EP2294309B1 - Fuel injector - Google Patents
Fuel injector Download PDFInfo
- Publication number
- EP2294309B1 EP2294309B1 EP09765667.2A EP09765667A EP2294309B1 EP 2294309 B1 EP2294309 B1 EP 2294309B1 EP 09765667 A EP09765667 A EP 09765667A EP 2294309 B1 EP2294309 B1 EP 2294309B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- fuel
- chamber
- injector
- fuel injector
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Not-in-force
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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
- 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
- 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
- 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
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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
- F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
- F02M2547/003—Valve inserts containing control chamber and valve piston
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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
- F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
- F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member
- F02M63/008—Hollow valve members, e.g. members internally guided
Definitions
- the invention relates to a fuel injector, in particular a common rail injector, for injecting fuel into a combustion chamber of an internal combustion engine according to the preamble of claim 1.
- the invention has for its object to propose a designed for highest injection pressures fuel injector. Preferably, this should be produced with conventional materials such as C45 steel.
- the invention is based on the idea radially between the injector body (housing part) and one, preferably designed as injector-side rail pressure accumulator (Minirail), high-pressure space to arrange an annulus in which permanently or temporarily a lower fuel pressure than in the high pressure chamber and a higher fuel pressure than in Low pressure range of the fuel injector prevails.
- injector-side rail pressure accumulator Minirail
- the pressure is thus gradually reduced from radially inward to radially outward, so that critical material loads can be avoided.
- injector body designed for well above 2000 bar fuel injectors with conventional materials, such as C45 steel can be performed, especially if the fuel pressure in the annulus does not exceed about 1800 bar. If, for example, the pressure in the high-pressure chamber of the fuel injector is at most 2000 bar, it is generally sufficient if the pressure difference between the annular space and the high-pressure space is approximately 200 bar.
- the pressure in the annular space during operation of the fuel injector is at least half as high as the pressure in the pressure chamber so as not to burden the separation between the annulus and the high-pressure chamber overly.
- a channel passing through the annular space in the radial direction is preferably provided, which is formed, for example, by the injector component which radially bounds the annular space.
- the fuel injector is preferably a so-called low-leakage injector, preferably without a permanent, low-pressure stage which produces a hydraulic closing force acting on the one-part or multi-part injection valve element.
- Such fuel injectors are preferably equipped with a long injection valve element whose axial extent preferably corresponds to at least 50%, preferably at least 60% or 70% of the axial extent of the entire fuel injector.
- An embodiment is particularly preferred in which the high-pressure space in which the injection valve element is accommodated extends in the axial direction as far as a nozzle hole arrangement, wherein the high-pressure space can be subdivided as required into two axially adjacent space sections, between which a closing throttle is arranged.
- the high-pressure chamber extends in the axial direction into a nozzle body which is axially adjacent to the injector body, in which case an embodiment can also be realized in which the pressure-reduced annular space formed between the injector body and the high-pressure chamber extends in the axial direction as far as into the nozzle body.
- a series-connected throttle combination which consists of at least one annulus inlet throttle and at least one annulus flow restrictor, via the annulus inlet throttle under high pressure, in particular at least approximately under rail pressure, standing fuel can flow into the annulus.
- Fuel can again flow out of the annular space in the direction of the low-pressure region of the fuel injector via the annular space drain throttle, the flow cross-sections of the at least one annular space inlet throttle and the at least one annular space throttle being dimensioned such that the desired pressure difference between annular space and high-pressure space is established.
- This pressure reduction mechanism is comparable to the known control room pressure drop, as is known from servo-controlled fuel injectors.
- the annulus pressure in comparison to the control chamber pressure has no influence on the injection behavior of the fuel injector, so that a lower accuracy requirement can be made in the production of the at least one annulus inlet throttle and the at least one annulus flow restrictor. It is particularly advantageous if the at least one annular space inlet throttle and / or the at least one annular space outlet throttle are structurally realized via a guide and / or a leak gap, as a result of which additional working steps for producing throttle bores can be saved. Of course it is also possible to perform at least one of the throttles as a throttle bore.
- the at least one annulus drain can also be replaced or formed by a pressure relief valve to be explained later.
- an embodiment of the fuel injector is not lowered in the pressure in the annulus during the entire operating time against the pressure in the high pressure chamber, but only at times when the pressure in the high pressure chamber exceeds a critical limit. This is usually only the case when the internal combustion engine is operated under full load.
- an embodiment is preferred in which the pressure in the annular space is reduced or reduced compared to the pressure in the high-pressure space only when a minimum pressure, in particular of approximately 1800 bar, is exceeded.
- At least one pressure relief valve is provided in the fuel flow direction between the annulus and the low pressure region of the fuel injector, which is preferably designed as a check valve.
- the pressure relief valve is designed such that it acts as an annular space drain throttle in the open state, so that the desired annular space pressure defines defined. The only temporary opening of the pressure relief valve, the parasitic flow rate can be reduced to an absolute minimum.
- the pressure relief valve comprises at least one spring, the spring force acts on an adjustable valve element.
- the spring is particularly preferably a leaf spring and / or the valve element is a valve ball, in particular designed as a steel ball.
- Structurally elegant is an embodiment in which the valve element is pressed by the spring onto a valve seat which is formed on an injector component which axially delimits the low-pressure region.
- the leaf spring can be clamped axially between a valve clamping screw for securing the injector component in the injector body and the injector component.
- the adjustable valve element of the pressure relief valve is formed by the injector component axially delimiting the low-pressure region, this injector component in this case being subjected to spring force against the injector body by means of a spring, for example an expansion sleeve or a disc spring.
- a spring for example an expansion sleeve or a disc spring.
- the fuel from the annulus with open pressure relief valve flows through an annular leakage gap in the low pressure region of the fuel injector, wherein the leakage gap, preferably axially, is formed between the Injektorbauteil and the injector, wherein to ensure sufficient tightness the closed pressure relief valve on the injector body and / or on the injector component preferably at least one biting edge is formed.
- the spring of the pressure relief valve is arranged such that the bias of the spring and thus the maximum pressure of the annular space is adjustable by means of a valve clamping screw, wherein the valve clamping screw preferably an axial securing for the low pressure region of the Fuel injector in the axial direction limiting injector component.
- Fig. 1 is a trained as a common rail injector fuel injector 1 for injecting fuel into a combustion chamber, not shown, of an internal combustion engine of a motor vehicle.
- a high pressure pump 2 delivers fuel from a reservoir 3 into a high-pressure fuel accumulator 4 (rail).
- this fuel especially diesel or gasoline, under high pressure, of about 2500 bar in this embodiment, stored.
- the fuel injector 1 is connected, among other injectors, not shown, via a supply line 5.
- This supply line 5 leads to a fuel supply connection 6 of the fuel injector 1, which leads via a supply channel 7 to a centric, serving as a minirail high-pressure chamber 8.
- this high-pressure chamber 8 there is essentially rail pressure of about 2500 bar.
- a fuel return port 10 is provided, to which a return line 11 is connected. Via the fuel return connection 10 and the return line 11, a control amount to be explained later as well as a leakage quantity of fuel from a low-pressure region 12 of the fuel injector 1 to the reservoir 3, which is also at low pressure of about 1 to 10 bar, flow off.
- an injection valve element 13 which is integral in the embodiment shown is one recorded axially adjustable.
- the injection valve element 13 is designed in several parts and consists for example of an upper control rod and a lower nozzle needle.
- the injection valve element 13 is guided longitudinally displaceable in a guide bore 14 of a lower nozzle body 15 in the drawing plane.
- axial channels 16 are realized on the outer circumference of the injection valve element 13 in the region of its lower guide as polished sections, via which the fuel can flow in the axial direction down to a nozzle hole arrangement 17 when the injection valve element 13 is open.
- the nozzle body 15 is clamped by means of a union nut 18 with an injector body 19.
- the injector body 19 forms the largest housing part of a housing 20.
- the injection valve element 13 has at its tip 21 a closing surface 22 with which the injection valve element 13 can be brought into tight contact with an injection valve element seat 23 formed inside the nozzle body 15.
- an injection valve element seat 23 formed inside the nozzle body 15.
- the injection valve element 13 abuts against its injection valve element seat 23, ie is in a closed position, the fuel outlet from the nozzle hole arrangement 17 is blocked. If, on the other hand, it is lifted off its injection valve element seat 23, fuel can flow from the high-pressure chamber 8 in the axial direction via the axial channels 16 into a lower nozzle space 24 designed as an annular space and from there past the injection valve element seat 23 to the nozzle hole arrangement 17 and there substantially under high pressure (FIG. Rail pressure) standing in the combustion chamber (not shown) to be injected.
- FOG. Rail pressure high pressure standing in the combustion chamber
- a control chamber 28 is limited, which is supplied via an introduced into the injection valve element 13 inlet throttle 29 with fuel from the high-pressure chamber 8.
- the control chamber 28 is connected via a axially extending in the injector component 27 drain passage 30 with outlet throttle 31 with a valve chamber 32 of a control valve 33 (servo-valve).
- the valve chamber 32 is bounded radially on the outside by a sleeve-shaped control valve element 34.
- the sleeve-shaped control valve element 34 is substantially pressure balanced in its closed position in the axial direction.
- valve chamber 32 is bounded in the axial direction upwards by a pressure pin 35, which is supported axially on the injector cover 9 and is formed as a component separate from the injector component 27.
- a co-operating with the sleeve-shaped control valve element 34 control valve seat 36 (here flat seat) is formed on the injector component 27.
- the sleeve-shaped control valve element 34 is integrally formed with an anchor plate 37 which cooperates with an electromagnetic actuator 38. If this is energized, lifts the control valve member 34 in the axial direction of its control valve seat 36 so that fuel from the valve chamber 32 and subsequently from the control chamber 28 in the low pressure region 12 and from there via the fuel return port 10 and the return line 11 to the reservoir 3 can flow out.
- the flow cross-sections of the inlet throttle 29, which may alternatively be embodied, for example, in the injector component 27, and the outlet throttle 31 are matched to one another such that when the control valve 33 is open, a net outflow of fuel from the control chamber 28 results. with the result that the fuel pressure in the control chamber 33 drops rapidly and thus a hydraulic opening force acts on the injection valve element 13, which lifts in sequence from its injection valve element seat 23 and the nozzle hole assembly 17 for injecting fuel into the combustion chamber releases.
- the energization of the electromagnetic actuator 38 is interrupted. With a one end on a shoulder of the pressure pin 35 and the other end on an upper end face of the armature plate 37 supporting the control closing spring 39, the sleeve-shaped control valve member 34 is moved back to its control valve seat 36.
- the fuel flowing in through the inlet throttle 29 causes an increase in pressure in the control chamber 28, with the result that the injection valve element 13 is moved back onto the injection valve element seat 23 assisted by a closing spring 40.
- the closing spring 40 is arranged in the projecting into the nozzle body 15 high-pressure chamber 8 and is supported at one end on a lower end face of the Injektorbauteils 27 and the other end on a peripheral collar 41 of the injection valve element 13.
- the axial channels 16 may be formed as throttle channels, thus reducing the pressure in the nozzle chamber 24 in comparison to the high pressure chamber 8 something.
- the pressure is advantageously reduced by only about 100 to 200 bar, so that the nozzle chamber 24 and the high-pressure chamber 8 can be regarded as a common space.
- annular space 42 In order to allow the injector body 19 not to be excessively stressed in pressure and subsequently made of conventional steels such as C45, see US Pat Fig. 1 shown fuel injector 1 an annular space 42 before, which is located radially between the high-pressure chamber 8 and the injector 19.
- the annular space 42 extends in the axial direction over the largest part of the axial extent of the injector body 19 and, if necessary, can also project axially into the nozzle body 15.
- the annular space 42 is bounded radially inwards with respect to the high-pressure chamber 8 by a tubular portion 43 of the injector component 27.
- a stepped bore 44 is introduced for this purpose, which limits the control chamber 28 in its upper end in the drawing plane.
- the pressure in the annular space 42 is permanently lower than in the high pressure chamber 8. Die Flow cross sections of the chokes to be explained below are adjusted so that the pressure in the annular space 42 does not exceed 1800 bar. As a result, the pressure load of the injector body 19, at least in pressure-critical Reduced areas over most of its axial extent.
- the supply channel 7 is partially formed as a bore in a screwed to the injector body 19, sleeve-shaped connection part 60, wherein the supply channel 7 continues in the radial direction in the high-pressure chamber 8, while the annular space 42 passes through in the radial direction and is sealed against this ,
- the injector component 22 is provided with a positive diameter jump 45 (circumferential collar) in the region of the supply channel 7, into which openings axially extending at a distance from the supply channel 7 are introduced, via which the fuel is introduced from a lower section of the annular space 42 into an upper section of the Annulus 42 can flow unhindered and preferably unthrottled.
- FIG. 1 shown Injektorbauteil 27 does not necessarily have to be made in one piece.
- the annular space 42 is bounded by the plate section 47 of the injector component 27, which, as mentioned above, can also be embodied as a separate component. This is pressed by a valve clamping screw 48 against an annular shoulder 49 of the injector body 19.
- a sealing element 50 In the axial direction down the annular space 42 is bounded by a sealing element 50, which is located radially between the lower portion of the tubular portion 43 of the Injektorbauteils 27 and the injector body 19.
- Fig. 1 further results can under high pressure of in the illustrated embodiment 2500 bar standing fuel flow in the radial direction via an annular space inlet throttle 51 into the annular space 42. From there, fuel flows via an annular component outlet throttle 52 provided in the injector component 27 into the low-pressure region 12 of the fuel injector 1.
- the flow cross-sections of the annular space inlet throttle 51 and the annular space flow restrictor 52 are matched to one another in such a way that the pressure in the annular space 42, as explained above, a Maximum pressure of 1800 bar does not exceed, whereby the pressure load of the injector body 19 is significantly reduced.
- the annular space inlet throttle 51 and the annular space drain throttle 52 are designed as throttle bores, with alternative manufacturing options can be realized. Since the pressure in the annular space 42 has no influence on the injection behavior of the fuel injector 1, the annular space inlet throttle 51 and the annular space drain throttle 52 can be made very small, whereby the necessary for the pressure reduction parasitic flow rate is low. On the other hand, the pressure in the annular space 42 does not react to highly dynamic pressure changes in the high-pressure space 8 serving as a minirail, but only to function-related rail pressure changes.
- the pressure in the annular space 42 in the embodiment according to Fig. 2 not permanently reduced compared to the high-pressure chamber 8. This is due to the fact that the fuel from the annular space 42 can only temporarily flow into the low-pressure region 12 of the fuel injector 1.
- the influx from the high-pressure chamber 8 in the annular space 42 is also at the in Fig. 2 shown embodiment via a designed as a throttle bore annular space inlet throttle 51.
- the annular space drain throttle 52 is in the embodiment according to Fig. 2 formed by a designed as a check valve pressure relief valve 53 which is designed so that this opens only in the direction of low pressure area 12 when a minimum pressure in the annular space 42 is exceeded.
- the overpressure valve 53 comprises a valve element 54 designed as a steel ball, which is acted upon by a spring 55 designed as a flat spring in the direction of a valve seat 56 formed on the injector component 27, more precisely on the plate section 47.
- a spring 55 designed as a flat spring in the direction of a valve seat 56 formed on the injector component 27, more precisely on the plate section 47.
- the underside of the valve element 54 via a channel 57 in the injector 27 is permanently in communication with the annulus volume of the annular space 42.
- the pressure relief valve 53 is dimensioned so that the throttling action of the pressure relief valve 53 has the desired level of pressure reduction in the annular space 42 result.
- annular space inlet throttle 51 is not formed as a throttle bore but as a leakage gap between a peripheral collar 58 of the tubular portion 43 of the injector 27 and the injector 19.
- a further annular space inlet throttle 51 is provided between the upper positive diameter jump 45 (circumferential collar) and the injector body 19.
- annular space drain throttle 52 no throttle channel is provided as annular space drain throttle 52.
- This is formed by the pressure relief valve 53, via which the annular space 42 with the low pressure region 12 of the fuel injector 1 is connectable.
- the valve element 54 is formed by the plate portion 47 of the Injektorbauteils 27. This is in the closed state of the pressure relief valve 53 on the annular shoulder 49 of the injector body 9 on.
- the overpressure valve 53 is open, the plate section 47 is adjusted in the axial direction upward, so that an annular gap is formed axially between the plate section 47 and a biting edge 59 of the injector body 19, wherein the flow cross-section of the annular gap is adjusted so that the desired throttling is achieved.
- the plate section 47 only lifts off from its valve seat 56 formed by the biting edge 59 on the injector body 19 when the pressure force acting on it exceeds the spring force of a spring 55 designed as a plate spring, which is supported in the axial direction upward on the valve clamping screw 48.
- the spring 55 tends to press the plate portion 47 axially downwardly against the annular shoulder 49 of the injector body 19.
Description
Die Erfindung betrifft einen Kraftstoff-injektor, insbesondere einen Common-Rail-Injektor, zum Einspritzen von Kraftstoff in einen Brennraum einer Brennkraftmaschine gemäß dem Oberbegriff des Anspruchs 1.The invention relates to a fuel injector, in particular a common rail injector, for injecting fuel into a combustion chamber of an internal combustion engine according to the preamble of
Die Einhaltung von Schadstoffgrenzwerten hat bei der Entwicklung von Verbrennungsmotoren die höchste Priorität. Gerade das Common-Rail-Einspritzsystem hat einen entscheidenden Beitrag zur Reduzierung der Schadstoffe geleistet. Der Vorteil der Common-Rail-Systeme liegt in ihrer Unabhängigkeit des Einspritzdrucks von Drehzahl und Last. Für die Einhaltung zukünftiger Abgaswerte ist jedoch gerade bei Dieselmotoren eine signifikante Erhöhung des Einspritzdruckes notwendig.Compliance with emission limits has the highest priority in the development of internal combustion engines. Especially the common rail injection system has made a decisive contribution to the reduction of pollutants. The advantage of the common-rail systems lies in their independence of the injection pressure of speed and load. For the compliance with future exhaust gas values, however, a significant increase of the injection pressure is necessary, especially for diesel engines.
Neueste Kraftstoff-Injektoren, wie beispielsweise der in der
Daher müssen zur Herstellung von Kraftstoff-Injektoren für höchste Einspritzdrücke von wesentlich größer als 2000 bar äußerst kostenintensive Spezialwerkstoffe eingesetzt werden, wobei nicht nur der Werkstoff an sich, sondern auch dessen Bearbeitung mit hohen Kosten verbunden ist.Therefore, for the production of fuel injectors for highest injection pressures of much greater than 2000 bar extremely expensive specialty materials must be used, whereby not only the material itself, but also its processing is associated with high costs.
Der Erfindung liegt die Aufgabe zugrunde, einen für höchste Einspritzdrücke ausgelegten Kraftstoff-Injektor vorzuschlagen. Bevorzugt soll dieser mit herkömmlichen Werkstoffen wie beispielsweise C45-Stahl herstellbar sein.The invention has for its object to propose a designed for highest injection pressures fuel injector. Preferably, this should be produced with conventional materials such as C45 steel.
Diese Aufgabe wird mit einem Kraftstoff-Injektor mit den Merkmalen des Anspruchs 1 gelöst. Vorteilhafte Weiterbildungen der Erfindung sind in den Unteransprüchen angegeben.This object is achieved with a fuel injector having the features of
Der Erfindung liegt der Gedanke zugrunde, radial zwischen dem Injektorkörper (Gehäuseteil) und einem, vorzugsweise als injektorseitiger Raildruckspeicher (Minirail) ausgebildeten, Hochdruckraum einen Ringraum anzuordnen, in dem dauerhaft oder zeitweise ein geringerer Kraftstoff-Druck als im Hochdruckraum und ein höherer Kraftstoffdruck als im Niederdruckbereich des Kraftstoff-Injektors herrscht. Auf diese Weise wird erreicht, dass auf die den Ringraum radial innen begrenzende Umfangswand lediglich der Differenzdruck aus dem Kraftstoff-Druck im Hochdruckraum und dem Kraftstoff-Druck im Ringraum wirkt. Die auf den außen angeordneten Injektorkörper wirkende Belastung ist ebenfalls reduziert, da dieser lediglich dem Kraftstoff-Druck im Ringraum ausgesetzt ist. Durch das Vorsehen eines Ringraums mit geringerem Hydraulikdruck als der Hochdruckraum wird der Druck also von radial innen nach radial außen stufenweise abgebaut, so dass kritische Materialbelastungen vermieden werden können. Auf diese Weise ist es möglich, dass auch Injektorkörper von für weit über 2000 bar ausgelegte Kraftstoff-Injektoren mit herkömmlichen Werkstoffen, wie C45-Stahl, ausgeführt werden können, insbesondere dann, wenn der Kraftstoff-Druck im Ringraum etwa 1800 bar nicht überschreitet. Soll der Druck im Hochdruckraum des Kraftstoff-Injektors beispielsweise maximal 2000 bar betragen, ist es in der Regel ausreichend, wenn die Druckdifferenz zwischen dem Ringraum und dem Hochdruckraum etwa 200 bar beträgt.The invention is based on the idea radially between the injector body (housing part) and one, preferably designed as injector-side rail pressure accumulator (Minirail), high-pressure space to arrange an annulus in which permanently or temporarily a lower fuel pressure than in the high pressure chamber and a higher fuel pressure than in Low pressure range of the fuel injector prevails. In this way, it is achieved that only the differential pressure from the fuel pressure in the high-pressure chamber and the fuel pressure in the annular space acts on the annular space bounding the annular space radially inside. The load acting on the outer injector body is also reduced because it is only exposed to the fuel pressure in the annulus. By providing an annular space with a lower hydraulic pressure than the high-pressure space, the pressure is thus gradually reduced from radially inward to radially outward, so that critical material loads can be avoided. In this way, it is possible that injector body designed for well above 2000 bar fuel injectors with conventional materials, such as C45 steel, can be performed, especially if the fuel pressure in the annulus does not exceed about 1800 bar. If, for example, the pressure in the high-pressure chamber of the fuel injector is at most 2000 bar, it is generally sufficient if the pressure difference between the annular space and the high-pressure space is approximately 200 bar.
Besonders bevorzugt ist eine Ausführungsform des Kraftstoff-Injektors, bei der der Druck im Ringraum während des Betriebs des Kraftstoffs-Injektors mindestens halb so hoch ist wie der Druck im Druckraum um somit die Abtrennung zwischen dem Ringraum und dem Hochdruckraum nicht über Gebühr zu belasten.Particularly preferred is an embodiment of the fuel injector, wherein the pressure in the annular space during operation of the fuel injector is at least half as high as the pressure in the pressure chamber so as not to burden the separation between the annulus and the high-pressure chamber overly.
Besonders bevorzugt ist eine Ausführungsform, bei der der aus dem Kraftstoff-Versorgungsanschluss von einem externen Kraftstoff-Hochdruckspeicher (Rail) zuströmende Kraftstoff unmittelbar in den Hochdruckraum geleitet wird. Bevorzugt ist hierzu ein den Ringraum in radialer Richtung durchsetzender Kanal vorgesehen, der beispielsweise von dem den Ringraum radial innen begrenzenden Injektorbauteil gebildet ist.Particularly preferred is an embodiment in which the fuel flowing in from the fuel supply connection from an external high-pressure fuel accumulator (rail) is conducted directly into the high-pressure space. For this purpose, a channel passing through the annular space in the radial direction is preferably provided, which is formed, for example, by the injector component which radially bounds the annular space.
Bevorzugt handelt es sich bei dem Kraftstoff-Injektor um einen sogenannten leckagearmen Injektor, vorzugsweise ohne dauerhafte, auf das ein- oder mehrteilig ausgebildete Einspritzventilelement wirkende, eine hydraulische Schließkraft erzeugende, Niederdruckstufe. Derartige Kraftstoff-Injektoren werden bevorzugt mit einem langen Einspritzventilelement ausgestattet, dessen Axialerstreckung bevorzugt mindestens 50%, vorzugsweise mindestens 60% oder 70% der Axialerstreckung des gesamten Kraftstoff-Injektors entspricht. Dabei ist eine Ausführungsform besonders bevorzugt, bei der sich der Hochdruckraum, in dem das Einspritzventilelement aufgenommen ist, in axialer Richtung bis zu einer Düsenlochanordnung erstreckt, wobei der Hochdruckraum bei Bedarf in zwei axial benachbarte Raumabschnitte unterteilt werden kann, zwischen denen eine Schließdrossel angeordnet ist, um den Kraftstoff-Druck im Bereich einer Einspritzventilelementspitze etwas, beispielsweise um 100 bis 200 bar, abzusenken, um hierdurch eine hydraulische Schließkraftkomponente zu erzeugen. Besonders bevorzugt ist eine Ausführungsform, bei der sich der Hochdruckraum in axialer Richtung bis in einen axial zu dem Injektorkörper benachbarten Düsenkörper hineinerstreckt, wobei in diesem Fall auch eine Ausführungsform realisierbar ist, bei der sich der zwischen dem Injektorkörper und dem Hochdruckraum ausgebildete, druckreduzierte Ringraum in axialer Richtung bis in den Düsenkörper hineinerstreckt.The fuel injector is preferably a so-called low-leakage injector, preferably without a permanent, low-pressure stage which produces a hydraulic closing force acting on the one-part or multi-part injection valve element. Such fuel injectors are preferably equipped with a long injection valve element whose axial extent preferably corresponds to at least 50%, preferably at least 60% or 70% of the axial extent of the entire fuel injector. An embodiment is particularly preferred in which the high-pressure space in which the injection valve element is accommodated extends in the axial direction as far as a nozzle hole arrangement, wherein the high-pressure space can be subdivided as required into two axially adjacent space sections, between which a closing throttle is arranged. to slightly lower the fuel pressure in the region of an injection valve element tip, for example by 100 to 200 bar, to thereby produce a hydraulic closing force component. Particularly preferred is an embodiment in which the high-pressure chamber extends in the axial direction into a nozzle body which is axially adjacent to the injector body, in which case an embodiment can also be realized in which the pressure-reduced annular space formed between the injector body and the high-pressure chamber extends in the axial direction as far as into the nozzle body.
Zur Erzielung der benötigten Druckabsenkung im Ringraum ist es denkbar eine in Reihe geschaltete Drosselkombination zu realisieren, die aus mindestens einer Ringraumzulaufdrossel und mindestens einer Ringraumablaufdrossel besteht, wobei über die Ringraumzulaufdrossel unter Hochdruck, insbesondere zumindest näherungsweise unter Raildruck, stehender Kraftstoff in den Ringraum zuströmen kann. Über die Ringraumablaufdrossel kann wiederum Kraftstoff aus dem Ringraum in Richtung des Niederdruckbereichs des Kraftstoff-Injektors abströmen, wobei die Durchflussquerschnitte der mindestens einen Ringraumzulaufdrossel und der mindestens einen Ringraumablaufdrossel derart dimensioniert sind, dass sich der gewünschte Druckunterschied zwischen Ringraum und Hochdruckraum einstellt. Dieser Druckabsenkungsmechanismus ist vergleichbar zur an sich bekannten Steuerraumdruckabsenkung, wie diese von servogesteuerten Kraftstoff-Injektoren bekannt ist. Der wesentliche Unterschied besteht darin, dass der Ringraumdruck im Vergleich zum Steuerraumdruck keinen Einfluss auf das Einspritzverhalten des Kraftstoff-Injektors hat, so dass an die mindestens eine Ringraumzulaufdrossel und die mindestens eine Ringraumablaufdrossel eine geringere Genauigkeitsanforderung bei der Fertigung gestellt werden kann. Besonders vorteilhaft ist es, wenn die mindestens eine Ringraumzulaufdrossel und/oder die mindestens eine Ringraumablaufdrossel konstruktiv über eine Führung und/oder einen Leckspalt realisiert sind, wodurch zusätzliche Arbeitsschritte zur Herstellung von Drosselbohrungen eingespart werden können. Selbstverständlich ist es auch möglich zumindest eine der Drosseln als Drosselbohrung auszuführen.To achieve the required pressure reduction in the annulus, it is conceivable to realize a series-connected throttle combination, which consists of at least one annulus inlet throttle and at least one annulus flow restrictor, via the annulus inlet throttle under high pressure, in particular at least approximately under rail pressure, standing fuel can flow into the annulus. Fuel can again flow out of the annular space in the direction of the low-pressure region of the fuel injector via the annular space drain throttle, the flow cross-sections of the at least one annular space inlet throttle and the at least one annular space throttle being dimensioned such that the desired pressure difference between annular space and high-pressure space is established. This pressure reduction mechanism is comparable to the known control room pressure drop, as is known from servo-controlled fuel injectors. The essential difference is that the annulus pressure in comparison to the control chamber pressure has no influence on the injection behavior of the fuel injector, so that a lower accuracy requirement can be made in the production of the at least one annulus inlet throttle and the at least one annulus flow restrictor. It is particularly advantageous if the at least one annular space inlet throttle and / or the at least one annular space outlet throttle are structurally realized via a guide and / or a leak gap, as a result of which additional working steps for producing throttle bores can be saved. Of course it is also possible to perform at least one of the throttles as a throttle bore.
Die mindestens eine Ringraumablaufdrossel kann auch durch ein später noch zu erläuterndes Überdruckventil ersetzt bzw. gebildet werden.The at least one annulus drain can also be replaced or formed by a pressure relief valve to be explained later.
Besonders bevorzugt ist eine Ausführungsform des Kraftstoff-Injektors, bei der Druck im Ringraum nicht während der gesamten Betriebszeit gegenüber dem Druck im Hochdruckraum abgesenkt wird, sondern nur zu Zeiten, in denen der Druck im Hochdruckraum eine kritische Grenze überschreitet. Dies ist in der Regel nur dann der Fall, wenn der Verbrennungsmotor unter Volllast betrieben wird. Anders ausgedrückt ist eine Ausführungsform bevorzugt, bei der der Druck im Ringraum im Vergleich zum Druck im Hochdruckraum erst ab Überschreiten eines Mindestdrucks, insbesondere von etwa 1800 bar, reduziert ist bzw. reduziert wird.Particularly preferred is an embodiment of the fuel injector, is not lowered in the pressure in the annulus during the entire operating time against the pressure in the high pressure chamber, but only at times when the pressure in the high pressure chamber exceeds a critical limit. This is usually only the case when the internal combustion engine is operated under full load. In other words, an embodiment is preferred in which the pressure in the annular space is reduced or reduced compared to the pressure in the high-pressure space only when a minimum pressure, in particular of approximately 1800 bar, is exceeded.
Diese Forderung kann konstruktiv dadurch realisiert werden, dass in Kraftstoffströmungsrichtung zwischen dem Ringraum und dem Niederdruckbereich des Kraftstoff-Injektors mindestens ein Überdruckventil vorgesehen ist, welches bevorzugt als Rückschlagventil ausgebildet ist. Dabei ist eine Ausführungsform besonders bevorzugt, bei der das Überdruckventil derart ausgelegt ist, dass es im geöffneten Zustand als Ringraumablaufdrossel wirkt, so dass sich der gewünschte Ringraumdruck definiert einstellt. Durch die nur zeitweise Öffnung des Überdruckventils kann die parasitäre Ablaufmenge auf ein absolutes Minimum reduziert werden.This requirement can be realized constructively in that at least one pressure relief valve is provided in the fuel flow direction between the annulus and the low pressure region of the fuel injector, which is preferably designed as a check valve. In this case, an embodiment is particularly preferred in which the pressure relief valve is designed such that it acts as an annular space drain throttle in the open state, so that the desired annular space pressure defines defined. The only temporary opening of the pressure relief valve, the parasitic flow rate can be reduced to an absolute minimum.
Bevorzugt umfasst das Überdruckventil mindestens eine Feder, die ein verstellbares Ventilelement federkraftbeaufschlagt. Besonders bevorzugt handelt es sich bei der Feder um eine Blattfeder und/oder bei dem Ventilelement um eine, insbesondere als Stahlkugel ausgebildete, Ventilkugel. Konstruktiv elegant ist eine Ausführungsform, bei der das Ventilelement von der Feder auf einen an einem den Niederdruckbereich axial begrenzenden Injektorbauteil ausgebildeten Ventilsitz gepresst wird. Dabei kann die Blattfeder beispielsweise axial zwischen einer Ventilspannschraube zum Festlegen des Injektorbauteils im Injektorkörper und dem Injektorbauteil geklemmt werden.Preferably, the pressure relief valve comprises at least one spring, the spring force acts on an adjustable valve element. The spring is particularly preferably a leaf spring and / or the valve element is a valve ball, in particular designed as a steel ball. Structurally elegant is an embodiment in which the valve element is pressed by the spring onto a valve seat which is formed on an injector component which axially delimits the low-pressure region. In this case, for example, the leaf spring can be clamped axially between a valve clamping screw for securing the injector component in the injector body and the injector component.
Alternativ ist eine Ausführungsform realisierbar, bei der das verstellbare Ventilelement des Überdruckventils von dem den Niederdruckbereich axial begrenzenden Injektorbauteil gebildet ist, wobei dieses Injektorbauteil in diesem Fall mittels einer Feder, beispielsweise einer Dehnhülse oder einer Tellerfeder, gegen den Injektorkörper federkraftbeaufschlagt ist. Besonders bevorzugt ist es dabei, wenn der Kraftstoff aus dem Ringraum bei geöffnetem Überdruckventil durch einen ringförmigen Leckagespalt in den Niederdruckbereich des Kraftstoff-Injektors strömt, wobei der Leckagespalt, vorzugsweise axial, zwischen dem Injektorbauteil und dem Injektorkörper gebildet ist, wobei zur Gewährleistung einer ausreichenden Dichtheit des geschlossenen Überdruckventils am Injektorkörper und/oder am Injektorbauteil bevorzugt mindestens eine Beißkante ausgebildet ist.Alternatively, an embodiment can be realized in which the adjustable valve element of the pressure relief valve is formed by the injector component axially delimiting the low-pressure region, this injector component in this case being subjected to spring force against the injector body by means of a spring, for example an expansion sleeve or a disc spring. It is particularly preferred if the fuel from the annulus with open pressure relief valve flows through an annular leakage gap in the low pressure region of the fuel injector, wherein the leakage gap, preferably axially, is formed between the Injektorbauteil and the injector, wherein to ensure sufficient tightness the closed pressure relief valve on the injector body and / or on the injector component preferably at least one biting edge is formed.
Bevorzugt ist die Feder des Überdruckventils derart angeordnet, dass die Vorspannung der Feder und damit der maximale Druck des Ringraums mittels einer Ventilspannschraube einstellbar ist, wobei die Ventilspannschraube vorzugsweise eine Axialsicherung für das den Niederdruckbereich des Kraftstoff-Injektors in axialer Richtung begrenzende Injektorbauteil ist.Preferably, the spring of the pressure relief valve is arranged such that the bias of the spring and thus the maximum pressure of the annular space is adjustable by means of a valve clamping screw, wherein the valve clamping screw preferably an axial securing for the low pressure region of the Fuel injector in the axial direction limiting injector component.
Weitere Vorteile, Merkmale und Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung bevorzugter Ausführungsbeispiele sowie anhand der Zeichnungen. Diese zeigen in:
- Fig. 1:
- eine erste Ausführungsform eines Kraftstoff-Injektors mit einem zwischen einem Hochdruckraum und einem Injektorkörper ausgebildeten Ringraum in dem der Kraftstoff-Druck im Betrieb des Kraftstoff-Injektors gegenüber dem Kraftstoff-Druck im Hochdruckraum dauerhaft reduziert ist,
- Fig. 2:
- eine alternative, zweite Ausführungsform eines Kraftstoff-Injektors mit einem zwischen Ringraum und Niederdruckbereich des Kraftstoff-Injektors angeordneten, als Rückschlagventil ausgebildeten Überdruckventils, das die Aufgabe hat, den Kraftstoff-Druck im Ringraum nur bei Überschreiten eines Mindestdrucks zu reduzieren und
- Fig. 3:
- ein weiteres alternatives, drittes Ausführungsbeispiel eines Kraftstoff-Injektors, bei dem das Ventilelement des Überdruckventils von einem eine Steuerkammer begrenzenden Injektorbauteil gebildet ist.
- Fig. 1:
- a first embodiment of a fuel injector with an annular space formed between a high-pressure chamber and an injector body in which the fuel pressure during operation of the fuel injector compared to the fuel pressure in the high-pressure chamber is permanently reduced,
- Fig. 2:
- an alternative, second embodiment of a fuel injector arranged between the annulus and low pressure region of the fuel injector designed as a check valve overpressure valve, which has the task to reduce the fuel pressure in the annulus only when a minimum pressure is exceeded and
- 3:
- a further alternative, third embodiment of a fuel injector, wherein the valve element of the pressure relief valve is formed by a control chamber bounding injector component.
In den Figuren sind gleiche Bauteile und Bauteile mit der gleichen Funktion mit den gleichen Bezugszeichen gekennzeichnet.In the figures, the same components and components with the same function with the same reference numerals.
In
Innerhalb des Hochdruckraums 8 ist ein in dem gezeigten Ausführungsbeispiel einteiliges Einspritzventilelement 13 axial verstellbar aufgenommen. Alternativ ist das Einspritzventilelement 13 mehrteilig ausgeführt und besteht beispielsweise aus einer oberen Steuerstange und einer unteren Düsennadel.Within the high-
Das Einspritzventilelement 13 ist längsverschieblich in einer Führungsbohrung 14 eines in der Zeichnungsebene unteren Düsenkörpers 15 geführt. Dabei sind am Außenumfang des Einspritzventilelementes 13 im Bereich seiner unteren Führung Axialkanäle 16 als Anschliffe realisiert, über die der Kraftstoff bei geöffnetem Einspritzventilelement 13 in axialer Richtung nach unten zu einer Düsenlochanordnung 17 strömen kann. Der Düsenkörper 15 ist mittels einer Überwurfmutter 18 mit einem Injektorkörper 19 verspannt. Der Injektorkörper 19 bildet bei dem gezeigten Ausführungsbeispiel das größte Gehäuseteil eines Gehäuses 20.The
Das Einspritzventilelement 13 weist an seiner Spitze 21 eine Schließfläche 22 auf, mit der das Einspritzventilelement 13 in dichte Anlage an einen innerhalb des Düsenkörpers 15 ausgebildeten Einspritzventilelementsitz 23 bringbar ist. Wenn das Einspritzventilelement 13 an seinem Einspritzventilelementsitz 23 anliegt, d.h. sich in einer Schließstellung befindet, ist der Kraftstoffaustritt aus der Düsenlochanordnung 17 gesperrt. Ist es dagegen von seinem Einspritzventilelementsitz 23 abgehoben, kann Kraftstoff aus dem Hochdruckraum 8 in axialer Richtung über die Axialkanäle 16 in einen unteren, als Ringraum ausgebildeten Düsenraum 24 und von dort aus am Einspritzventilelementsitz 23 vorbei zur Düsenlochanordnung 17 strömen und dort im Wesentlichen unter Hochdruck (Raildruck) stehend in den Brennraum (nicht gezeigt) gespritzt werden.The
Von einer oberen Stirnseite 25 des Einspritzventilelements 13 und einem Steuerraumabschnitt 26 eines Injektorbauteils 27 wird eine Steuerkammer 28 begrenzt, die über eine in das Einspritzventilelement 13 eingebrachte Zulaufdrossel 29 mit Kraftstoff aus dem Hochdruckraum 8 versorgt wird. Die Steuerkammer 28 ist über einen axial im Injektorbauteil 27 verlaufenden Ablaufkanal 30 mit Ablaufdrossel 31 mit einer Ventilkammer 32 eines Steuerventils 33 (Servo-Ventil) verbunden. Die Ventilkammer 32 wird radial außen von einem hülsenförmigen Steuerventilelement 34 begrenzt. Das hülsenförmige Steuerventilelement 34 ist in seiner Schließstellung in axialer Richtung im Wesentlichen druckausgeglichen. Die Ventilkammer 32 wird in axialer Richtung nach oben von einem Druckstift 35 begrenzt, der sich axial am Injektordeckel 9 abstützt und als von dem Injektorbauteil 27 separates Bauteil ausgebildet ist. Ein mit dem hülsenförmigen Steuerventilelement 34 zusammenwirkender Steuerventilsitz 36 (hier Flachsitz) ist am Injektorbauteil 27 ausgebildet.From an upper end face 25 of the
Das hülsenförmige Steuerventilelement 34 ist einteilig mit einer Ankerplatte 37 ausgebildet, die mit einem elektromagnetischen Aktuator 38 zusammenwirkt. Wird dieser bestromt, hebt das Steuerventilelement 34 in axialer Richtung von seinem Steuerventilsitz 36 ab, so dass Kraftstoff aus der Ventilkammer 32 und in der Folge aus der Steuerkammer 28 in den Niederdruckbereich 12 und von dort aus über den Kraftstoffrücklaufanschluss 10 und die Rücklaufleitung 11 zum Vorratsbehälter 3 abströmen kann. Dabei sind die Durchflussquerschnitte der Zulaufdrossel 29, die alternativ beispielsweise auch im Injektorbauteil 27 ausgebildet sein kann, und der Ablaufdrossel 31 derart aufeinander abgestimmt, dass bei geöffnetem Steuerventil 33 ein Nettoabfluss von Kraftstoff aus der Steuerkammer 28 resultiert, mit der Folge, dass der Kraftstoffdruck in der Steuerkammer 33 rapide abfällt und somit eine hydraulische Öffnungskraft auf das Einspritzventilelement 13 wirkt, welches in der Folge von seinem Einspritzventilelementsitz 23 abhebt und die Düsenlochanordnung 17 zum Einspritzen von Kraftstoff in den Brennraum freigibt.The sleeve-shaped
Zum Beenden des Einspritzvorgangs wird die Bestromung des elektromagnetischen Aktuators 38 unterbrochen. Mit einer sich einenends an einer Schulter des Druckstiftes 35 und anderenends an einer oberen Stirnseite der Ankerplatte 37 abstützenden Steuerschließfeder 39 wird das hülsenförmige Steuerventilelement 34 zurück auf seinen Steuerventilsitz 36 bewegt. Der durch die Zulaufdrossel 29 nachströmende Kraftstoff sorgt für eine Druckerhöhung in der Steuerkammer 28 mit der Folge, dass das Einspritzventilelement 13 unterstützt durch eine Schließfeder 40 zurück auf den Einspritzventilelementsitz 23 bewegt wird. Die Schließfeder 40 ist dabei in dem in den Düsenkörper 15 hineinragenden Hochdruckraum 8 angeordnet und stützt sich einenends an einer unteren Stirnseite des Injektorbauteils 27 und anderenends an einem Umfangsbund 41 des Einspritzventilelementes 13 ab. Zum Erzeugen einer ausreichend hohen Schließkraft können die Axialkanäle 16 als Drosselkanäle ausgebildet sein, um somit den Druck im Düsenraum 24 im Vergleich zum Hochdruckraum 8 etwas zu reduzieren. Der Druck wird jedoch mit Vorteil etwa nur um etwa 100 bis 200 bar reduziert, so dass der Düsenraum 24 und der Hochdruckraum 8 als ein gemeinsamer Raum angesehen werden können. Durch den durch das Schließen des Einspritzventilelementes 13 hervorgerufenen abrupten Abfall der Einspritzrate entsteht im Düsenraum 24 und vor allem im Hochdruckraum 8 ein Druckstoß (Joukowski-Stoß) der am Kraftstoff-Hochdruckspeicher 4 reflektiert wird. Diese Mengenwellen führen zu Druckschwingungen. Die dadurch bedingten Spitzendrücke können mehrere hundert bar über dem maximalen Raildruck liegen, wodurch der gesamte Kraftstoff-Injektor 1 sowie das Versorgungssystem entsprechend auf die Spitzendrücke ausgelegt werden müssen.To end the injection process, the energization of the
Um zu ermöglichen, dass der Injektorkörper 19 nicht über die Maßen druckbelastet wird und in der Folge aus herkömmlichen Stählen, wie beispielsweise C45, hergestellt werden kann, sieht der in
Der Ringraum 42 wird radial innen gegenüber dem Hochdruckraum 8 begrenzt von einem rohrförmigen Abschnitt 43 des Injektorbauteils 27. Im Injektorbauteil 27 ist hierzu eine Stufenbohrung 44 eingebracht, die in ihrem in der Zeichnungsebene oberen Ende die Steuerkammer 28 begrenzt. Im Ringraum 42 herrscht dauerhaft ein geringerer Kraftstoffdruck als im Hochdruckraum 8 und dauerhaft ein höherer Kraftstoffdruck als im Niederdruckbereich 12 des Kraftstoff-Injektors 1. Durch mittels einer im Folgenden noch zu erläuternden Drosselanordnung ist der Druck im Ringraum 42 dauerhaft geringer als im Hochdruckraum 8. Die Durchflussquerschnitte der im Folgenden noch zu erläuternden Drosseln sind dabei derart abgestimmt, dass der Druck im Ringraum 42 1800 bar nicht überschreitet. Hierdurch wird die Druckbelastung des Injektorkörpers 19, zumindest in druckkritischen Bereichen über den größten Teil seiner Axialerstreckung reduziert.The
Wie sich aus
Das in
In axialer Richtung nach oben wird der Ringraum 42 begrenzt von dem wie erwähnt auch als separates Bauteil ausführbaren Plattenabschnitt 47 des Injektorbauteils 27. Dieses ist von einer Ventilspannschraube 48 gegen eine Ringschulter 49 des Injektorkörpers 19 gepresst. In axialer Richtung nach unten wird der Ringraum 42 begrenzt von einem Dichtelement 50, welches sich radial zwischen dem unteren Bereich des rohrförmigen Abschnitts 43 des Injektorbauteils 27 und dem Injektorkörper 19 befindet.In the axial direction upward, the
Wie sich aus
Im Folgenden werden anhand der
Im Gegensatz zu dem Ausführungsbeispiel gemäß
Wie sich weiter aus
Das in
Auch ist kein Drosselkanal als Ringraumablaufdrossel 52 vorgesehen. Diese wird gebildet von dem Überdruckventil 53, über das der Ringraum 42 mit dem Niederdruckbereich 12 des Kraftstoff-Injektors 1 verbindbar ist. Das Ventilelement 54 wird gebildet von dem Plattenabschnitt 47 des Injektorbauteils 27. Dieses liegt im geschlossenen Zustand des Überdruckventils 53 auf der Ringschulter 49 des Injektorkörpers 9 auf. Bei geöffnetem Überdruckventil 53 ist der Plattenabschnitt 47 in axialer Richtung nach oben verstellt, sodass ein Ringspalt axial zwischen dem Plattenabschnitt 47 und einer Beißkante 59 des Injektorkörpers 19 gebildet ist, wobei der Durchflussquerschnitt des Ringspaltes so abgestimmt ist, dass die gewünschte Drosselung erzielt wird.Also, no throttle channel is provided as annular
Der Plattenabschnitt 47 hebt erst dann von seinem von der Beißkante 59 gebildeten Ventilsitz 56 am Injektorkörper 19 ab, wenn die auf ihn wirkende Druckkraft die Federkraft einer als Tellerfeder ausgebildeten Feder 55 überschreitet, die sich in axialer Richtung nach oben an der Ventilspannschraube 48 abstützt. Die Feder 55 ist bestrebt, den Plattenabschnitt 47 axial nach unten gegen die Ringschulter 49 des Injektorkörpers 19 zu pressen. Durch Verstellen der Ventilspannschraube 48 kann die Vorspannung der Feder 55 eingestellt werden.The
Claims (11)
- Fuel injector (1), in particular common rail injector, for injecting fuel into a combustion chamber of an internal combustion engine, having a fuel return port (10) and having a single-part or multi-part injection valve element (13) which is adjustable between an open position and a closed position and which is arranged at least in sections in a high-pressure chamber (8) provided in an injector body (19), wherein an annular chamber (42) is arranged radially between the high-pressure chamber (8) and the injector body (19), said annular chamber being connected to the high-pressure chamber (8), and wherein, during the operation of the fuel injector (1), the fuel pressure is at least intermittently lower in the annular chamber (42) than the fuel pressure in the high-pressure chamber (8) and is higher than the fuel pressure in the fuel return port (10), characterized in that the annular chamber (42) is connected to a low-pressure region (12), which is preferably arranged hydraulically downstream, by at least one annular chamber outlet throttle (52) or via at least one pressure release valve (53) which preferably carries out throttling in the open state and is designed in particular as a check valve.
- Fuel injector according to Claim 1, characterized in that the pressure in the annular chamber (42) is at least half the level of the pressure in the high-pressure chamber (8).
- Fuel injector according to either of Claims 1 and 2, characterized in that the fuel flowing in from a supply duct (7) is conducted directly into the high-pressure chamber (8).
- Fuel injector according to one of the preceding claims, characterized in that the high-pressure chamber (8) extends axially as far as a nozzle hole arrangement (17).
- Fuel injector according to one of the preceding claims, characterized in that the high-pressure chamber (8) and/or a supply duct (7) leading to the high-pressure chamber (8) is hydraulically connected to the annular chamber (42) via at least one annular chamber inlet throttle (51).
- Fuel injector according to one of the preceding claims, characterized in that the annular chamber (42) is bounded radially on the inside by an injector component (27) which is tubular at least in sections and preferably bounds a control chamber (28).
- Fuel injector according to one of the preceding claims, characterized in that the pressure in the annular chamber (42) is reduced in comparison to the pressure in the high-pressure chamber (8) only after a minimum pressure, in particular of more than 1800 bar, is exceeded.
- Fuel injector according to one of the preceding claims, characterized in that the pressure release valve (53) comprises a spring (55), in particular a leaf spring, and an, in particular spherical, valve element which is acted upon by spring force by the spring (55), preferably towards an injector component (27) bounding the low-pressure region (12).
- Fuel injector according to one of the preceding claims, characterized in that an adjustable valve element of the pressure release valve (53) is formed by an injector component (27) which bounds the low-pressure region (12) and is pressed by means of a spring (55), in particular by means of an extension sleeve or a disc spring, against the injector body (19).
- Fuel injector according to Claim 9, characterized in that, when the pressure release valve (53) is open, an, in particular annular, linkage gap is formed, preferably axially, between the injector component (27) and the injector body (19).
- Fuel injector according to either of Claims 9 and 10, characterized in that the prestressing of the spring (55) of the pressure release valve (53) is adjustable by means of a valve clamping spring (48).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102008002527A DE102008002527A1 (en) | 2008-06-19 | 2008-06-19 | Fuel injector |
PCT/EP2009/054814 WO2009153087A1 (en) | 2008-06-19 | 2009-04-22 | Fuel injector |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2294309A1 EP2294309A1 (en) | 2011-03-16 |
EP2294309B1 true EP2294309B1 (en) | 2014-06-11 |
Family
ID=40887985
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP09765667.2A Not-in-force EP2294309B1 (en) | 2008-06-19 | 2009-04-22 | Fuel injector |
Country Status (6)
Country | Link |
---|---|
EP (1) | EP2294309B1 (en) |
CN (1) | CN102066741B (en) |
BR (1) | BRPI0914857A2 (en) |
DE (1) | DE102008002527A1 (en) |
RU (1) | RU2541484C2 (en) |
WO (1) | WO2009153087A1 (en) |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102010003202A1 (en) * | 2010-03-24 | 2011-09-29 | Robert Bosch Gmbh | Common rail injector with pressure compensated switching valve and additional storage volume |
CH710127A1 (en) * | 2014-09-17 | 2016-03-31 | Ganser Crs Ag | Fuel injection valve for internal combustion engines. |
JP6384366B2 (en) * | 2015-03-09 | 2018-09-05 | 株式会社デンソー | Fuel injection device |
GB2553140B (en) * | 2016-08-25 | 2020-04-01 | Delphi Tech Ip Ltd | Control valve assembly of a fuel injector |
WO2018119775A1 (en) * | 2016-12-28 | 2018-07-05 | 白保忠 | Counter-recoil sequence valve and sequential driving method therefor |
CN110848060B (en) * | 2019-10-14 | 2022-03-15 | 中国北方发动机研究所(天津) | Electric control pressure accumulation oil sprayer |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6012644A (en) * | 1997-04-15 | 2000-01-11 | Sturman Industries, Inc. | Fuel injector and method using two, two-way valve control valves |
US5720318A (en) * | 1995-05-26 | 1998-02-24 | Caterpillar Inc. | Solenoid actuated miniservo spool valve |
US6047899A (en) * | 1998-02-13 | 2000-04-11 | Caterpillar Inc. | Hydraulically-actuated fuel injector with abrupt end to injection features |
DE10002109A1 (en) * | 2000-01-19 | 2001-08-02 | Bosch Gmbh Robert | Injection system |
DE102006051581A1 (en) * | 2006-11-02 | 2008-05-08 | Robert Bosch Gmbh | Fuel injector for common-rail-high pressure storage injection system, has cavity formed in injection valve unit, where cavity represents storage space for damping pressure vibration |
DE102007021330A1 (en) | 2007-05-07 | 2008-11-13 | Robert Bosch Gmbh | Fuel injector for an internal combustion engine with common rail injection system |
-
2008
- 2008-06-19 DE DE102008002527A patent/DE102008002527A1/en not_active Withdrawn
-
2009
- 2009-04-22 CN CN200980123041.7A patent/CN102066741B/en not_active Expired - Fee Related
- 2009-04-22 BR BRPI0914857-4A patent/BRPI0914857A2/en not_active Application Discontinuation
- 2009-04-22 WO PCT/EP2009/054814 patent/WO2009153087A1/en active Application Filing
- 2009-04-22 EP EP09765667.2A patent/EP2294309B1/en not_active Not-in-force
- 2009-04-22 RU RU2011101635/06A patent/RU2541484C2/en not_active IP Right Cessation
Also Published As
Publication number | Publication date |
---|---|
RU2011101635A (en) | 2012-07-27 |
CN102066741A (en) | 2011-05-18 |
RU2541484C2 (en) | 2015-02-20 |
WO2009153087A1 (en) | 2009-12-23 |
DE102008002527A1 (en) | 2009-12-24 |
CN102066741B (en) | 2014-07-09 |
EP2294309A1 (en) | 2011-03-16 |
BRPI0914857A2 (en) | 2020-08-18 |
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