EP2735725A1 - Fuel injector valve for combustion engines - Google Patents
Fuel injector valve for combustion engines Download PDFInfo
- Publication number
- EP2735725A1 EP2735725A1 EP13188175.7A EP13188175A EP2735725A1 EP 2735725 A1 EP2735725 A1 EP 2735725A1 EP 13188175 A EP13188175 A EP 13188175A EP 2735725 A1 EP2735725 A1 EP 2735725A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- sleeve
- fuel injection
- control
- chamber
- control piston
- 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
- 239000000446 fuel Substances 0.000 title claims abstract description 74
- 238000002485 combustion reaction Methods 0.000 title claims description 13
- 238000002347 injection Methods 0.000 claims description 57
- 239000007924 injection Substances 0.000 claims description 57
- 238000007789 sealing Methods 0.000 claims description 27
- 238000004519 manufacturing process Methods 0.000 description 6
- 230000008901 benefit Effects 0.000 description 4
- 230000000694 effects Effects 0.000 description 2
- 239000002828 fuel tank Substances 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000008859 change Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000003111 delayed effect Effects 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 238000004804 winding Methods 0.000 description 1
Images
Classifications
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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
- F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
- F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
- F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
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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
- F02M63/0012—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
- 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
- F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
- F02M63/0043—Two-way valves
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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
- F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
- F02M2547/001—Control chambers formed by movable sleeves
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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
- F02M63/0012—Valves
- F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
- F02M63/0054—Check valves
Definitions
- the invention relates to a fuel injection valve, as it is preferably used for the injection of fuel directly into combustion chambers of self-igniting, high-speed internal combustion engines.
- fuel injection valves and fuel injection systems which inject fuel directly into combustion chambers of auto-ignition, high-speed internal combustion engines, the injection being carried out under high pressure.
- the fuel is conveyed by a high-pressure fuel pump from a fuel tank, compressed to high pressure and conveyed into a so-called rail, which serves as a reservoir for the compressed fuel.
- a high-pressure fuel pump from a fuel tank, compressed to high pressure and conveyed into a so-called rail, which serves as a reservoir for the compressed fuel.
- From this high-pressure fuel storage go from several lines that serve to supply the fuel injection valves, via which the compressed fuel is ultimately injected into the respective combustion chambers of the internal combustion engine.
- Such fuel injection valves are for example from the DE 100 24 702 A1 known.
- the known fuel injection valves operate on the servorhydraulic principle, that is, they include a nozzle needle, which is arranged longitudinally displaceable in the nozzle body of the fuel injection valve and opens or closes by their longitudinal movement one or more injection openings. The movement of this nozzle needle and thus the beginning and end of each injection is controlled hydraulically.
- a fuel-filled control chamber is present, the fuel pressure exerts a hydraulic closing force on the nozzle needle and presses it against a nozzle seat. Is the control room via a control valve connected to a low-pressure chamber, the pressure in the control chamber decreases and the nozzle needle is pushed away from the nozzle seat in its open position and thus releases the injection openings. When the pressure in the control chamber is increased again, the nozzle needle slides back into its closed position and closes the injection openings.
- the control valve with which the pressure in the control room is controlled, functions as a 2/2-way valve, d. H. it opens or closes the outlet throttle, which connects the control chamber with a low-pressure chamber.
- the inlet throttle which supplies the control chamber with fuel under high pressure, is always open. Even when the control valve is open, so constantly highly compressed fuel flows through the inlet throttle in the control room and from there via the outlet throttle directly into the low-pressure chamber. This amount of fuel must be compressed by the high pressure pump, although it is not needed for fuel injection.
- the additional power capacity required for the high-pressure fuel pump reduces the efficiency of the internal combustion engine.
- the fuel additionally discharged via the outlet throttle, which expands in the region of the outlet throttle and thus releases a considerable amount of heat, leads to a high thermal load on the control valve, in particular in high-performance internal combustion engines and in continuous operation under high load.
- a fuel injection valve in which the fuel supply and the fuel flow in the control chamber is controlled by a 3/2-way valve.
- the control chamber is connected to the inlet throttle and the outlet throttle closed when the injection is to be terminated.
- the inlet throttle is closed while the outlet throttle is opened.
- the 3/2-way valve has the disadvantage that it is relatively expensive to manufacture and requires additional space.
- the switching operation ie the construction or reduction of the fuel pressure in the control valve, relatively slow, which affects the small-capacity of the fuel injection valve, so that Fuel injector can not represent very small amounts of fuel or not with the necessary accuracy.
- the fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage over that the fuel injector reliably shuts off the inlet throttle during injection or seals against the control chamber, the fuel injection valve thus constructed is easy to manufacture. The necessary tolerances can be maintained so as to ensure a reliable function over the entire functional area.
- the fuel injection valve has a housing in which a pressure chamber can be filled with fuel at high pressure with a longitudinally movable nozzle needle, which cooperates with a nozzle seat and opens the connection of the pressure chamber with at least one injection opening by its longitudinal movement and closes.
- a control chamber which can be filled with fuel at high pressure via an inlet throttle, wherein at least indirectly a closing force is exerted on the nozzle needle by the pressure in the control chamber.
- the nozzle needle is guided at its end facing away from the nozzle seat in a sleeve, wherein the sleeve radially bounds the control chamber and wherein the sleeve rests against a valve body in which a control piston is movably arranged.
- the valve body defines together with the control piston a valve space, which is connectable to the control chamber via an outlet throttle and a control valve with a low-pressure chamber.
- the fuel injection valve according to the invention thus has a guide for the nozzle needle, which is independent of the leadership of the control piston. This allows a simpler and more cost-effective production, since the guides of both parts, so the control piston and the nozzle needle, does not have to be aligned and thus they can be produced in separate steps.
- the stroke of the control piston can be very precisely adjusted by an exact manufacture of the valve body in which the control piston is guided to an exact function represent the control piston over the entire operating range of the fuel injection valve.
- control piston is guided in the valve body and controls by its movement an inlet throttle and on, over which the control chamber can be filled with fuel under high pressure.
- inlet throttle is advantageously formed in the valve body and opens into the pressure chamber, d. H. That the highly compressed fuel from the pressure chamber, which surrounds the nozzle needle, is passed through the inlet throttle in the control chamber, thus resulting in a very compact structure that can be integrated into the existing concepts.
- control piston has a sealing surface, with which the control piston cooperates with a sealing seat for opening and closing the inlet throttle.
- This sealing seat causes the actual switching function, d. H. via this sealing seat, the inlet throttle is separated from the control room or connected to this.
- the sleeve in which the nozzle needle is guided by a closing spring with a formed on the sleeve contact surface sealingly pressed against an end face of the valve body is guided by a closing spring with a formed on the sleeve contact surface sealingly pressed against an end face of the valve body.
- the contact surface of the sleeve has a sealing edge which comes to rest on the end face of the valve body and which improves the sealing effect.
- the control chamber can be sealed well against the pressure chamber, with certain degrees of freedom with respect to the angle and with respect to a Desaxtechnik the nozzle needle remain.
- the end face of the valve body may be conically shaped and the contact surface of the sleeve flat, so that in this way a sealing edge is achieved, which improves the seal between the valve body and the sleeve.
- a shoulder may be provided on the inside of the sleeve, which limits the movement of the control piston during its opening movement and thus acts as a stop.
- the fine adjustment can be done in an advantageous manner via a shim, which is arranged so that the shim is clamped between the heel and the control piston when the control piston is in its open position.
- the thickness of this dial allows the stroke to be accurately adjusted in the range of one to a few microns so that the fuel injector or the function of the control piston can be easily adapted to the various conditions in the respective injector.
- control piston comes into abutment with its opening movement on a contact surface of the sleeve, with which the sleeve bears against the valve body.
- this requires a longer design, d. H.
- the sleeve can be made simpler, so that the overall result is a simpler structure.
- a fuel injection valve according to the invention is shown schematically in longitudinal section.
- the fuel injection valve comprises a housing 1, the an injector body 2 and a nozzle body 3, which are screwed together with a clamping nut 4 against each other.
- a pressure chamber 6 is formed, which is delimited at its combustion chamber end by a nozzle seat 17 and in which a nozzle needle 5 is longitudinally displaceable, with the nozzle seat 17 for opening and closing of injection openings 11, the combustion chamber facing formed in the nozzle body 3, cooperates.
- the nozzle needle 5 is guided with a guide portion 105 in the nozzle body 3 and at its end facing away from the nozzle seat in a sleeve 9, wherein between the sleeve 9 and a shoulder 15 of the nozzle needle 5, a closing spring 13 is arranged under pressure bias, on the one hand the nozzle needle 5 against the nozzle seat 14 presses and on the other hand, the sleeve 9 presses against a valve body 10.
- the valve body 10 in turn is in contact with a throttle plate 7, which also closes off the pressure chamber 6 nozzle seat facing away and which is clamped by a clamping screw 8 against a shoulder in the injector 2 and thus closes the pressure chamber 6 at this point liquid-tight. It can also be provided that the throttle plate 7 and the valve body 10 are integrally formed.
- the pressure chamber 6 can be filled with high-pressure fuel via a high-pressure connection 25, which has been compressed by a high-pressure pump (not shown in the drawing).
- This high fuel pressure prevails in the pressure chamber 6 and causes a hydraulic force on the nozzle needle 5, which acts on them from the nozzle seat 17 with a force acting in the longitudinal direction hydraulic force that exceeds the force of the closing spring 13 by far.
- the nozzle needle 5 with its nozzle seat facing away from the end face delimits a control chamber 12, which is bounded radially on the outside by the sleeve 9.
- the nozzle needle 5 opposite side of the control chamber 12 is bounded by a control piston 14 which is arranged longitudinally displaceable in the valve body 10 and thereby also guided in the valve body 10.
- the control piston 14 is designed as a stepped piston and is pressed by a spring 22 which surrounds the control piston 14 and which bears against a shoulder in the valve body 10 in the direction of the nozzle needle 5.
- the spring 22 is supported at its other end on a sealing surface 37 on the control piston 14, which is provided with a sealing seat 34 which is formed on the valve body 10, for opening and closing a flow cross-section interacts.
- the spring 22 is thus arranged in an inlet space 18, which is formed by the heel in the control piston 14 and in the valve body 10.
- an inlet throttle 27 is formed, which connects the pressure chamber 6 with the inlet chamber 18.
- a bevel is formed on the control sleeve 9, which ensures the connection between the inlet chamber 18 and the control chamber 12 when the control piston 14th in its open position, d. H. when it abuts a shoulder 29 formed on the inside of the sleeve 19.
- a valve chamber 16 is limited within the valve body 10, which is connected via an opening formed in the control piston 14 discharge throttle 28 with the control chamber 12.
- the discharge space 16 is in turn connected via a control valve 31 which is disposed within the injector body 2, with a low-pressure chamber 26 which is connected via a drain connection 40 with a low-pressure line, not shown, and ultimately with the fuel tank of the internal combustion engine.
- the control valve 31 is operated electromagnetically and has a magnet armature 32 with a sealing ball 33 attached thereto and moved by the magnet armature 32.
- the sealing ball 33 cooperates with a throttle valve 7 formed on the control valve seat 35, which is conical and serves as an abutment for the sealing ball 33 and for the armature 32.
- an electromagnet 36 is provided, which pulls the armature 32 and thus the sealing ball 33 from the control valve seat 35 when energized.
- an armature spring 38 is provided, which is arranged within the coil winding of the electromagnet 36.
- the operation of the fuel injection valve is as follows: At the beginning of the injection, when the injection valve is closed, the control valve 31 is in its closed position, ie the sealing ball 33 closes the outlet channel 30.
- the inlet chamber 18 prevails because of the connection to the pressure chamber 6 the inlet throttle 27, the same high pressure as in the high-pressure chamber 6, wherein this high pressure in the control chamber 12 and in the valve chamber 16 adjusts, so that the control piston 14 is surrounded by high pressure, which acts on both the first end face 20 and on the second end face 21 , so that ultimately no acting in the longitudinal direction resulting hydraulic forces act on the Steurkolben 14.
- the control piston 14 is pressed into contact with the shoulder 29, so that it is in the in FIG. 1 shown position. Due to the high pressure in the control chamber 12, the nozzle needle 5 is pressed against the nozzle seat 17 and thus closes the injection openings 11 so that they have no connection to the pressure chamber 6.
- control valve 31 If an injection to happen, the control valve 31 is actuated by the electromagnet 36 is energized. The armature 32 is then tightened and lifts the sealing ball 33 from the control valve seat 35, so that the valve chamber 16 is connected via the drain passage 30 with the low-pressure chamber 26. The pressure in the valve chamber 16 breaks it immediately, so that the control piston 14 is driven by the higher pressure in the control chamber 12 in the longitudinal direction in the direction of the control valve 31, until the control piston 14 comes with its sealing surface 37 on the sealing seat 34 of the valve body 10 to rest. As a result, the supply chamber 18 is separated from the control chamber 12, so that no more fuel via the inlet throttle 27 flows into the inlet chamber 18.
- the pressure in the control chamber 12 also collapses, so that the hydraulic force on the end face of the nozzle needle 5 is reduced.
- the nozzle needle 5 now lifts, driven by the pressure in the pressure chamber 6, from the nozzle seat 17 and releases a flow cross-section to the injection openings 11 so that fuel flows under high pressure from the pressure chamber 6 into the injection openings 11 and exits through them.
- By the movement of the nozzle needle 5 of the fuel in the control chamber 12 is slightly compressed, so continue to be a pressure difference between the Control chamber 12 and the valve chamber 16 results because a pressure compensation via the outlet throttle 28 is only delayed.
- control piston 14 is held in its upper position, ie in abutment with the sealing seat 34, during the entire injection.
- the nozzle needle 5 in the embodiment shown here has no upper mechanical stop, ie that it is operated ballistically.
- the control valve 31 is closed again, which is done by switching off the coil current of the electromagnet 36.
- the armature spring 38 By the armature spring 38, the armature 32 is pushed back into its closed position, d. H.
- the pressure in the valve chamber 16 rises again by inflowing fuel via the outlet throttle 28, which is sufficient together with the pressure in the inlet chamber 18, the control piston 14 back into contact with the shoulder 29 of the sleeve 9 Press, so that the connection between the inlet chamber 18 and the control chamber 12 is turned on again.
- the inflowing fuel via the inlet throttle 27 quickly increases the pressure in the control chamber 12 and also further in the valve chamber 16, so that the nozzle needle 5 experiences an increased force on its front side and is pressed by this hydraulic force in the control chamber 12 back into its closed position, ie in contact with the nozzle seat 17. Since the volumes of all rooms in the region of the control piston 14, so the valve chamber 16, the control chamber 12 and the inlet chamber 18, are very low, a pressure equalization between these rooms and the fuel injection valve is very quickly is ready for the next injection.
- Fig. 2 shows in an enlarged view in the region of the control piston 14, a further embodiment of the fuel injection valve according to the invention, with only a few changes have been made.
- a significant change concerns the insertion of a dial 23 which rests on the shoulder 29 on the inside of the sleeve 9 and is clamped in the open position of the control piston 14 between this and the shoulder 29.
- the stroke of the control piston 14, which is only very small and is generally between 10 and 30 micrometers, can be adjusted by the thickness of this adjusting washer 23 to achieve rapid switching between the two end positions of the control piston.
- a connecting groove 19 is provided at the valve needle 5 facing the end of the control piston 14.
- Another modification relates to the configuration of the contact surface 43 of the sleeve 9.
- This is formed here via a double cone, so that there is a sealing edge 45, with which the sleeve 9 rests against the end face 41 of the valve body 10.
- a sealing edge 45 By the sealing edge 45, a relatively high surface pressure in this area is achieved, which causes a better sealing effect between the sleeve 9 and the valve body 10.
- the nozzle needle 5 in the radial direction has a certain play and a possible Desax ist between the central axis of the control piston 14 and the axis of the valve needle 5 does not affect the function because the guidance of both bodies is decoupled. This facilitates the manufacture, since the sleeve 9 and the valve body 10 can be made separately.
- a further embodiment of the fuel injection valve according to the invention is shown, whereby also this embodiment only in the region of the control piston of the embodiment of FIG. 1 different.
- the stop of the control piston 14 is not provided here on a shoulder on the inside of the sleeve 9, but the stop is located on the contact surface 43 of the sleeve 9, wherein the hydraulic connection between the inlet chamber 18 and the control chamber 12 in turn by a connecting groove 19 at the second end face 21 of the control piston 14 is provided.
- This embodiment has the advantage that it is easier to manufacture and the paragraph 29 can be omitted on the inside of the sleeve 9.
- this embodiment increases the required installation space in the axial direction compared with the exemplary embodiments FIG. 1 or FIG. 2 ,
- a further modification with regard to the preceding exemplary embodiments relates to the configuration of the end face 41 of the valve body 10 or the contact surface 43 of the sleeve 9.
- the contact surface 43 of the sleeve 9 is here flat, so that the sleeve 9 assumes a rectangular shape when viewed in cross section.
- the end face 41 of the valve body 10 is conical, so that here too a sealing edge 45 'results, which ensures the increased surface pressure and thus a good seal.
- the operation is otherwise identical to that of the previous embodiments.
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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)
Abstract
Description
Die Erfindung betrifft ein Kraftstoffeinspritzventil, wie es vorzugsweise zur Einspritzung von Kraftstoff direkt in Brennräume von selbstzündenden, schnelllaufenden Brennkraftmaschinen verwendet wird.The invention relates to a fuel injection valve, as it is preferably used for the injection of fuel directly into combustion chambers of self-igniting, high-speed internal combustion engines.
Aus dem Stand der Technik sind Kraftstoffeinspritzventile und Kraftstoffeinspritzsysteme bekannt, die Kraftstoff direkt in Brennräume von selbstzündenden, schnell laufenden Brennkraftmaschinen einspritzen, wobei die Einspritzung unter hohem Druck geschieht. Hierzu wird der Kraftstoff durch eine Kraftstoffhochdruckpumpe aus einem Kraftstofftank gefördert, auf hohen Druck verdichtet und in ein sogenanntes Rail gefördert, das als Speicher für den verdichteten Kraftstoff dient. Von diesem Kraftstoffhochdruckspeicher gehen mehrere Leitungen ab, die der Versorgung der Kraftstoffeinspritzventile dienen, über die der verdichtete Kraftstoff letztlich in die jeweiligen Brennräume der Brennkraftmaschine eingespritzt wird. Solche Kraftstoffeinspritzventile sind beispielsweise aus der
Die bekannten Kraftstoffeinspritzventile arbeiten nach dem servorhydraulischen Prinzip, das heißt, sie beinhalten eine Düsennadel, die längsverschiebbar im Düsenkörper des Kraftstoffeinspritzventils angeordnet ist und die durch ihre Längsbewegung eine oder mehrere Einspritzöffnungen aufsteuert oder verschließt. Die Bewegung dieser Düsennadel und damit Beginn und Ende jeder Einspritzung wird hydraulisch gesteuert. Dazu ist ein kraftstoffgefüllter Steuerraum vorhanden, dessen Kraftstoffdruck eine hydraulische Schließkraft auf die Düsennadel ausübt und sie gegen einen Düsensitz drückt. Wird der Steuerraum über ein Steuerventil mit einem Niederdruckraum verbunden, so sinkt der Druck im Steuerraum und die Düsennadel wird vom Düsensitz weg in ihre Öffnungsstellung gedrückt und gibt so die Einspritzöffnungen frei. Wird der Druck im Steuerraum wieder erhöht, gleitet die Düsennadel zurück in ihre Schließstellung und verschließt die Einspritzöffnungen.The known fuel injection valves operate on the servorhydraulic principle, that is, they include a nozzle needle, which is arranged longitudinally displaceable in the nozzle body of the fuel injection valve and opens or closes by their longitudinal movement one or more injection openings. The movement of this nozzle needle and thus the beginning and end of each injection is controlled hydraulically. For this purpose, a fuel-filled control chamber is present, the fuel pressure exerts a hydraulic closing force on the nozzle needle and presses it against a nozzle seat. Is the control room via a control valve connected to a low-pressure chamber, the pressure in the control chamber decreases and the nozzle needle is pushed away from the nozzle seat in its open position and thus releases the injection openings. When the pressure in the control chamber is increased again, the nozzle needle slides back into its closed position and closes the injection openings.
Das Steuerventil, mit dem der Druck im Steuerraum gesteuert wird, funktioniert dabei als 2/2-Wegeventil, d. h. es öffnet oder verschließt die Ablaufdrossel, die den Steuerraum mit einem Niederdruckraum verbindet. Während dieses Vorgangs bleibt die Zulaufdrossel, über die der Steuerraum mit Kraftstoff unter hohem Druck versorgt wird, stets geöffnet. Auch bei geöffnetem Steuerventil fließt so ständig hochverdichteter Kraftstoff über die Zulaufdrossel in den Steuerraum und von dort weiter über die Ablaufdrossel direkt in den Niederdruckraum. Diese Kraftstoffmenge muss von der Hochdruckpumpe verdichtet werden, obwohl sie für die Kraftstoffeinspritzung nicht benötigt wird. Die dafür benötigte zusätzliche Leistungskapazität der Kraftstoffhochdruckpumpe schmälert die Effizienz der Brennkraftmaschine. Darüber hinaus führt der zusätzlich über die Ablaufdrossel abgeführte Kraftstoff, der im Bereich der Ablaufdrossel expandiert und damit ein erhebliches Maß an Wärme freisetzt, zu einer großen thermischen Belastung des Steuerventils, insbesondere bei leistungsstarken Brennkraftmaschinen und im Dauerbetrieb unter hoher Last.The control valve, with which the pressure in the control room is controlled, functions as a 2/2-way valve, d. H. it opens or closes the outlet throttle, which connects the control chamber with a low-pressure chamber. During this process, the inlet throttle, which supplies the control chamber with fuel under high pressure, is always open. Even when the control valve is open, so constantly highly compressed fuel flows through the inlet throttle in the control room and from there via the outlet throttle directly into the low-pressure chamber. This amount of fuel must be compressed by the high pressure pump, although it is not needed for fuel injection. The additional power capacity required for the high-pressure fuel pump reduces the efficiency of the internal combustion engine. In addition, the fuel additionally discharged via the outlet throttle, which expands in the region of the outlet throttle and thus releases a considerable amount of heat, leads to a high thermal load on the control valve, in particular in high-performance internal combustion engines and in continuous operation under high load.
Zur Vermeidung dieses Nachteils ist aus der
Das erfindungsgemäße Kraftstoffeinspritzventil mit den kennzeichnenden Merkmalen des Patentanspruchs 1 weist demgegenüber den Vorteil auf, dass der Kraftstoffinjektor die Zulaufdrossel zuverlässig während der Einspritzung abschaltet bzw. gegen den Steuerraum abdichtet, wobei das so gebaute Kraftstoffeinspritzventil einfach zu fertigen ist. Die notwendigen Toleranzen können so eingehalten werden, um eine zuverlässige Funktion über den gesamten Funktionsbereich zu gewährleisten. Hierzu weist das Kraftstoffeinspritzventil ein Gehäuse auf, in dem ein mit Kraftstoff unter hohem Druck befüllbarer Druckraum ausgebildet ist mit einer darin längsbeweglichen Düsennadel, die mit einem Düsensitz zusammenwirkt und durch ihre Längsbewegung die Verbindung des Druckraums mit wenigstens einer Einspritzöffnung öffnet und schließt. Weiterhin ist ein Steuerraum vorgesehen, der über eine Zulaufdrossel mit Kraftstoff unter hohem Druck befüllbar ist, wobei durch den Druck im Steuerraum zumindest mittelbar eine Schließkraft auf die Düsennadel ausgeübt wird. Die Düsennadel ist an ihrem dem Düsensitz abgewandten Ende in einer Hülse geführt, wobei die Hülse den Steuerraum radial begrenzt und wobei die Hülse an einem Ventilkörper anliegt, in welchem ein Steuerkolben beweglich angeordnet ist. Der Ventilkörper begrenzt zusammen mit dem Steuerkolben einen Ventilraum, der mit dem Steuerraum über eine Ablaufdrossel und über ein Steuerventil mit einem Niederdruckraum verbindbar ist.The fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage over that the fuel injector reliably shuts off the inlet throttle during injection or seals against the control chamber, the fuel injection valve thus constructed is easy to manufacture. The necessary tolerances can be maintained so as to ensure a reliable function over the entire functional area. For this purpose, the fuel injection valve has a housing in which a pressure chamber can be filled with fuel at high pressure with a longitudinally movable nozzle needle, which cooperates with a nozzle seat and opens the connection of the pressure chamber with at least one injection opening by its longitudinal movement and closes. Furthermore, a control chamber is provided which can be filled with fuel at high pressure via an inlet throttle, wherein at least indirectly a closing force is exerted on the nozzle needle by the pressure in the control chamber. The nozzle needle is guided at its end facing away from the nozzle seat in a sleeve, wherein the sleeve radially bounds the control chamber and wherein the sleeve rests against a valve body in which a control piston is movably arranged. The valve body defines together with the control piston a valve space, which is connectable to the control chamber via an outlet throttle and a control valve with a low-pressure chamber.
Das erfindungsgemäße Kraftstoffeinspritzventil weist also eine Führung für die Düsennadel auf, die unabhängig von der Führung des Steuerkolbens ist. Dies erlaubt eine einfachere und kostengünstigere Fertigung, da die Führungen beider Teile, also des Steuerkolbens und der Düsennadel, nicht fluchten muss und sie somit in getrennten Arbeitsschritten herstellbar sind. Darüber hinaus lässt sich der Hub des Steuerkolbens durch eine exakte Fertigung des Ventilkörpers, in dem der Steuerkolben geführt ist, sehr präzise einstellen, um eine exakte Funktion des Steuerkolbens über den gesamten Arbeitsbereich des Kraftstoffeinspritzventils darzustellen.The fuel injection valve according to the invention thus has a guide for the nozzle needle, which is independent of the leadership of the control piston. This allows a simpler and more cost-effective production, since the guides of both parts, so the control piston and the nozzle needle, does not have to be aligned and thus they can be produced in separate steps. In addition, the stroke of the control piston can be very precisely adjusted by an exact manufacture of the valve body in which the control piston is guided to an exact function represent the control piston over the entire operating range of the fuel injection valve.
In einer ersten vorteilhaften Ausgestaltung ist der Steuerkolben im Ventilkörper geführt und steuert durch seine Bewegung eine Zulaufdrossel auf und zu, über die der Steuerraum mit Kraftstoff unter hohem Druck befüllbar ist. Insbesondere wenn die Zulaufdrossel vorteilhafterweise im Ventilkörper ausgebildet ist und in den Druckraum mündet, d. h. dass der hochverdichtete Kraftstoff aus dem Druckraum, der die Düsennadel umgibt, über die Zulaufdrossel in den Steuerraum geleitet wird, ergibt sich so ein sehr kompakter Aufbau, der in die bisher bestehenden Konzepte integrierbar ist.In a first advantageous embodiment, the control piston is guided in the valve body and controls by its movement an inlet throttle and on, over which the control chamber can be filled with fuel under high pressure. In particular, when the inlet throttle is advantageously formed in the valve body and opens into the pressure chamber, d. H. That the highly compressed fuel from the pressure chamber, which surrounds the nozzle needle, is passed through the inlet throttle in the control chamber, thus resulting in a very compact structure that can be integrated into the existing concepts.
In einer weiteren vorteilhaften Ausgestaltung weist der Steuerkolben eine Dichtfläche auf, mit der der Steuerkolben mit einem Dichtsitz zum Öffnen und Verschließen der Zulaufdrossel zusammenwirkt. Dieser Dichtsitz bewirkt die eigentliche Schaltfunktion, d. h. über diesen Dichtsitz wird die Zulaufdrossel vom Steuerraum getrennt oder mit diesem verbunden.In a further advantageous embodiment, the control piston has a sealing surface, with which the control piston cooperates with a sealing seat for opening and closing the inlet throttle. This sealing seat causes the actual switching function, d. H. via this sealing seat, the inlet throttle is separated from the control room or connected to this.
In einer weiteren vorteilhaften Ausgestaltung wird die Hülse, in der die Düsennadel geführt ist, durch eine Schließfeder mit einer an der Hülse ausgebildeten Kontaktfläche dichtend gegen eine Stirnseite des Ventilkörpers gedrückt. Vorzugsweise weist hierbei die Kontaktfläche der Hülse eine Dichtkante auf, die an der Stirnseite des Ventilkörpers zur Anlage kommt und die die Dichtwirkung verbessert. Mit dieser Maßnahme lässt sich der Steuerraum gut gegen den Druckraum abdichten, wobei gewisse Freiheitsgrade hinsichtlich der Winkel und bezüglich einer Desaxierung der Düsennadel erhalten bleiben. Alternativ kann auch die Stirnseite des Ventilkörpers konisch geformt sein und die Kontaktfläche der Hülse eben, sodass auch auf diese Weise eine Dichtkante zustande kommt, die die Abdichtung zwischen dem Ventilkörper und der Hülse verbessert.In a further advantageous embodiment, the sleeve in which the nozzle needle is guided by a closing spring with a formed on the sleeve contact surface sealingly pressed against an end face of the valve body. Preferably, in this case, the contact surface of the sleeve has a sealing edge which comes to rest on the end face of the valve body and which improves the sealing effect. With this measure, the control chamber can be sealed well against the pressure chamber, with certain degrees of freedom with respect to the angle and with respect to a Desaxierung the nozzle needle remain. Alternatively, the end face of the valve body may be conically shaped and the contact surface of the sleeve flat, so that in this way a sealing edge is achieved, which improves the seal between the valve body and the sleeve.
Zur Begrenzung des Hubs des Steuerkolbens bei seiner Öffnungsbewegung, also bei der Öffnung und Verbindung der Zulaufdrossel mit dem Steuerraum, kann an der Innenseite der Hülse ein Absatz vorgesehen sein, der die Bewegung des Steuerkolbens bei seiner Öffnungsbewegung begrenzt und damit als Anschlag fungiert. Da für eine ordnungsgemäße Funktion die Größe dieses Maximalhubs des Steuerkolbens entscheidend ist, kann die Feineinstellung in vorteilhafter Weise über eine Einstellscheibe geschehen, die so angeordnet ist, dass die Einstellscheibe zwischen dem Absatz und dem Steuerkolben eingeklemmt wird, wenn der Steuerkolben in seiner Öffnungsstellung ist. Über die Dicke dieser Einstellscheibe lässt sich der Hub im Bereich von einem bis wenigen Mikrometern genau einstellen, sodass sich das Kraftstoffeinspritzventil bzw. die Funktion des Steuerkolbens an die verschiedenen Bedingungen in dem jeweiligen Einspritzventil problemlos anpassen lässt.To limit the stroke of the control piston during its opening movement, ie at the opening and connection of the inlet throttle with the control chamber, a shoulder may be provided on the inside of the sleeve, which limits the movement of the control piston during its opening movement and thus acts as a stop. Because for a proper function, the size of this Maximalhubs the control piston is crucial, the fine adjustment can be done in an advantageous manner via a shim, which is arranged so that the shim is clamped between the heel and the control piston when the control piston is in its open position. The thickness of this dial allows the stroke to be accurately adjusted in the range of one to a few microns so that the fuel injector or the function of the control piston can be easily adapted to the various conditions in the respective injector.
Es kann auch vorgesehen sein, dass der Steuerkolben bei seiner Öffnungsbewegung an einer Kontaktfläche der Hülse zur Anlage kommt, mit der die Hülse am Ventilkörper anliegt. Dies bedingt zwar eine längere Bauform, d. h. eine weniger kompakte Ausführung als die mit dem Absatz an der Innenseite der Hülse erreichbar ist, andererseits kann die Hülse einfacher ausgefertigt werden, sodass sich insgesamt ein einfacherer Aufbau ergibt.It can also be provided that the control piston comes into abutment with its opening movement on a contact surface of the sleeve, with which the sleeve bears against the valve body. Although this requires a longer design, d. H. On the other hand, the sleeve can be made simpler, so that the overall result is a simpler structure.
Weitere Vorteile und vorteilhafte Ausgestaltungen des Gegenstandes der Erfindung sind der Beschreibung und der Zeichnung entnehmbar.Further advantages and advantageous embodiments of the subject matter of the invention can be taken from the description and the drawing.
In der Zeichnung sind verschiedene Ausführungsbeispiele des erfindungsgemäßen Kraftstoffeinspritzventils dargestellt. Es zeigt
- Figur 1
- einen Längsschnitt durch ein erfindungsgemäßes Kraftstoffeinspritzventil,
Figur 2- ein weiteres Ausführungsbespiel, wobei nur der Bereich des Druckraums dargestellt ist, und
Figur 3- einen Längsschnitt durch ein weiteres erfindungsgemäßes Kraftstoffeinspritzventil in derselben Darstellung wie
Fig. 1 .
- FIG. 1
- a longitudinal section through a fuel injection valve according to the invention,
- FIG. 2
- a further Ausführungsbespiel, wherein only the area of the pressure chamber is shown, and
- FIG. 3
- a longitudinal section through another inventive fuel injection valve in the same representation as
Fig. 1 ,
In
Der Druckraum 6 ist über einen Hochdruckanschluss 25 mit Kraftstoff unter hohem Druck befüllbar, der von einer in der Zeichnung nicht dargestellten Hochdruckpumpe verdichtet worden ist. Dieser hohe Kraftstoffdruck herrscht im Druckraum 6 und bewirkt eine hydraulische Kraft auf die Düsennadel 5, die diese vom Düsensitz 17 weg mit einer in Längsrichtung wirkenden hydraulischen Kraft beaufschlagt, die die Kraft der Schließfeder 13 bei weitem übersteigt. Zur Erzeugung einer für die Längsbewegung der Düsennadel 5 notwendigen Gegenkraft begrenzt die Düsennadel 5 mit ihrer düsensitzabgewandten Stirnseite einen Steuerraum 12, der durch die Hülse 9 radial außen begrenzt wird. Die der Düsennadel 5 gegenüberliegende Seite des Steuerraums 12 wird von einem Steuerkolben 14 begrenzt, der im Ventilkörper 10 längsverschiebbar angeordnet ist und dabei auch im Ventilkörper 10 geführt ist. Der Steuerkolben 14 ist als Stufenkolben ausgeführt und wird von einer Feder 22, die den Steuerkolben 14 umgibt und die an einem Absatz im Ventilkörper 10 anliegt, in Richtung der Düsennadel 5 gedrückt. Hierbei stützt sich die Feder 22 mit ihrem anderen Ende an einer Dichtfläche 37 am Steuerkolben 14 ab, die mit einem Dichtsitz 34, der am Ventilkörper 10 ausgebildet ist, zum Öffnen und Schließen eines Durchflussquerschnittes zusammenwirkt. Die Feder 22 ist somit in einem Zulaufraum 18 angeordnet, der durch den Absatz im Steuerkolben 14 bzw. im Ventilkörper 10 gebildet wird.The
Im Ventilkörper 10 ist eine Zulaufdrossel 27 ausgebildet, die den Druckraum 6 mit dem Zulaufraum 18 verbindet. Über den zwischen dem Dichtsitz 34 und der Dichtfläche 37 gebildeten Querschnitt wird der Zulaufraum 18 mit dem Steuerraum 12 verbunden, wobei hierzu an der Steuerhülse 9 eine Anschrägung ausgebildet ist, die die Verbindung zwischen dem Zulaufraum 18 und dem Steuerraum 12 sicherstellt, wenn der Steuerkolben 14 in seiner Öffnungsstellung ist, d. h. wenn er an einem Absatz 29, der an der Innenseite der Hülse 19 ausgebildet ist, zur Anlage kommt.In the
Begrenzt durch den Steuerkolben 10, durch die Drosselscheibe 7 und durch die der Düsennadel 5 abgewandte erste Stirnseite 20 des Steuerkolbens 14 wird innerhalb des Ventilkörpers 10 ein Ventilraum 16 begrenzt, der über eine im Steuerkolben 14 ausgebildete Ablaufdrossel 28 mit dem Steuerraum 12 verbunden ist. Der Ablaufraum 16 ist wiederum über ein Steuerventil 31, das innerhalb des Injektorkörpers 2 angeordnet ist, mit einem Niederdruckraum 26 verbunden, der über einen Leckölanschluss 40 mit einer nicht dargestellten Niederdruckleitung und letztlich mit dem Kraftstofftank der Brennkraftmaschine verbunden ist. Die Verbindung des Ablaufraums 16 mit dem Niederdruckraum 26 erfolgt über einen Ablaufkanal 30, der in der Drosselscheibe 7 ausgebildet ist und der mittels des Steuerventils 31 geöffnet oder verschlossen werden kann.Limited by the
Das Steuerventil 31 wird elektromagnetisch betrieben und weist einen Magnetanker 32 mit einer daran angebrachten und durch den Magnetanker 32 bewegten Dichtkugel 33 auf. Die Dichtkugel 33 wirkt mit einem an der Drosselscheibe 7 ausgebildeten Steuerventilsitz 35 zusammen, der konisch ausgebildet ist und als Widerlager für die Dichtkugel 33 bzw. für den Magnetanker 32 dient. Zur Bewegung des Magnetankers 32 ist ein Elektromagnet 36 vorgesehen, der bei Bestromung den Magnetanker 32 und damit die Dichtkugel 33 vom Steuerventilsitz 35 wegzieht. Um den Magnetanker 32 wieder zurück in seine Schließstellung zu drücken, ist eine Ankerfeder 38 vorgesehen, die innerhalb der Spulenwicklung des Elektromagnets 36 angeordnet ist.The
Die Funktionsweise des Kraftstoffeinspritzventils ist wie folgt: Zu Beginn der Einspritzung, wenn das Einspritzventil geschlossen ist, befindet sich das Steuerventil 31 in seiner geschlossenen Stellung, d. h. die Dichtkugel 33 verschließt den Ablaufkanal 30. Im Zulaufraum 18 herrscht wegen der Verbindung mit dem Druckraum 6 über die Zulaufdrossel 27 der gleiche Hochdruck wie im Hochdruckraum 6, wobei sich dieser hohe Druck auch im Steuerraum 12 und im Ventilraum 16 einstellt, sodass der Steuerkolben 14 von Hochdruck umgeben ist, der sowohl auf die erste Stirnseite 20 als auch auf die zweite Stirnseite 21 wirkt, sodass letztendlich keine in Längsrichtung wirkenden resultierenden hydraulischen Kräfte auf den Steurkolben 14 wirken. Durch die Feder 22 wird der Steuerkolben 14 in Anlage an den Absatz 29 gedrückt, sodass er sich in der in
Soll eine Einspritzung geschehen, so wird das Steuerventil 31 betätigt, indem der Elektromagnet 36 bestromt wird. Der Magnetanker 32 wird daraufhin angezogen und hebt die Dichtkugel 33 vom Steuerventilsitz 35 ab, sodass der Ventilraum 16 über den Ablaufkanal 30 mit dem Niederdruckraum 26 verbunden wird. Der Druck im Ventilraum 16 bricht darauf sofort ein, sodass der Steuerkolben 14 angetrieben durch den höheren Druck im Steuerraum 12 in Längsrichtung in Richtung des Steuerventils 31 verschoben wird, bis der Steuerkolben 14 mit seiner Dichtfläche 37 am Dichtsitz 34 des Ventilkörpers 10 zur Anlage kommt. Dadurch wird der Zulaufraum 18 vom Steuerraum 12 getrennt, sodass kein Kraftstoff mehr über die Zulaufdrossel 27 in den Zulaufraum 18 einströmt. Durch die Verbindung über die Ablaufdrossel 28 und durch die Bewegung des Steuerkolbens 14, die das Volumen des Steuerraums 12 vergrößert, bricht daraufhin auch der Druck im Steuerraum 12 zusammen, sodass sich die hydraulische Kraft auf die Stirnseite der Düsennadel 5 vermindert. Die Düsennadel 5 hebt nunmehr, angetrieben durch den Druck im Druckraum 6, vom Düsensitz 17 ab und gibt einen Durchflussquerschnitt zu den Einspritzöffnungen 11 frei, sodass Kraftstoff unter hohem Druck aus dem Druckraum 6 in die Einspritzöffnungen 11 strömt und durch diese austritt. Durch die Bewegung der Düsennadel 5 wird der Kraftstoff im Steuerraum 12 etwas komprimiert, sodass sich weiterhin eine Druckdifferenz zwischen dem Steuerraum 12 und dem Ventilraum 16 ergibt, da ein Druckausgleich über die Ablaufdrossel 28 nur zeitverzögert geschieht. Durch diese Druckdifferenz, wird der Steuerkolben 14 in seiner oberen Stellung, d. h. in Anlage am Dichtsitz 34, während der gesamten Einspritzung gehalten. Hierbei ist zu beachten, dass die Düsennadel 5 in der hier gezeigten Ausführungsform keinen oberen mechanischen Anschlag hat, d. h. dass sie ballistisch betrieben wird.If an injection to happen, the
Zur Beendigung der Einspritzung, was zu einem Zeitpunkt geschieht, zu dem die Düsennadel 5 noch in ihrer Aufwärtsbewegung begriffen ist, wird das Steuerventil 31 wiederum geschlossen, was durch Abschalten des Spulenstroms des Elektromagneten 36 geschieht. Durch die Ankerfeder 38 wird der Magnetanker 32 zurück in seine Schließstellung gedrückt, d. h. die Dichtkugel 33 verschließt wieder den Ablaufkanal 30. Daraufhin steigt der Druck im Ventilraum 16 durch zuströmenden Kraftstoff über die Ablaufdrossel 28 wieder an, was zusammen mit dem Druck im Zulaufraum 18 ausreicht, den Steuerkolben 14 zurück in Anlage an den Absatz 29 der Hülse 9 zu drücken, sodass die Verbindung zwischen dem Zulaufraum 18 und dem Steuerraum 12 erneut aufgesteuert wird. Der nachströmende Kraftstoff über die Zulaufdrossel 27 erhöht rasch wieder den Druck in Steuerraum 12 und auch weiter in Ventilraum 16, sodass die Düsennadel 5 eine erhöhte Kraft auf ihre Stirnseite erfährt und durch diese hydraulische Kraft im Steuerraum 12 wieder zurück in ihre Schließstellung gedrückt wird, also in Anlage an den Düsensitz 17. Da die Volumina sämtlicher Räume im Bereich des Steuerkolbens 14, also des Ventilraums 16, des Steuerraums 12 und auch des Zulaufraums 18, sehr gering sind, stellt sich sehr rasch wieder ein Druckausgleich zwischen diesen Räumen ein und das Kraftstoffeinspritzventil ist bereit für die nächste Einspritzung.To complete the injection, which happens at a time when the
Eine weitere Änderung betrifft die Ausgestaltung der Kontaktfläche 43 der Hülse 9. Diese ist hier über einen Doppelkegel geformt, sodass sich eine Dichtkante 45 ergibt, mit der die Hülse 9 an der Stirnseite 41 des Ventilkörpers 10 anliegt. Durch die Dichtkante 45 wird eine relativ hohe Flächenpressung in diesem Bereich erreicht, was eine bessere Dichtwirkung zwischen der Hülse 9 und dem Ventilkörper 10 bewirkt. Gleichzeitig erreicht man durch die Trennung der beiden Funktionen des Ventilkörpers 10 und der Hülse 9, dass die Düsennadel 5 in radialer Richtung ein gewisses Spiel hat und sich eine eventuelle Desaxierung zwischen der Mittelachse des Steuerkolbens 14 und der Achse der Ventilnadel 5 nicht auf die Funktion auswirkt, da die Führung beider Körper entkoppelt ist. Dies erleichtert die Fertigung, da die Hülse 9 und der Ventilkörper 10 getrennt hergestellt werden können.Another modification relates to the configuration of the
In
Eine weitere Änderung bezüglich der vorhergehenden Ausführungsbeispiele betrifft die Ausgestaltung der Stirnseite 41 des Ventilkörpers 10 bzw. der Kontaktfläche 43 der Hülse 9. Die Kontaktfläche 43 der Hülse 9 ist hier flach ausgebildet, sodass die Hülse 9 im Querschnitt betrachtet eine Rechteckform annimmt. Um weiterhin eine gute Abdichtung zu erzielen, ist die Stirnseite 41 des Ventilkörpers 10 konisch ausgebildet, sodass sich auch hier eine Dichtkante 45' ergibt, die für die erhöhte Flächenpressung und damit für eine gute Abdichtung sorgt. Die Funktionsweise ist ansonsten identisch mit der der vorhergehenden Ausführungsbeispiele.A further modification with regard to the preceding exemplary embodiments relates to the configuration of the
Claims (12)
dadurch gekennzeichnet, dass
die Düsennadel (5) an ihrem dem Düsensitz (17) abgewandten Ende in einer Hülse (9) geführt ist, wobei die Hülse (9) den Steuerraum (12) radial begrenzt und wobei die Hülse (9) an einem Ventilkörper (10) anliegt, in welchem ein Steuerkolben (14) beweglich angeordnet ist, wobei der Ventilkörper (10) zusammen mit dem Steuerkolben (14) einen Ventilraum (16) begrenzt, der mit dem Steuerraum (12) über eine Ablaufdrossel (28) und über ein Steuerventil (31) mit einem Niederdruckraum (26) verbindbar ist.Fuel injection valve for internal combustion engines having a housing (1) in which a high pressure fuel can be filled pressure chamber (6) is formed therein with a longitudinally movable nozzle needle (5) which cooperates with a nozzle seat (17) and by their longitudinal movement, the connection of the pressure chamber (6) with at least one injection opening (11) opens and closes, and with a control chamber (12) via an inlet throttle (27) can be filled with fuel under high pressure, wherein at least indirectly by the pressure in the control chamber (12) a closing force is exerted on the nozzle needle (5),
characterized in that
the nozzle needle (5) is guided at its end facing away from the nozzle seat (17) in a sleeve (9), wherein the sleeve (9) radially limits the control chamber (12) and wherein the sleeve (9) rests against a valve body (10) in which a control piston (14) is movably arranged, wherein the valve body (10) together with the control piston (14) delimits a valve space (16) which communicates with the control chamber (12) via an outlet throttle (28) and via a control valve (14). 31) with a low pressure space (26) is connectable.
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DE201210221624 DE102012221624A1 (en) | 2012-11-27 | 2012-11-27 | Fuel injection valve for internal combustion engines |
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WO2015024692A1 (en) * | 2013-08-20 | 2015-02-26 | Delphi International Operations Luxembourg S.À R.L. | Control valve arrangement |
EP2960487A1 (en) * | 2014-06-26 | 2015-12-30 | Robert Bosch Gmbh | Fuel injector valve for combustion engines |
EP2867517B1 (en) * | 2012-06-29 | 2016-07-13 | Robert Bosch GmbH | Fuel injection valve for internal combustion engines |
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CN111502880A (en) * | 2020-03-17 | 2020-08-07 | 成都威特电喷有限责任公司 | Electric control high-pressure fuel injection device capable of preventing dynamic leakage |
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DE102017002366A1 (en) * | 2017-03-10 | 2018-09-13 | Liebherr-Components Deggendorf Gmbh | Fuel injection valve |
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JP2011208554A (en) * | 2010-03-29 | 2011-10-20 | Denso Corp | Fuel injection device |
US20120152206A1 (en) * | 2010-12-17 | 2012-06-21 | Denso Corporation | Fuel injection device |
-
2012
- 2012-11-27 DE DE201210221624 patent/DE102012221624A1/en not_active Withdrawn
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2013
- 2013-10-10 EP EP13188175.7A patent/EP2735725B1/en active Active
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DE10024702A1 (en) | 2000-05-18 | 2001-11-22 | Bosch Gmbh Robert | Fuel injector for storage injection system includes bypass channel injecting into outlet path at valve chamber |
DE10131617A1 (en) | 2001-06-29 | 2003-01-23 | Bosch Gmbh Robert | Fuel injector switching valve for pressure relief / loading of a control room |
WO2004040119A1 (en) * | 2002-10-31 | 2004-05-13 | Robert Bosch Gmbh | Injection valve |
WO2007098621A1 (en) * | 2006-03-03 | 2007-09-07 | Ganser-Hydromag Ag | Fuel injection valve for internal combustion engines |
DE102006026398A1 (en) * | 2006-06-07 | 2007-12-13 | Robert Bosch Gmbh | Injector for injecting fuel into a combustion chamber of an internal combustion chamber operates via an actuator while linked to a fuel inlet for supplying fuel under system pressure |
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Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
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EP2867517B1 (en) * | 2012-06-29 | 2016-07-13 | Robert Bosch GmbH | Fuel injection valve for internal combustion engines |
EP2818690A1 (en) * | 2013-06-27 | 2014-12-31 | Robert Bosch Gmbh | Fuel injector valve with multi-part valve body on the control chamber |
WO2015024692A1 (en) * | 2013-08-20 | 2015-02-26 | Delphi International Operations Luxembourg S.À R.L. | Control valve arrangement |
EP2960487A1 (en) * | 2014-06-26 | 2015-12-30 | Robert Bosch Gmbh | Fuel injector valve for combustion engines |
US10077748B2 (en) | 2014-12-23 | 2018-09-18 | Cummins Inc. | Fuel injector for common rail |
CN111502880A (en) * | 2020-03-17 | 2020-08-07 | 成都威特电喷有限责任公司 | Electric control high-pressure fuel injection device capable of preventing dynamic leakage |
Also Published As
Publication number | Publication date |
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EP2735725B1 (en) | 2015-12-30 |
DE102012221624A1 (en) | 2014-05-28 |
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