the nozzle chamber 11 in connection with the control pressure which is reduced only in the control chamber 38 leads to a strong acceleration of the control piston 46 and thus of the entire first piston
- connection 54 to the return system 36 is provided between the nozzle chamber 11 and the control chamber 38 in order to discharge leaks through the first needle guide 4 and / or through a guide of the control piston 46. On in this way interactions with the control piston 46 can be avoided.
- the separate arrangement of the control room 38 makes it possible to manufacture the volume of the control room 38 with increased precision.
- the volume of the control chamber 38 in the embodiment according to FIG. 2 no longer depends on the volume of the return springs 8 and 25, which can vary depending on the manufacturing tolerances. In the embodiment according to FIG. 2, the desired opening pressures and closing pressures can thus be set better.
- the injection nozzle according to the invention thus enables an active needle closing both for the first nozzle needle 2 and for the second nozzle needle 3
- Control room 38 delayed reduced control pressure is supported.
- the first nozzle needle 2 can thus be opened at a comparatively low opening pressure, which enables reduced combustion noises.
- the first nozzle needle 2 can already be closed at relatively high pressures, which reduces soot formation.
- Nozzle needle 3 are braked, which reduces the risk of bouncing the second nozzle needle 3 when opening. This also reduces a jump in volume when opening the second nozzle needle 3. Furthermore, the control pressure in the control chamber 38, which decreases comparatively quickly when the nozzle needles 2, 3 are closed, likewise 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 such that, for 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 spaces, such as annular space 17, so far that the closing forces at the first nozzle needle 2 or at the first needle assembly 10 predominate.
- the first nozzle needle 2 is closed automatically. This automatic closing of the first nozzle needle 2 then interrupts the fuel supply to the at least one first spray hole 5 and to the at least one second spray hole 15.
- the pressure acting in the opening direction then also drops at the second pressure stage 20, so that the second nozzle needle 3 also then at the latest closes.
- a driver coupling 52 is provided, the second nozzle needle 2 closes earlier accordingly.
- those arranged within the first sealing seat 18 are also in the opening direction effective areas decoupled from the injection pressure, so that there is a pressure equilibrium between the nozzle chamber 11 and the control chamber 38.
- the closing forces predominate due to the first return spring 8, so that the nozzle needles 2, 3 remain closed.
- This embodiment thus defines a maximum full load quantity and regulates the fuel supply automatically in order 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 a corresponding manner when realizing the automatic closing process.
- Valve body first control edge second control edge
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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)
Description
Claims
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 (de) | 2003-11-28 | 2004-09-07 | Einspritzdüse |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1778967A1 true EP1778967A1 (de) | 2007-05-02 |
EP1778967B1 EP1778967B1 (de) | 2008-02-20 |
Family
ID=34609386
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP04762760A Not-in-force EP1778967B1 (de) | 2003-11-28 | 2004-09-07 | Einspritzdüse |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP1778967B1 (de) |
AT (1) | ATE386879T1 (de) |
DE (2) | DE10355806A1 (de) |
WO (1) | WO2005054660A1 (de) |
Family Cites Families (3)
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 |
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2003
- 2003-11-28 DE DE10355806A patent/DE10355806A1/de not_active Withdrawn
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2004
- 2004-09-07 AT AT04762760T patent/ATE386879T1/de not_active IP Right Cessation
- 2004-09-07 EP EP04762760A patent/EP1778967B1/de not_active Not-in-force
- 2004-09-07 WO PCT/DE2004/001977 patent/WO2005054660A1/de active IP Right Grant
- 2004-09-07 DE DE502004006282T patent/DE502004006282D1/de active Active
Non-Patent Citations (1)
Title |
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See references of WO2005054660A1 * |
Also Published As
Publication number | Publication date |
---|---|
EP1778967B1 (de) | 2008-02-20 |
DE10355806A1 (de) | 2005-06-23 |
ATE386879T1 (de) | 2008-03-15 |
DE502004006282D1 (de) | 2008-04-03 |
WO2005054660A1 (de) | 2005-06-16 |
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