EP1518050B1 - Injector for an injection system - Google Patents
Injector for an injection system Download PDFInfo
- Publication number
- EP1518050B1 EP1518050B1 EP03737904A EP03737904A EP1518050B1 EP 1518050 B1 EP1518050 B1 EP 1518050B1 EP 03737904 A EP03737904 A EP 03737904A EP 03737904 A EP03737904 A EP 03737904A EP 1518050 B1 EP1518050 B1 EP 1518050B1
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- EP
- European Patent Office
- Prior art keywords
- injector
- bore
- injection
- pressure
- drilled
- 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 - Fee Related
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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
- 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
- F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
- F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
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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
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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
- F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
- F02M55/02—Conduits between injection pumps and injectors, e.g. conduits between pump and common-rail or conduits between common-rail and injectors
- F02M55/025—Common rails
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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
- F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
- F02M55/04—Means for damping vibrations or pressure fluctuations in injection pump inlets or outlets
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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
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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
- F02M61/167—Means for compensating clearance or thermal expansion
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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
- F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
- F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
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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
- F02M2200/31—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements
- F02M2200/315—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements for damping fuel pressure fluctuations
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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
- F02M2200/40—Fuel-injection apparatus with fuel accumulators, e.g. a fuel injector having an integrated fuel accumulator
Definitions
- the invention is based on the preamble of the main claim • of an injector for an injection system, which is designed for the injection of fuel into an internal combustion engine.
- the injector is connected by means of a high-pressure line to a high-pressure accumulator (rail) of the injection system, which provides the fuel required for injection into a cylinder of the internal combustion engine.
- the fuel is provided by a high pressure pump with a certain operating pressure in the high pressure accumulator.
- a high-pressure bore is provided, through which the fuel is guided by means of a controllable nozzle needle to injection holes of the injector.
- the high-pressure bore is in the form of stepped bores, the diameter of the individual stepped bores becoming narrower in the direction of the nozzle tip.
- a further bore is provided, which is likewise designed as a stepped bore, wherein the diameter of the individual stages of the further bore also decreases in the direction of the nozzle tip.
- an injection valve is provided with a high-pressure bore for supplying fuel to injection holes of a nozzle needle.
- the high-pressure bore is formed as a stepped bore, wherein the diameter of the individual holes decrease in the direction of the nozzle tip.
- a further bore which is also formed as a stepped bore, wherein the diameter of the bore decreases in the direction of the nozzle tip.
- the invention has for its object to further form an injector for the fuel injection, that in particular the pressure drops, vibrations and their interactions occurring in the multiple injection of fuel can be reduced and a more uniform injection is possible. This object is achieved with the features of claim 1.
- the high-pressure bore which is mounted within the injector, designed such that it forms the largest possible buffer memory for the fuel.
- the high pressure bore is located in close proximity to the injection holes of the nozzle unit.
- the length of the connecting lines between the high-pressure accumulator and the connected injectors can advantageously be regarded as less critical, since the pressure drop occurring during the injection can be compensated in particular by the buffer volume which is made available by the high-pressure bore according to the invention within the injector.
- the high-pressure bore in the injector is designed as a stepped bore.
- the stepped bore has two or more drill steps.
- the high-pressure bore has at least two bore diameters, with subsequent bore diameters being narrower towards the nozzle tip. It is provided a further step-shaped bore which is arranged parallel to the high-pressure bore. The bore diameter of the further bore expand in the direction of the nozzle tip.
- the adjacent cross-sectional areas of the two holes are formed inversely proportional to each other. This ensures that the intermediate wall between the two holes always maintains the same strength.
- the injector can be made overall slim, without compromising the necessary strength in the high pressure area.
- a particularly advantageous solution is also seen, for example, make the individual drilling stages of the high-pressure bore in the flow direction of the fuel, for example, each narrower. Start at the top end of the injector with the widest hole and then drill the next hole with a smaller diameter so that the narrowest hole is formed near the nozzle tip.
- Such an arrangement of the individual drilling stages is particularly easy to carry out in terms of manufacturing technology.
- the volume for the fuel to be stored can also be predetermined in a simple manner. It seems advantageous to make the volume smaller for the individual drilling stages in the flow direction of the fuel. In this way, one obtains in the upper part of the injector, a relatively large storage volume for the fuel, since there is usually enough space for the expansion of the high pressure bore available. In the lower drilling stages, however, the volume can be designed so that the damping effect of the pressure waves is particularly pronounced.
- a further improvement of the damping effect for the pressure waves can also be achieved if the transition between two drilling stages is provided with a bevelled, in particular with a conical annular surface. At the ring surface, the pressure waves are also broken and partially absorbed.
- transitions In order to avoid that new vibrations can form at the transition between two adjacent drilling stages due to different flow velocities in the individual drilling stages, in an alternative embodiment of the invention it is proposed to design the transitions continuously.
- Such stepless transitions which are formed, for example, arcuate, can be easily mounted manufacturing technology with a correspondingly shaped profile cutter.
- the two bores are drilled parallel to the longitudinal axis of the injector and have at the upper end of the injector housing an access opening. These access openings provide good access for the connection of electrical lines for the piezoelectric actuator and an external fuel line.
- the injector according to the invention is particularly well suited for use in a common rail injection system. Especially When injecting diesel fuel is working with a very high fuel pressure, so here at Injection intensity of pressure waves and vibrations is especially high.
- FIG. 1 is shown in a schematic representation of an embodiment of an injector 10 according to the invention.
- an injector housing 1 in which an axially parallel, stepped longitudinal bore is introduced.
- the longitudinal bore is in the right part of FIG. 1 recognizable and is designed as a high-pressure bore 2. It has at its upper end an access opening 13 to which an external fuel line can be connected, for example with a screw thread.
- a further stepped bore 10 In the left part of FIG. 1 is introduced a further stepped bore 10. Their drilling stages are preferably designed so that the drill diameters expand from top to bottom towards the nozzle tip.
- an access opening 13 is likewise provided, on which an electrical connection and control lines for the piezoelectric actuator 9 can be provided.
- the adjacent two step-shaped holes 2,10 are preferably formed with their drill diameters such that at a Bohrquer bain the two adjacent Cross-sectional areas 14a, 14b behave inversely proportional to each other. In addition to a narrower bore, there is thus a larger bore, so that preferably the sum of the drill cross sections in different stages is preferably constant. This advantageously achieves that the wall thickness between the two holes is always made homogeneous and sufficiently strong to withstand the high fuel pressure.
- the piezoelectric actuator 9 is fixedly arranged with its upper end on the injector 1. Its lower end is designed to be movable and acts on an axial length change to a nozzle needle 6, which is arranged in a nozzle unit 11.
- the nozzle needle 6 can open in response to control signals to the actuator with its lower conical portion injection holes 5 of the nozzle unit 11 or close fuel-tight.
- a high-pressure chamber 7 and an inlet throttle 3 and an outlet throttle 8 are furthermore provided in the nozzle unit 11.
- the inlet throttle 3 is connected to a feed line 4, which is fed by the high pressure bore 2 and substantially promotes the high pressure fuel to the nozzle needle 6, so that the fuel exits when lifting the nozzle needle 6 via the injection holes 5 and into the combustion chamber of a Internal combustion engine can be injected.
- the high-pressure bore 2 forms with its entire volume V1, V2, Vn a buffer for the fuel to be injected.
- a connection for an external connecting line is provided at the access opening 13, which can be firmly connected to the high-pressure bore 2, for example by means of a union nut.
- the black arrow above the high-pressure bore 2 should indicate the direction of flow of the fuel.
- the high pressure bore 2 is formed in contrast to a conventional cylindrical bore as a multiple stepped bore.
- FIG. 1 For example, three drill stages with the drill diameters d1, d2 and dn are shown.
- the uppermost drill step has the largest diameter d1, while the underlying drill stages are formed with a smaller diameter d2, dn.
- the number of drill steps is freely selectable and depends on the injector type or intended use. Alternatively, subsequent holes can also be formed further.
- the length of the bores is preferably to be selected such that the largest possible buffer volume is formed but nevertheless sufficiently large wall thicknesses remain for the high-pressure bore.
- the uppermost drilling stage has a length L1 and the subsequent drilling stages have the lengths L2 and Ln, respectively.
- the per se known high pressure accumulator (Rail) of a commercial common rail injection system can be saved.
- the injection system with the injector according to the invention can be made simpler and cheaper.
- the necessary installation space in the vehicle is reduced in an advantageous manner, so that the injection system, in particular in internal combustion engines Can be used with many cylinders and in tight spaces in the engine compartment.
- the individual volumes V1, V2, Vn as a function of operating conditions of the internal combustion engine.
- the uppermost volume V1 could be slightly smaller, the volume V2 larger, and the volume Vn again smaller or the same size. In this way, requirements of the internal combustion engine, for example, in terms of emissions, engine performance and fuel consumption can be optimized.
- a significant further advantage of the invention is also seen in the fact that the pressure waves or vibrations occurring during the injection process are damped by the different bore diameters d1, d2, dn. As the pressure waves on the sidewalls of the individual drill stages are irregularly broken, reflected and absorbed, the attenuation results in a more uniform injection course. In particular, in the multiple injection, in which the fuel is injected in several individual injection pulses in the shortest time intervals, the exact control is particularly important.
- the high pressure bore 2 cache also supports this injection process.
- FIG. 2 shows an enlarged view of a section of the in FIG. 1 explained high-pressure bore 2 of the injector 11.
- the transitions 20 are explained, which form between two adjacent drilling stages.
- the transitions 20 are formed, for example, with a beveled, in particular a conical annular surface.
- the edges of the annular surface 20, which each arise between a drilling step and the annular surface, were further rounded off with a corresponding tool between the two drilling stages d2 and dn, so that a stepless transition from the drilling step d2 to the drilling step dn arises. This prevents the edges from generating new pressure waves or vibrations that could affect the smooth flow of the injection.
- FIG. 3 shows a schematic arrangement for a common rail injection system, as used for example in the diesel injection. It shows the previously described and per se known high-pressure accumulator (rail) 31 to which four injectors 11 are hydraulically connected via four connecting lines 32.
- the size of the high-pressure accumulator 31 and the number of connected injectors 11 depends essentially on the number and the volume of the combustion chambers (cylinder) of the engine type used. In this case, the four injectors 11 are provided for a four-cylinder engine.
- the fuel is pumped by a high-pressure pump 33, which is connected to the high-pressure accumulator 31, at high pressure in the high pressure accumulator 31 and is then available in the individual buffer storage of the connected injectors 11 for injection.
- the high-pressure pump 33 is in turn supplied by a fuel pump 35.
- the fuel pump 35 from a reservoir (in FIG. 3 symbolized by the arrow) the fuel with a lower overpressure via lines 36 and one or more filter units 34 to the high-pressure pump 33.
- the injection holes 5 (FIG. FIG. 1 ) are opened or closed again and thus the injection process can be controlled.
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- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
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- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
Description
Die Erfindung geht nach der Gattung des Hauptanspruchs aus • von einem Injektor für ein Einspritzsystem, das zur Einspritzung von Kraftstoff in einen Verbrennungsmotor ausgebildet ist. Bei einem solchen System ist der Injektor mittels einer Hochdruckleitung mit einem Hochdruckspeicher (Rail) des Einspritzsystems verbunden, der den für die Einspritzung in einen Zylinder des Verbrennungsmotors benötigten Kraftstoff bereitstellt. Der Kraftstoff wird dabei von einer Hochdruckpumpe mit einem bestimmten Betriebsdruck in dem Hochdruckspeicher bereitgestellt. Bei einem Einspritzvorgang, der durch das Abheben der Düsennadel von ihrem Sitz in einer Düseneinheit des Injektors eingeleitet wird, kommt es jedoch zu Druckeinbrüchen und Druckwellen beziehungsweise zu Schwingungen im Einspritzsystem, da die Verbindungsleitungen zwischen dem Hochdruckspeicher und den in der Regel mehreren an dem Hochdruckspeicher angeschlossenen Injektoren relativ lang sind. Diese Effekte sind insbesondere auch bei Mehrfacheinspritzungen mit kurzen Zeitabständen besonders nachteilig, da sie den vorgesehenen Einspritzverlauf beeinträchtigen können.The invention is based on the preamble of the main claim • of an injector for an injection system, which is designed for the injection of fuel into an internal combustion engine. In such a system, the injector is connected by means of a high-pressure line to a high-pressure accumulator (rail) of the injection system, which provides the fuel required for injection into a cylinder of the internal combustion engine. The fuel is provided by a high pressure pump with a certain operating pressure in the high pressure accumulator. In an injection process, which is initiated by the lifting of the nozzle needle from its seat in a nozzle unit of the injector, however, there are pressure drops and pressure waves or vibrations in the injection system, since the connecting lines between the high-pressure accumulator and the more usually connected to the high-pressure accumulator Injectors are relatively long. These effects are particularly disadvantageous, especially in the case of multiple injections with short time intervals, since they can impair the intended course of injection.
Bisher wurde dieses Problem dadurch zu lösen versucht, dass durch konstruktive Maßnahmen die Verbindungsleitungen zwischen dem Hochdruckspeicher und den Injektoren möglichst kurz gewählt wurden. Dies wurde beispielsweise dadurch erreicht, dass der Hochdruckspeicher möglichst in unmittelbarer Nähe zum Zylinderkopf des Verbrennungsmotors angeordnet wurde. Der Kraftstoff wird dann über die verkürzten Verbindungsleitungen und eine in den Injektoren angeordnete Hochdruckbohrung mit konstantem Bohrungsdurchmesser zu der Düseneinheit des Injektors geführt. Diese Anordnung stellt zwar eine gewisse Verbesserung dar, liefert jedoch insbesondere für schnelle Mehrfacheinspritzungen keine zufrieden stellenden Ergebnisse. Aus dem japanischen Patent Abstract
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Der Erfindung liegt die Aufgabe zugrunde, einen Injektor für die Kraftstoffeinspritzung derart weiter zu bilden, dass insbesondere die bei der Mehrfacheinspritzung von Kraftstoff auftretenden Druckeinbrüche, -schwingungen und deren Wechselwirkungen reduziert werden und eine gleichmäßigere Einspritzung ermöglicht wird. Diese Aufgabe wird mit den Merkmalen des Anspruchs 1 gelöst.The invention has for its object to further form an injector for the fuel injection, that in particular the pressure drops, vibrations and their interactions occurring in the multiple injection of fuel can be reduced and a more uniform injection is possible. This object is achieved with the features of
Bei dem erfindungsgemäßen Injektor wird entsprechend der Merkmale des Hauptanspruchs die Hochdruckbohrung, die innerhalb des Injektors angebracht ist, derart ausgebildet, dass sie einen möglichst großen Pufferspeicher für den Kraftstoff bildet. Die Hochdruckbohrung befindet sich in unmittelbarer Nähe zu den Einspritzlöchern der Düseneinheit. Dadurch ist die Länge der Verbindungsleitungen zwischen dem Hochdruckspeicher und den angeschlossenen Injektoren in vorteilhafter Weise als weniger kritisch anzusehen, da der bei der Einspritzung auftretende Druckabfall insbesondere von dem Puffervolumen ausgeglichen werden kann, das durch die erfindungsgemäße Hochdruckbohrung innerhalb des Injektors zur Verfügung gestellt wird. Des weiteren wird als besonders vorteilhaft angesehen, dass durch die erfindungsgemäße Lösung auch die unerwünschten Rückwirkungen auf den Rail und den weiteren Injektoren weitgehend unterdrückt werden. Die Hochdruckbohrung im Injektor ist als Stufenbohrung ausgebildet. Die Stufenbohrung weist dabei zwei oder mehrere Bohrstufen auf. Erfindungsgemäß weist die Hochdruckbohrung wenigstens zwei Bohrdurchmesser auf, wobei nachfolgende Bohrdurchmesser zur Düsenspitze hin enger ausgebildet sind. Es ist eine weitere stufenförmige Bohrung vorgesehen, die parallel zur Hochdruckbohrung angeordnet ist. Die Bohrungsdurchmesser der weiteren Bohrung erweitern sich in Richtung der Düsenspitze.In the injector according to the invention is according to the features of the main claim, the high-pressure bore, which is mounted within the injector, designed such that it forms the largest possible buffer memory for the fuel. The high pressure bore is located in close proximity to the injection holes of the nozzle unit. As a result, the length of the connecting lines between the high-pressure accumulator and the connected injectors can advantageously be regarded as less critical, since the pressure drop occurring during the injection can be compensated in particular by the buffer volume which is made available by the high-pressure bore according to the invention within the injector. Furthermore, it is considered to be particularly advantageous that the unwanted reactions to the rail and the other injectors are largely suppressed by the inventive solution. The high-pressure bore in the injector is designed as a stepped bore. The stepped bore has two or more drill steps. According to the invention, the high-pressure bore has at least two bore diameters, with subsequent bore diameters being narrower towards the nozzle tip. It is provided a further step-shaped bore which is arranged parallel to the high-pressure bore. The bore diameter of the further bore expand in the direction of the nozzle tip.
Dadurch werden die sich in den einzelnen Bohrungsstufen ausbreitenden Druckwellen an den Bohrungswänden unregelmäßig reflektiert, so dass sie sich teilweise gegenseitig kompensieren oder abschwächen. Die Dämpfung der Druckwellen ist dabei um so stärker ausgeprägt, je mehr Bohrstufen an der Hochdruckbohrung angebracht werden können.As a result, the pressure waves propagating in the individual bore stages are reflected irregularly on the bore walls, so that they partially compensate each other or weaken. The damping of the pressure waves is the more pronounced, the more drilling stages can be attached to the high pressure bore.
Gemäß der Erfindung sind die benachbarten Querschnittsflächen der beiden Bohrungen umgekehrt proportional zueinander ausgebildet. Dadurch wird erreicht, dass die Zwischenwand zwischen den beiden Bohrungen stets die gleiche Stärke beibehält. Bei dieser Lösung kann der Injektor insgesamt schlank ausgebildet werden, ohne die notwendige Festigkeit im Hochdruckbereich zu gefährden.According to the invention, the adjacent cross-sectional areas of the two holes are formed inversely proportional to each other. This ensures that the intermediate wall between the two holes always maintains the same strength. In this solution, the injector can be made overall slim, without compromising the necessary strength in the high pressure area.
Durch die in den abhängigen Ansprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen des im Anspruch 1 angegebenen Injektors gegeben.The measures listed in the dependent claims advantageous refinements and improvements of the
Eine besonders vorteilhafte Lösung wird auch darin gesehen, die einzelnen Bohrstufen der Hochdruckbohrung in Fließrichtung des Kraftstoffs beispielsweise jeweils enger auszuführen. Man beginnt am oberen Ende des Injektors mit der weitesten Bohrung und bohrt anschließend die nächste Bohrstufe mit einem kleineren Durchmesser, so dass im Bereich der Düsenspitze die engste Bohrung ausgebildet ist. Eine derartige Anordnung der einzelnen Bohrstufen ist fertigungstechnisch besonders einfach durchführbar. Des weiteren ergibt sich strömungstechnisch gesehen der Vorteil, dass die Druckwellen umso stärker gedämpft werden, je weiter sie sich von ihrem eigentlichen Entstehungsort an der Spitze der Düsennadel entfernt haben.A particularly advantageous solution is also seen, for example, make the individual drilling stages of the high-pressure bore in the flow direction of the fuel, for example, each narrower. Start at the top end of the injector with the widest hole and then drill the next hole with a smaller diameter so that the narrowest hole is formed near the nozzle tip. Such an arrangement of the individual drilling stages is particularly easy to carry out in terms of manufacturing technology. Furthermore, there is the fluidic advantage that the pressure waves are attenuated the more, the further they have moved away from their actual place of origin at the tip of the nozzle needle.
Durch die Länge der einzelnen Bohrstufen in der Hochdruckbohrung kann auf einfache Weise auch das Volumen für den zu speichernden Kraftstoff vorgegeben werden. Dabei scheint es vorteilhaft, das Volumen für die einzelnen Bohrstufen in Fließrichtung des Kraftstoffs kleiner auszubilden. Auf diese Weise erhält man im oberen Teil des Injektors ein relativ großes Speichervolumen für den Kraftstoff, da hier in der Regel genügend Raum für die Aufweitung der Hochdruckbohrung zur Verfügung steht. Bei den unteren Bohrstufen kann dagegen das Volumen so ausgebildet sein, dass die Dämpfungswirkung der Druckwellen besonders gut ausgeprägt ist.Due to the length of the individual drill stages in the high-pressure bore, the volume for the fuel to be stored can also be predetermined in a simple manner. It seems advantageous to make the volume smaller for the individual drilling stages in the flow direction of the fuel. In this way, one obtains in the upper part of the injector, a relatively large storage volume for the fuel, since there is usually enough space for the expansion of the high pressure bore available. In the lower drilling stages, however, the volume can be designed so that the damping effect of the pressure waves is particularly pronounced.
Eine weitere Verbesserung der Dämpfungswirkung für die Druckwellen kann auch dadurch erzielt werden, wenn der Übergang zwischen zwei Bohrstufen mit einer abgeschrägten, insbesondere mit einer kegelförmigen Ringfläche versehen wird. An der Ringfläche werden die Druckwellen ebenfalls gebrochen und teilweise absorbiert.A further improvement of the damping effect for the pressure waves can also be achieved if the transition between two drilling stages is provided with a bevelled, in particular with a conical annular surface. At the ring surface, the pressure waves are also broken and partially absorbed.
Um zu vermeiden, dass sich am Übergang zwischen zwei benachbarten Bohrstufen durch unterschiedliche Strömungsgeschwindigkeiten in den einzelnen Bohrstufen neue Schwingungen ausbilden können, wird in einer alternativen Ausführungsform der Erfindung vorgeschlagen, die Übergänge stufenlos auszubilden. Derartige stufenlose Übergänge, die beispielsweise bogenförmig ausgebildet sind, lassen sich fertigungstechnisch mit einem entsprechend geformten Profilfräser leicht anbringen.In order to avoid that new vibrations can form at the transition between two adjacent drilling stages due to different flow velocities in the individual drilling stages, in an alternative embodiment of the invention it is proposed to design the transitions continuously. Such stepless transitions, which are formed, for example, arcuate, can be easily mounted manufacturing technology with a correspondingly shaped profile cutter.
Günstig erscheint auch, die Druckwellen oder Schwingungen durch unterschiedlich lange Bohrstufen zu beeinflussen.It also seems favorable to influence the pressure waves or vibrations by drilling stages of different lengths.
Des weiteren ist vorteilhaft, dass die beiden Bohrungen parallel zur Längsachse des Injektorgehäuses gebohrt sind und am oberen Ende des Injektorgehäuses eine Zugangsöffnung aufweisen. Über diese Zugangsöffnungen besteht ein guter Zugang zum Anschluss von elektrischen Leitungen für den piezoelektrische Aktor und einer externe Kraftstoffleitung.Furthermore, it is advantageous that the two bores are drilled parallel to the longitudinal axis of the injector and have at the upper end of the injector housing an access opening. These access openings provide good access for the connection of electrical lines for the piezoelectric actuator and an external fuel line.
Der erfindungsgemäße Injektor eignet sich besonders gut für die Verwendung bei einem Common Rail Einspritzsystem. Insbesondere bei der Einspritzung von Diesel-Kraftstoff wird mit einem sehr hohen Kraftstoffdruck gearbeitet, so dass hier bei der Einspritzung die Intensität der Druckwellen und der Schwingungen besonders hoch ist.The injector according to the invention is particularly well suited for use in a common rail injection system. Especially When injecting diesel fuel is working with a very high fuel pressure, so here at Injection intensity of pressure waves and vibrations is especially high.
Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und wird in der Beschreibung nachfolgernd erläutert.
-
zeigt in schematischer Darstellung einen Querschnitt durch einen erfindungsgemäßen Injektor,Figur 1 -
zeigt schematisch zwei Übergang zwischen jeweils zwei Bohrstufen undFigur 2 -
Figur 3 zeigt ein Common Rail Einspritzsystem mit einer Anordnung von vier erfindungsgemäße Injektoren.
-
FIG. 1 shows a schematic representation of a cross section through an injector according to the invention, -
FIG. 2 schematically shows two transition between each two drill stages and -
FIG. 3 shows a common rail injection system with an array of four injectors according to the invention.
In
Im linken Teil von
Die nebeneinander liegenden beiden stufenförmigen Bohrungen 2,10 sind mit ihren Bohrdurchmessern vorzugsweise derart ausgebildet, dass sich bei einem Bohrquerschnitt die beiden benachbarten Querschnittsflächen 14a,14b umgekehrt proportional zueinander verhalten. Neben einer engeren Bohrung liegt somit eine größere Bohrung, so dass vorzugsweise die Summe der Bohrquerschnitte in verschiedenen Stufen vorzugsweise konstant ist. Dadurch wird in vorteilhafter Weise erreicht, dass die Wandstärke zwischen den beiden Bohrungen stets homogen und ausreichend stark ausgeführt ist, um dem hohen Kraftstoffdruck standzuhalten.The adjacent two step-shaped
Der piezoelektrische Aktor 9 ist mit seinem oberen Ende am Injektorgehäuse 1 fest angeordnet. Sein unteres Ende ist beweglich ausgebildet und wirkt bei axialer Längenänderung auf eine Düsennadel 6, die in einer Düseneinheit 11 angeordnet ist. Die Düsenadel 6 kann in Abhängigkeit von Steuersignalen an dem Aktor mit ihrem unteren kegelförmigen Teil Einspritzlöcher 5 der Düseneinheit 11 öffnen oder kraftstoffdicht verschließen.The
Zur Steuerung der Düsennadel 6 sind des weiteren in der Düseneinheit 11 eine Hochdruckkammer 7 sowie eine Zulaufdrossel 3 und eine Ablaufdrossel 8 vorgesehen. Die Zulaufdrossel 3 ist mit einer Zulaufleitung 4 verbunden, die von der Hochdruckbohrung 2 gespeist wird und im wesentlichen den unter hohem Druck stehenden Kraftstoff zur Düsennadel 6 fördert, so dass der Kraftstoff beim Abheben der Düsenadel 6 über die Einspritzlöcher 5 austritt und in den Brennraum eines Verbrennungsmotors eingespritzt werden kann.To control the
Die Hochdruckbohrung 2 bildet mit ihrem gesamten Volumen V1, V2, Vn einen Pufferspeicher für den einzuspritzenden Kraftstoff. Im oberen Teil der Hochdruckbohrung V1 ist an der Zugangsöffnung 13 ein Anschluss für eine externe Verbindungsleitung vorgesehen, die beispielsweise mittels einer Überwurfmutter mit der Hochdruckbohrung 2 fest verbunden werden kann. Über die Verbindungsleitung wird der einzuspritzende Kraftstoff, beispielsweise Benzin oder Diesel zum Injektor 11 gefördert. Der schwarze Pfeil oberhalb der Hochdruckbohrung 2 soll die Fließrichtung des Kraftstoffs anzeigen.The high-
Die Hochdruckbohrung 2 ist im Gegensatz zu einer üblichen zylindrischen Bohrung als mehrfache Stufenbohrung ausgebildet. In
Des weiteren ist vorgesehen, die Länge der Bohrungen vorzugsweise so zu wählen, dass ein möglichst großes Puffervolumen entsteht aber dennoch genügend große Wandstärken für die Hochdruckbohrung verbleiben. Die oberste Bohrstufe weist eine Länge L1 und die nachfolgenden Bohrstufen weisen die Längen L2 beziehungsweise Ln auf. Auf diese Weise kann somit mit sehr einfachen Mitteln für jede Bohrstufe ein bestimmtes Volumen V1, V2, Vn für den zu speichernden Kraftstoff vorgegeben werden, da sich die einzelnen Volumina V nach der trigonometrischen Formel
berechnen lassen (d= Bohrdurchmesser, L= Länge der Bohrung).Furthermore, it is provided that the length of the bores is preferably to be selected such that the largest possible buffer volume is formed but nevertheless sufficiently large wall thicknesses remain for the high-pressure bore. The uppermost drilling stage has a length L1 and the subsequent drilling stages have the lengths L2 and Ln, respectively. In this way, a specific volume V1, V2, Vn can be specified for the fuel to be stored with very simple means for each drilling stage, since the individual volumes V according to the trigonometric formula
let calculate (d = drill diameter, L = length of the bore).
Es wird angestrebt, das Speichervolumen des gesamten Pufferspeichers möglichst groß auszubilden, so dass je nach dem, für welchen Motortyp der Injektor 1 verwendet werden soll, unter Umständen der per se bekannte Hochdruckspeicher (Rail) eines handelsüblichen Common Rail Einspritzsystems eingespart werden kann. Des weiteren kann das Einspritzsystem mit dem erfindungsgemäßen Injektor einfacher und preiswerter hergestellt werden. Hinzu kommt auch, dass sich der notwendige Einbauraum in dem Fahrzeug in vorteilhafter Weise verringert, so dass das Einspritzsystem insbesondere bei Verbrennungsmotoren mit vielen Zylindern sowie bei engen Platzverhältnissen im Motorraum verwendet werden kann.It is desirable to make the storage volume of the entire buffer memory as large as possible, so that depending on the type of engine for which the
In alternativer Ausgestaltung der Erfindung ist vorgesehen, die einzelnen Volumina V1, V2, Vn in Abhängigkeit von Betriebsbedingungen des Verbrennungsmotors auszubilden. Beispielsweise könnte das oberste Volumen V1 etwas kleiner, das Volumen V2 größer und das Volumen Vn wieder kleiner oder gleich groß ausgebildet sein. Auf diese Weise lassen sich Erfordernisse des Verbrennungsmotors beispielsweise hinsichtlich der Emissionen, der Motorleistung und des Kraftstoffverbrauch optimieren.In an alternative embodiment of the invention, it is provided to form the individual volumes V1, V2, Vn as a function of operating conditions of the internal combustion engine. For example, the uppermost volume V1 could be slightly smaller, the volume V2 larger, and the volume Vn again smaller or the same size. In this way, requirements of the internal combustion engine, for example, in terms of emissions, engine performance and fuel consumption can be optimized.
Ein wesentlicher weiterer Vorteil der Erfindung wird auch darin gesehen, dass durch die unterschiedlichen Bohrdurchmesser d1, d2, dn die beim Einspritzvorgang auftretenden Druckwellen beziehungsweise -schwingungen gedämpft werden. Da die Druckwellen an den Seitenwänden der einzelnen Bohrstufen unregelmäßig gebrochen, reflektiert und absorbiert werden, ergibt sich durch die Dämpfung ein gleichmäßigerer Einspritzverlauf. Insbesondere bei der Mehrfacheinspritzung, bei der der Kraftstoff in mehreren einzelnen Einspritzimpulsen in kürzesten Zeitabständen eingespritzt wird, ist die exakte Steuerung besonders wichtig. Der Pufferspeicher der Hochdruckbohrung 2 unterstützt auch dieses Einspritzverfahren.A significant further advantage of the invention is also seen in the fact that the pressure waves or vibrations occurring during the injection process are damped by the different bore diameters d1, d2, dn. As the pressure waves on the sidewalls of the individual drill stages are irregularly broken, reflected and absorbed, the attenuation results in a more uniform injection course. In particular, in the multiple injection, in which the fuel is injected in several individual injection pulses in the shortest time intervals, the exact control is particularly important. The high pressure bore 2 cache also supports this injection process.
Zwischen den beiden Bohrstufen d2 und dn wurden beispielhaft die Kanten der Ringfläche 20, die jeweils zwischen einer Bohrstufe und der Ringsfläche entstehen, mit einem entsprechenden Werkzeug weiter abgerundet, so dass ein stufenloser Übergang von der Bohrstufe d2 zur Bohrstufe dn entsteht. Dadurch wird verhindert, dass an den Kanten neue Druckwellen oder -schwingungen entstehen können, die den gleichmäßigen Verlauf der Einspritzung beeinträchtigen könnten.By way of example, the edges of the
Der Kraftstoff wird von einer Hochdruckpumpe 33, die mit dem Hochdruckspeicher 31 verbunden ist, mit hohem Druck in den Hochdruckspeicher 31 gepumpt und steht dann in den einzelnen Pufferspeichern der angeschlossenen Injektoren 11 zur Einspritzung zur Verfügung. Die Hochdruckpumpe 33 wird ihrerseits von einer Kraftstoffpumpe 35 versorgt. Hierzu fördert die Kraftstoffpumpe 35 aus einem Vorratsbehälter (in
Claims (9)
- Injector for an injection system designed for the injection of fuel into an internal combustion engine, wherein the injector (11) can be connected to a high-pressure accumulator (31) of the injection system via a pressurized fuel line (32), and having a high-pressure bore (2) through which the fuel can be conducted by means of a controllable nozzle needle (6) to injection holes (5) of the injector (11), wherein the high-pressure bore (2) of the injector (11) is designed as a buffer accumulator (V1, V2, Vn) for the pressurized fuel, wherein in the injector housing (1), a further stepped bore (10) is arranged parallel to at least one drilled stage of the high-pressure bore (2), wherein the drilled diameter of the further bore (10) widens from the top downwards, characterized in that, in at least two successive bores of the high-pressure bore (2) and of the stepped bore (10), a cross-sectional area (14a) of the high-pressure bore (2) is formed so as to be inversely proportional to a cross-sectional area (14b) of the further stepped bore (10).
- Injector according to Claim 1, characterized in that the high-pressure bore (2) is formed as a stepped bore.
- Injector according to Claim 1, characterized in that the first drilled diameter (d1) of the high-pressure bore (2) is larger than the second drilled diameter (d2), and the latter is larger than a third drilled diameter (dn) that may be provided.
- Injector according to one of the preceding claims, characterized in that the volume (V1, V2, Vn), which accommodates the fuel, of the individual drilled stages is formed taking into consideration the spatial conditions in the injector (11) and/or operating conditions of an engine.
- Injector according to one of the preceding claims, characterized in that the individual drilled stages have at their transitions (20) a beveled, in particular conical annular surface.
- Injector according to one of the preceding claims, characterized in that the transition (20) between two adjacent drilled stages is designed to be continuous.
- Injector according to one of the preceding claims, characterized in that the individual drilled stages have different lengths (L1, L2, Ln), wherein the lengths (L1, L2, Ln) decrease according to a predefined ratio in the direction of the nozzle tip.
- Injector according to one of the preceding claims, characterized in that the high-pressure bore (2) and/or the further bore (10) are drilled parallel to the longitudinal axis of the injector housing (1) and have an access opening (13) at the top end of the injector housing (1).
- Injector according to one of the preceding claims, characterized in that the injector (11) can be used for a common rail injection system, in particular for the injection of diesel fuel.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10229638 | 2002-07-02 | ||
DE10229638 | 2002-07-02 | ||
PCT/DE2003/001702 WO2004005699A1 (en) | 2002-07-02 | 2003-05-26 | Injector for an injection system |
Publications (2)
Publication Number | Publication Date |
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EP1518050A1 EP1518050A1 (en) | 2005-03-30 |
EP1518050B1 true EP1518050B1 (en) | 2011-10-05 |
Family
ID=30009774
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP03737904A Expired - Fee Related EP1518050B1 (en) | 2002-07-02 | 2003-05-26 | Injector for an injection system |
EP03762417A Expired - Fee Related EP1530680B1 (en) | 2002-07-02 | 2003-06-24 | Method for the production of a module with a moving insert for an injection valve and injection valve |
Family Applications After (1)
Application Number | Title | Priority Date | Filing Date |
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EP03762417A Expired - Fee Related EP1530680B1 (en) | 2002-07-02 | 2003-06-24 | Method for the production of a module with a moving insert for an injection valve and injection valve |
Country Status (2)
Country | Link |
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EP (2) | EP1518050B1 (en) |
WO (2) | WO2004005699A1 (en) |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
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DE102004026171B4 (en) * | 2004-05-28 | 2010-05-20 | Continental Automotive Gmbh | Injector |
US7334570B2 (en) | 2005-04-01 | 2008-02-26 | Achates Power, Inc. | Common rail fuel injection system with accumulator injectors |
DE102005055359A1 (en) | 2005-11-21 | 2007-05-24 | Robert Bosch Gmbh | Intermediate plate for a fuel injector and fuel injector |
DE102006046898A1 (en) * | 2006-10-04 | 2008-04-10 | Robert Bosch Gmbh | Throttle plate for solenoid valve |
FI123513B (en) * | 2010-12-02 | 2013-06-14 | Waertsilae Finland Oy | Fuel supply unit, method for operating it and combustion engine |
AT512439B1 (en) * | 2012-01-26 | 2013-12-15 | Bosch Gmbh Robert | DEVICE FOR INJECTING FUEL IN THE COMBUSTION ENGINE OF AN INTERNAL COMBUSTION ENGINE |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2033051A1 (en) * | 1970-07-03 | 1972-01-05 | Bosch Gmbh Robert | Electrically controlled fuel injection device |
DE2120030A1 (en) * | 1971-04-23 | 1972-11-02 | Robert Bosch Gmbh, 7000 Stuttgart | Fuel injector |
DE2461309A1 (en) * | 1973-12-26 | 1975-07-10 | Isuzu Motors Ltd | FUEL INJECTION DEVICE |
US4526151A (en) * | 1982-03-12 | 1985-07-02 | Mitsubishi Jukogyo Kabushiki Kaisha | Fuel injection device |
JPH0688557A (en) * | 1992-07-24 | 1994-03-29 | Nippondenso Co Ltd | Electromagnetic control fuel injection system |
DE19822503C1 (en) * | 1998-05-19 | 1999-11-25 | Siemens Ag | Control valve for fuel injector |
DE19921242C1 (en) * | 1999-05-07 | 2000-10-26 | Siemens Ag | Method of positioning control drive in common rail fuel injector for motor vehicle internal combustion engine |
DE10055644A1 (en) * | 2000-11-10 | 2002-05-23 | Siemens Ag | Procedure, for adjusting discharge control of fuel injector, consists of measuring spacing between two defined locations and selecting valve piston to suit. |
JP3928362B2 (en) * | 2001-02-14 | 2007-06-13 | 株式会社デンソー | Structure to improve seal surface pressure of fluid transfer device |
US6629650B2 (en) * | 2001-07-10 | 2003-10-07 | Delphi Technologies, Inc. | Fuel injector with integral damper |
-
2003
- 2003-05-26 EP EP03737904A patent/EP1518050B1/en not_active Expired - Fee Related
- 2003-05-26 WO PCT/DE2003/001702 patent/WO2004005699A1/en not_active Application Discontinuation
- 2003-06-24 EP EP03762417A patent/EP1530680B1/en not_active Expired - Fee Related
- 2003-06-24 WO PCT/DE2003/002105 patent/WO2004005704A1/en not_active Application Discontinuation
Also Published As
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WO2004005699A1 (en) | 2004-01-15 |
EP1530680A1 (en) | 2005-05-18 |
EP1530680B1 (en) | 2011-09-28 |
EP1518050A1 (en) | 2005-03-30 |
WO2004005704A1 (en) | 2004-01-15 |
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