EP1171708B1 - Einspritzdüse - Google Patents
Einspritzdüse Download PDFInfo
- Publication number
- EP1171708B1 EP1171708B1 EP01913560A EP01913560A EP1171708B1 EP 1171708 B1 EP1171708 B1 EP 1171708B1 EP 01913560 A EP01913560 A EP 01913560A EP 01913560 A EP01913560 A EP 01913560A EP 1171708 B1 EP1171708 B1 EP 1171708B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- injection nozzle
- nozzle according
- injection
- control valve
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
Images
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
- F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
- F02M61/042—The valves being provided with fuel passages
- F02M61/045—The valves being provided with fuel 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
- F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
- F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
- F02M47/025—Hydraulically actuated valves draining the chamber to release the closing pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
- F02M47/06—Other fuel injectors peculiar thereto
-
- 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
- F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
- F02M61/042—The valves being provided with fuel passages
-
- 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
- F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
- F02M61/08—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series the valves opening in direction of fuel flow
-
- 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
- F02M61/161—Means for adjusting injection-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
- 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
Definitions
- the invention relates to an injection nozzle with a nozzle body, a in this slidable nozzle needle and two groups of spray holes provided is.
- a nozzle body a in this slidable nozzle needle and two groups of spray holes provided is.
- the opening stroke of the nozzle needle is either just one group of the spray holes or both groups of spray holes used for injection. In this way you can have different Use injection cross sections, so that the fuel injection better to the respective operating conditions of the supplied from the injection system internal combustion engine can be adapted.
- the opening stroke of the nozzle needle In order to select the injection cross section in the desired manner, must the opening stroke of the nozzle needle to be controlled as precisely as possible. There are it meanwhile different solution approaches.
- One way of controlling the Opening stroke is the opening and closing of the nozzle needle directly caused by a piezo actuator. That way, just about any one can Intermediate position to be approached and held within the Nadelhubes.
- Another way to control the opening stroke is that the Opening the nozzle needle causing fuel pressure to control so that the desired opening stroke sets.
- the object of the invention is to provide a fuel injection nozzle, in the opening stroke of the nozzle needle with little effort and high reliability can be limited to a desired value.
- the task further consists in providing a fuel injector, at the spray cross-section can be selected independently of all other parameters can.
- DE 195 04 849 A1 is known in the an injection valve, which is a longitudinally movable valve member and a hydraulic Stop chamber comprises.
- the hydraulic stop chamber can via a Relieved control valve, so that depending on the position of the control valve, a longitudinal movement the valve member is enabled or blocked.
- the filling of the control room happens at high pressure from the common rail system.
- the control valve is designed as a solenoid valve and can also several injectors simultaneously drive.
- An injection nozzle with the features of claim 1 has the advantage that the opening stroke of the nozzle needle with little effort in the desired manner can be limited. If only a small opening stroke is desired, the control valve is closed, so that the outflow in the abutment chamber existing fluid is prevented. That the exit of the stop chamber controlling control valve can be operated with low energy, because it is not immediately acted upon by the high pressure, the opening causes the nozzle needle. Furthermore, the control valve during the injection breaks the injection nozzle are actuated, ie between two consecutive Injection cycles, so that the switching operations in phases with low Pressurization done and the switching phases no high requirements with regard to the time.
- FIG. 1 shows an injection nozzle which has a nozzle body 10. This is at its combustion chamber end with two groups of spray holes 12, 14 through which fuel can be injected through a supply bore 16 and a pressure chamber 18 is supplied.
- a nozzle needle 20 is slidably disposed in the nozzle body 10. These is acted upon by a return spring 22 in a position in which the injection holes 12, 14 are closed. By applying a sufficiently high fuel pressure to the pressure chamber 18, the nozzle needle 20 against the effect the compression spring 22 are shifted upward with respect to Figure 1, so that depending on the size of this opening stroke either only the injection holes 14 or the spray holes 12 are released. Because the nozzle needle 20 is moved into the interior of the nozzle body 10 for opening the injection holes, This type of injector is referred to as an internal opening injector.
- the nozzle needle 20 is provided with a piston 24 which is displaceable in a Stop chamber 26 is arranged, which is formed in the nozzle body 10.
- a piston 24 which is displaceable in a Stop chamber 26 is arranged, which is formed in the nozzle body 10.
- Stop chamber 26 is arranged, which is formed in the nozzle body 10.
- the piston 24 divides the stop chamber 26 into two sections, wherein the with respect to the piston of the spray holes remote from the stop chamber 26 is provided with an output 28. Between the piston 24th and the nozzle needle 20, a stop plate 29 is arranged, which is the maximum Opening stroke of the nozzle needle limited.
- the output 28 leads to a valve chamber 30 (see also FIG. 3) of a control valve 31.
- a valve ball 32 is arranged, of a Valve spring 34 is acted upon against a valve seat 36.
- actuating part On the side facing away from the valve spring 34 side of the valve ball 32 engages this an actuating part, which consists of a control piston 38 and an extension 40th consists.
- the adjusting piston 38 is arranged in a control chamber 42, whose from the Valve chamber 30 remote portion is connected to a control line 44 and the valve chamber 30 facing portion with a return line 46 is connected.
- the return line 46 leads into a leakage collecting space 48 in the nozzle body 10. With the leakage collecting chamber 48 is also a leakage-discharge line 49 connected between the stop plate 29 and the piston 24 opens.
- the injection nozzle described works in the following way: before the start of injection is determined depending on external parameters, whether a complete Opening stroke of the nozzle needle is required, so that the two groups of Spray holes 12, 14 are opened, or if only a Detailö Stamm required is, so that only the injection holes 14 are released. If a complete Opening stroke is required by applying a suitable pressure to the Control line 44, for example, a fuel prefeed, the actuating piston shifted towards the valve chamber 30, so that the valve ball 32 against the action of the valve spring 34 by means of the extension 40 from the valve seat 36th is lifted. Thus, the output 28 from the abutment chamber 26 to Return line 46 opened.
- the nozzle needle 20 by applying a suitable fuel pressure is opened to the supply bore 16 can in the abutment chamber 26 above the piston 24 existing fluid at the Valve ball 32 escape from the stop chamber 26 over.
- the Nozzle needle 20 are fully opened, since the piston 24 is almost free in the stop chamber 26 can move, with the maximum opening stroke is predetermined by the stop plate 29.
- FIG. 5 shows how the control valves of all injection nozzles of an injection system can be switched together.
- the control lines become common controlled by an actuator 50, the control lines either with a Pre-feed line 52 or a leakage collecting space can connect. If the control lines 44 are connected to the prefeed line, the Control piston of the individual control valves with fuel under supply pressure applied. This causes the control valve is open, so that the Output 28 of the stop chamber 26 connected to the leakage collecting space is and a complete opening of the nozzle needles of the injectors is possible. In contrast, when the control lines 44 connected to the leakage collecting space are, the control valves 31 are closed, so that a limitation of the opening stroke the nozzle needles is made.
- a special feature of this stroke limitation is that the opening and Closing the control valve in the injection breaks and thus in the unloaded Condition of the valve is done; the forces to operate the control valve are so tiny. Due to the immediate proximity of the control valve to the stop chamber results in a small volume and thus a stiff characteristic of the enclosed Volume formed hydraulic spring. Since the control valve with Fuel can be actuated, which must not be under injection pressure, but only under low pressure, for example pre-feed pressure, results low energy consumption and a simplified structure, as no high-pressure lines required are. Furthermore, there are no problems with pressure oscillations. As an alternative to using the prefeed pressure of the fuel, the low pressure be provided by a separate supply system or by a leakage current of the high pressure system.
- FIG. 2 shows an injection nozzle according to a second embodiment.
- the injection nozzle according to the second embodiment has an outwardly opening injection nozzle, So an injector, in which the nozzle needle 20 to open after is adjusted outside to the combustion chamber. For this reason, the output is 28 arranged in the portion of the stop chamber 26, with respect to the piston 24 faces the spray holes.
- FIG. 4 shows a variant not according to the invention to the control valve shown in FIG.
- a piezo-actuator 39 is used here, which together forms the Eetuschiststeil for the valve ball 32 with the extension.
- the piezo actuator 39 can directly by changing the length of the extension 40 so the valve spring 34th move that the valve ball 32 is lifted from the valve seat 36; instead of the control line 44 are used (not shown) cable to the necessary Apply voltage to the piezo actuator.
- FIG. 6 schematically shows the control valve 31 according to the variant of FIG. 4 shown.
- the piezo actuator 39 can by connecting the valve ball 32, the connection the output 28 to the return line 46 open or close to this Way to achieve a variable stroke of the nozzle needle 20 of the injection nozzle.
- FIGS. 7a and 7b show a first variant of the second embodiment, So an outside opening injector. So far in this variant components be used, which are known from the preceding figures The same reference numerals are used, and it is to the above explanations directed.
- valve seat 37 which is the first valve seat on the other Side of the valve cone 32 'opposite.
- the control valve When the adjusting piston 38 is acted upon by low pressure, preferably is less than 10 bar, the control valve is opened and the valve cone from the first Valve seat lifted and brought into contact with the second valve seat 37. Thereby is the connection from the stop chamber via the output 28 to the Return line open, so that the opening stroke of the nozzle needle from the piston 24 displaced amount of fluid can flow out of the stop chamber 26.
- the second valve seat is used in case of a possible pressure build-up in the control valve to prevent that acts on the valve cone, a closing force, it against the first valve seat is acted upon and the control valve closes.
- a Pressure build-up could be due to fluid backflow when opening the nozzle needle acting flow resistance can be caused.
- a Pressure build-up would produce a closing force, which depends on the pressure difference between the pressure acting on the actuator piston and the pressure the side facing away from the actuating piston of the valve cone and the other is determined by the cross-sectional area of the actuating piston.
- FIGS. 7c and 7d a variant of the control valve shown in FIG. 7b is shown shown.
- the valve cone 32 ' has a valve seat 36 associated valve surface 60, which is shaped as a ball portion with a radius R.
- the radius R is chosen comparatively large. With a diameter of the valve seat of 2 mm, the radius R is on the order of 3 mm.
- the valve seat is designed in that the cone formed by it has an opening angle W1 of 70 ° with respect to the central axis of the valve cone has.
- the extension 40 of the valve cone 32 ' is provided with a projection 62 which in the guide bore 64 for the valve cone 32 'is present. That way is one formed double guide for the valve cone, so that a radial displacement the valve cone, as they come from due to a from the Abêtbohrung Pressure wave and / or caused by radial forces of the valve spring 34 could, certainly prevented. This ensures the correct position of the valve cone at the valve seat, which increases the reliability of the sealing effect.
- FIGS. 7e and 7f show a further variant of the control valve shown in FIG. 7b shown.
- the valve cone 32 ' has a valve seat 36 associated Valve surface 60, which is formed here of two frustoconical surfaces 66, 68. Of the Valve seat is formed so that the cone formed by it has an opening angle W1 of 70 ° with respect to the central axis of the valve cone.
- the two frustoconical surfaces 66 and 68 make an angle with the central axis of the cone W2 or W3, which is in the order of 80 ° or 45 °.
- the double cone valve surface leads to a pure line contact and thus a high surface pressure, which positively affects the sealing effect. Furthermore the biconve valve surface is better and better compared to the ball valve surface reproducible to manufacture, which in turn ensures the reliability of the sealing effect increases and also leads to a reduction in costs.
- FIGS. 7g and 7h show a further variant of the one shown in FIG. 7b Control valve shown.
- the valve cone 32 ' has no extension here on, so that no double guide is formed for the valve cone.
- the valve surface 60 of the valve cone 32 ' is made two frustoconical surfaces 66, 68.
- the included with the central axis opening angle W1 of the valve seat is here 29.5 °, while the angles W2 and W3 of the frusto-conical surfaces 66, 68 of the valve surface 60 are 30.5 ° and 22.5 °, respectively.
- the area of the valve seat with the central axis includes, a radial pressing out of the valve cone from its valve seat, this could be caused by a side-acting pressure wave from the diversion bore or a radial component of the force of the valve spring, reliably avoided.
- the second, production-technically complex double piston guide superfluous, the production cost of the Valve seat remains the same.
- the acute-angled double-cone valve surface contributes to the safe Caulking at.
- FIGS. 8a and 8b show a second variant of the second embodiment shown.
- the same reference numerals are used, and reference is made to the above explanations.
- valve ball 32 used by the actuator piston 38 via the extension 40th lifted from the first valve seat 36 and pressed against the second valve seat 37 can be.
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)
Description
- Figur 1 in einer Schnittansicht eine Einspritzdüse gemäß einer ersten Ausführungsform der Erfindung;
- Figur 2 in einer Schnittansicht eine zweite Ausführungsform der Erfindung;
- Figur 3 in einer vergrößerten Schnittansicht das Steuerventil, das bei den in den Figuren 1 und 2 gezeigten Einspritzdüsen verwendet wird;
- Figur 3a in einer vergrößerten Schnittansicht eine Ausführungsvariante zu dem in Figur 3 gezeigten Steuerventil;
- Figur 4 in einer vergrößerten Schnittansicht eine alternative nicht erfindungsgemäße Ausgestaltung des Steuerventils;
- Figur 5 in einer schematischen Ansicht eine hydraulische Schaltung, wie sie bei dem Steuerventil gemäß Figur 3 verwendet werden kann; und
- Figur 6 in einer schematischen Ansicht die hydraulische Schaltung entsprechend der Variante des Steuerventils von Figur 4;
- Figur 7a eine Einspritzdüse gemäß einer ersten Variante der zweiten Ausführungsform;
- Figur 7b in vergrößertem Maßstab schematisch das bei der Einspritzdüse von Figur 7a verwendete Steuerventil;
- Figur 7c in vergrößertem Maßstab schematisch einen Ausschnitt einer Variante des in Figur 7b gezeigten Steuerventils;
- Figur 7d den Ausschnitt d von Figur 7c in wiederum vergrößertem Maßstab;
- Figur 7e in vergrößertem Maßstab schematisch einen Ausschnitt einer weiteren Variante des in Figur 7b gezeigten Steuerventils;
- Figur 7f den Ausschnitt f von Figur 7e in wiederum vergrößertem Maßstab;
- Figur 7g in vergrößertem Maßstab schematisch einen Ausschnitt einer weiteren Variante des in Figur 7b gezeigten Steuerventils;
- Figur 7h den Ausschnitt h von Figur 7g in wiederum vergrößertem Maßstab;
- Figur 8a eine Einspritzdüse gemäß einer zweiten Variante der zweiten Ausführungsform; und
- Figur 8b in vergrößertem Maßstab schematisch das bei der Einspritzdüse von Figur 8a verwendete Steuerventil.
Claims (16)
- Einspritzdüse mit einem Düsenkörper (10), einer in diesem verschiebbaren Düsennadel (20), zwei Gruppen von Spritzlöchern (12,14), die in Abhängigkeit von einem Öffnungshub der Düsennadel freigegeben werden, einem Kolben (24), der mit der Düsennadel (20) verbunden ist, einer Anschlagkammer (26), in der der Kolben angeordnet ist und die mit einem Ausgang (28) versehen ist, und einem Steuerventil (31), das den Ausgang der Anschlagkammer öffnen und schließen kann, wodurch der Hub des Kolbens in der Anschlagkammer (26) und damit der Öffnungshub der Düsennadel (20) selektiv begrenzt werden kann, dadurch gekennzeichnet, daß die Anschlagkammer (26) bei geschlossenem Steuerventil (31) als hydraulische Feder dient, während der Kraftstoff bei geöffnetem Steuerventil (31) aus der Anschlagkammer (26) über den Ausgang (28) entweichen kann, wobei das Steuerventil (31) ein Ventilelement (30) aufweist, das von einer Ventilfeder (34) gegen einen Ventilsitz (36) beaufschlagt wird und durch einen Stellkolben (38), der mit unter einem Niedrigdruck stehenden Kraftstoff beaufschlagbar ist, vom Ventilsitz (36) abgehoben werden kann.
- Einspritzdüse nach Anspruch 1, dadurch gekennzeichnet, daß das Steuerventil ein Magnetventil ist.
- Einspritzdüse nach Anspruch 1, dadurch gekennzeichnet, daß das Ventilelement eine Ventilkugel (32) ist.
- Einspritzdüse nach Anspruch 1, dadurch gekennzeichnet, daß das Ventilelement ein Ventilkonus (32') ist.
- Einspritzdüse nach Anspruch 4, dadurch gekennzeichnet, daß der Ventilkonus eine Ventilfläche (60) aufweist, die als Kugelabschnitt ausgebildet ist.
- Einspritzdüse nach Anspruch 4, dadurch gekennzeichnet, daß der Ventilkonus eine Ventilfläche (60) aufweist, die durch zwei aneinander angrenzende Kegelstumpfflächen (66, 68) ausgebildet ist.
- Einspritzdüse nach Anspruch 6, dadurch gekennzeichnet, daß der Öffnungswinkel (W2) der näher am Fortsatz (46) liegenden Kegelstumpffläche kleiner ist als der Öffnungswinkel (W1) des Ventilsitzes (36).
- Einspritzdüse nach Anspruch 7, dadurch gekennzeichnet, daß der Winkel W1 29,5° beträgt und die Winkel W2 30,5° beträgt.
- Einspritzdüse nach Anspruch 6, dadurch gekennzeichnet, daß die Öffnungswinkel (W2, W3) der beiden Kegelstumpfflächen (66, 68) sich vom Öffnungswinkel (W1) des Ventilsitzes unterscheiden.
- Einspritzdüsen nach Anspruch 9, dadurch gekennzeichnet, daß die Öffnungswinkel (W2, W3) der beiden Kegelstumpfflächen 80° bzw. 45° betragen und der Öffnungswinkel (W1) des Ventilsitzes etwa 70° beträgt.
- Einspritzdüse nach Anspruch 1, dadurch gekennzeichnet, daß der Niederdruck gleich einem Kraftstoff-Vorförderdruck ist.
- Einspritzdüse nach Anspruch 1, dadurch gekennzeichnet, daß der Niederdruck von einer separaten Versorgung bereitgestellt wird.
- Einspritzdüse nach Anspruch 1, dadurch gekennzeichnet, daß der Niederdruck von einer Leckage des Kraftstoff-Hochdrucksystems stammt.
- Einspritzdüse nach einem der Ansprüche 1 bis 13, dadurch gekennzeichnet, daß ein zweiter Ventilsitz (37) vorgesehen ist, an dem das Ventilelement (32; 32') bei geöffnetem Steuerventil anliegen kann.
- Einspritzdüse nach einem der Ansprüche 1 bis 14, dadurch gekennzeichnet, daß die Düsennadel (20) mit den beiden Gruppen von Spritzlöchern (12, 14) versehen ist.
- Einspritzdüse nach einem der Ansprüche 1 bis 14, dadurch gekennzeichnet, daß der Düsenkörper (10) mit den beiden Gruppen von Spritzlöchern (12, 14) versehen ist.
Applications Claiming Priority (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10005373 | 2000-02-07 | ||
DE10005373 | 2000-02-07 | ||
DE10100512A DE10100512A1 (de) | 2000-02-07 | 2001-01-08 | Einspritzdüse |
DE10100512 | 2001-01-08 | ||
PCT/DE2001/000394 WO2001059293A1 (de) | 2000-02-07 | 2001-02-02 | Einspritzdüse |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1171708A1 EP1171708A1 (de) | 2002-01-16 |
EP1171708B1 true EP1171708B1 (de) | 2005-09-14 |
Family
ID=26004230
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP01913560A Expired - Lifetime EP1171708B1 (de) | 2000-02-07 | 2001-02-02 | Einspritzdüse |
Country Status (6)
Country | Link |
---|---|
US (1) | US6691935B1 (de) |
EP (1) | EP1171708B1 (de) |
JP (1) | JP2003522882A (de) |
CZ (1) | CZ296968B6 (de) |
DE (1) | DE50107401D1 (de) |
WO (1) | WO2001059293A1 (de) |
Families Citing this family (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102004061800A1 (de) * | 2004-12-22 | 2006-07-06 | Robert Bosch Gmbh | Injektor eines Kraftstoffeinspritzsystems einer Brennkraftmaschine |
JP4412241B2 (ja) * | 2005-06-15 | 2010-02-10 | 株式会社デンソー | 燃料噴射弁 |
DE102006026877A1 (de) * | 2006-06-09 | 2007-12-13 | Robert Bosch Gmbh | Kraftstoff-Einspritzvorrichtung für eine Brennkraftmaschine |
KR101043745B1 (ko) | 2006-12-15 | 2011-06-22 | 맨 디젤 앤드 터보 필리얼 아프 맨 디젤 앤드 터보 에스이 티스크랜드 | 내연기관용 연료분사기 |
WO2008071187A1 (en) * | 2006-12-15 | 2008-06-19 | Man Diesel A/S | A fuel injector for an internal combustion engine |
DK2239451T3 (da) * | 2009-03-30 | 2011-10-10 | Waertsilae Switzerland Ltd | Brændstofindsprøjtningsindretning til interne forbrændingsmotorer |
KR101328757B1 (ko) * | 2009-10-28 | 2013-11-13 | 현대중공업 주식회사 | 디젤 엔진용 2단 연료 분사밸브 |
DE102010063379B4 (de) * | 2010-12-17 | 2017-04-06 | Robert Bosch Gmbh | Expansionsmaschine und Verfahren zur Abwärmenutzung von Verbrennungskraftmaschinen |
DK178656B1 (en) * | 2015-03-20 | 2016-10-17 | Man Diesel & Turbo Filial Af Man Diesel & Turbo Se Tyskland | Fuel valve for injecting a low flashpoint fuel into a combustion chamber of a large self-igniting turbocharged two-stroke internal combustion engine |
KR101638815B1 (ko) * | 2016-01-07 | 2016-07-25 | 한빛정공(주) | 4 행정용 인젝션 밸브 |
US10544771B2 (en) * | 2017-06-14 | 2020-01-28 | Caterpillar Inc. | Fuel injector body with counterbore insert |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4640252A (en) * | 1984-01-28 | 1987-02-03 | Mazda Motor Corporation | Fuel injection system for diesel engine |
AT407428B (de) * | 1989-04-12 | 2001-03-26 | Avl Verbrennungskraft Messtech | Hydraulisch betätigbares ventil mit steuerbarem hub |
DE19504849A1 (de) * | 1995-02-15 | 1996-08-22 | Bosch Gmbh Robert | Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen |
US5682858A (en) * | 1996-10-22 | 1997-11-04 | Caterpillar Inc. | Hydraulically-actuated fuel injector with pressure spike relief valve |
JPH10281038A (ja) | 1997-04-01 | 1998-10-20 | Denso Corp | 燃料噴射弁 |
DE19739905A1 (de) * | 1997-09-11 | 1999-03-18 | Bosch Gmbh Robert | Kraftstoffeinspritzventil |
-
2001
- 2001-02-02 JP JP2001558604A patent/JP2003522882A/ja active Pending
- 2001-02-02 EP EP01913560A patent/EP1171708B1/de not_active Expired - Lifetime
- 2001-02-02 DE DE50107401T patent/DE50107401D1/de not_active Expired - Fee Related
- 2001-02-02 CZ CZ20013596A patent/CZ296968B6/cs not_active IP Right Cessation
- 2001-02-02 US US09/958,375 patent/US6691935B1/en not_active Expired - Fee Related
- 2001-02-02 WO PCT/DE2001/000394 patent/WO2001059293A1/de active IP Right Grant
Also Published As
Publication number | Publication date |
---|---|
DE50107401D1 (de) | 2005-10-20 |
JP2003522882A (ja) | 2003-07-29 |
CZ296968B6 (cs) | 2006-08-16 |
US6691935B1 (en) | 2004-02-17 |
CZ20013596A3 (cs) | 2003-02-12 |
EP1171708A1 (de) | 2002-01-16 |
WO2001059293A1 (de) | 2001-08-16 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
DE19946827C1 (de) | Ventil zum Steuern von Flüssigkeiten | |
EP0898650A1 (de) | Kraftstoffeinspritzeinrichtung für brennkraftmaschinen | |
DE10001828A1 (de) | Direktgesteuerte Kraftstoffeinspritzeinrichtung für eine Kolbenbrennkraftmaschine | |
DE10001099A1 (de) | Steuerventil für einen Injektor eines Kraftstoffeinspritzsystems für Brennkraftmaschinen mit Druckerhöhung im Steuerraum | |
EP1144857B1 (de) | Doppelschaltendes steuerventil mit hydraulischer verstärkung des aktors | |
EP1171708B1 (de) | Einspritzdüse | |
EP1117921A1 (de) | Common-rail-injektor | |
DE19939448A1 (de) | Injektor | |
EP1682769A1 (de) | Kraftstoffinjektor mit mehrteiligem, direktgesteuertem einspritzventilglied | |
EP1650427B1 (de) | Kraftstoffeinspritzventil für Brennkraftmaschinen | |
EP1658427B1 (de) | Kraftstoffeinspritzventil für brennkraftmaschinen | |
DE102010023698A1 (de) | Einspritzventil mit Direkt- und Servoantrieb | |
EP1276983B1 (de) | Ventil zum steuern von flüssigkeiten | |
DE10100512A1 (de) | Einspritzdüse | |
EP1908953B1 (de) | Kraftstoffeinspritzanlage | |
EP3184803B1 (de) | Kraftstoffinjektor | |
EP1724462A2 (de) | Kraftstoffeinspritzdüse | |
EP3184802B1 (de) | Kraftstoffinjektor | |
WO2001055583A2 (de) | Einspritzdüse | |
EP1187981A2 (de) | Steuerventil für einen injektor für ein kraftstoffeinspritzsystem mit von einem stössel geführtem stellglied | |
WO2001053689A1 (de) | Ventil zum steuern von flüssigkeiten | |
WO2001014715A1 (de) | Injektor | |
EP1502023A1 (de) | Kraftstoffeinspritzeinrichtung für brennkraftmaschinen | |
WO2005026525A1 (de) | Kraftstoffeinspritzventil für brennkraftmaschinen | |
DE102015226373A1 (de) | Kraftstoffinjektor |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR |
|
17P | Request for examination filed |
Effective date: 20020218 |
|
RBV | Designated contracting states (corrected) |
Designated state(s): DE FR GB IT |
|
17Q | First examination report despatched |
Effective date: 20040927 |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): DE FR GB IT |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GB Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20050914 |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D Free format text: NOT ENGLISH |
|
REF | Corresponds to: |
Ref document number: 50107401 Country of ref document: DE Date of ref document: 20051020 Kind code of ref document: P |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20060215 Year of fee payment: 6 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20060407 Year of fee payment: 6 |
|
GBV | Gb: ep patent (uk) treated as always having been void in accordance with gb section 77(7)/1977 [no translation filed] |
Effective date: 20050914 |
|
ET | Fr: translation filed | ||
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
26N | No opposition filed |
Effective date: 20060615 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST Effective date: 20071030 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: IT Payment date: 20070531 Year of fee payment: 7 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20070901 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20070228 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20080202 |