EP2064438B1 - Fuel injection valve - Google Patents
Fuel injection valve Download PDFInfo
- Publication number
- EP2064438B1 EP2064438B1 EP07802673A EP07802673A EP2064438B1 EP 2064438 B1 EP2064438 B1 EP 2064438B1 EP 07802673 A EP07802673 A EP 07802673A EP 07802673 A EP07802673 A EP 07802673A EP 2064438 B1 EP2064438 B1 EP 2064438B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- discharge openings
- fuel injection
- valve
- valve seat
- spray
- 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
-
- 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
- F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
- F02M61/1853—Orifice plates
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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
- F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
- F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
- F02M61/184—Discharge orifices having non circular sections
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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
- F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
- F02M61/188—Spherical or partly spherical shaped valve member ends
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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
- F02M51/00—Fuel-injection apparatus characterised by being operated electrically
- F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
- F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means
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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
- F02M61/14—Arrangements of injectors with respect to engines; Mounting of injectors
- F02M61/145—Arrangements of injectors with respect to engines; Mounting of injectors the injection nozzle opening into the air intake conduit
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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
- F02M69/00—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel
- F02M69/04—Injectors peculiar thereto
- F02M69/042—Positioning of injectors with respect to engine, e.g. in the air intake conduit
Definitions
- the invention relates to a fuel injection valve according to the preamble of the main claim.
- the perforated disc has a plurality of ejection openings, wherein an inflow opening immediately upstream of the ejection openings is designed such that an inflow of the ejection openings takes place from radially inward to radially outward.
- the ejection openings are triangular or trapezoidal in shape and taper in the radial direction to the outside.
- the fuel injection valve according to the invention with the characterizing features of the main claim has the advantage that in a simple manner on the one hand a super atomization of the fuel is achieved and on the other hand, the exhaust emissions of an internal combustion engine are effectively reduced significantly.
- fuel sprays are sprayed from the fuel injection valve, which are equipped with areas of different droplet size, larger droplets in an outer region form a jacket envelope and smaller droplets fill the inner region of a hollow cone lamella. This is achieved by the specific geometry and orientation of the ejection openings in conjunction with the horizontal flow.
- the outer droplets of the sprayed-off fuel sprays strike down as wall film on the Saugrohrwandache.
- an inflow opening with an inflow cavity which is larger than an exit opening downstream of the valve seat, is provided in the valve seat body upstream of the ejection openings.
- the valve seat body already assumes the function of influencing the flow in the perforated disc.
- an S-impact in the flow for atomization improvement of the fuel is achieved by the formation of the inflow opening, since the valve seat body with the upper boundary of the inflow opening covers the ejection openings of the perforated disk.
- the ejection openings are oriented so that they taper radially outward from an inlet edge for the flow.
- the spray orifices are characterized in that by maximizing the effective separation edge, whereby a desired increased separation effect of the flow in the spray orifices and thus the desired droplet distribution is achieved.
- FIG. 1 a partially illustrated injection valve
- FIG. 2 the perforated disk increases in a section with a schematic clarification of the droplet distribution to form a hollow disk spray
- FIG. 3 a first embodiment of a perforated disc in a plan view
- FIG. 4 the detail IV in FIG. 3 as a first injection opening
- FIG. 5 A second embodiment of a spray-discharge opening
- FIG. 6 A third embodiment of a spray-discharge opening
- FIG. 7 A fourth embodiment of a spray-discharge opening
- FIG. 8 A fifth embodiment of a spray-discharge opening
- FIG. 9 a sixth embodiment of a spray opening
- FIG. 10 a valve end with a perforated disc to form a two-jet spray consisting of two full-disk sprays, where it bai FIG. 10 is an example of a non-claimed item.
- FIG. 1 For example, as an embodiment, a valve in the form of an injector for fuel injection systems of mixture-compression spark-ignition internal combustion engines is partially shown.
- the injection valve has a tubular valve seat carrier 1, which only schematically indicates a part of a valve housing and in which a longitudinal opening 3 is formed concentrically to a valve longitudinal axis 2.
- a longitudinal opening 3 In the longitudinal opening 3 is a z.
- the actuation of the injection valve takes place in a known manner, for example electromagnetically.
- a schematically indicated electromagnetic circuit with a solenoid 10, an armature 11 and a core 12.
- the armature 11 is connected to the valve closing body. 7 opposite end of the valve needle 5 by eg a trained by a laser weld and aligned with the core 12.
- a valve seat body 16 is tightly mounted, for example by welding. At its valve end body 7 facing away, lower end face 17 of the valve seat body 16 is stepped, with a flat, eg single-layer perforated disc 23 is fixed to the end face 17.
- the perforated disc 23 has at least four, but ideally eight to forty injection orifices 25.
- an inflow opening 28 is provided in the valve seat body 16, via which the individual ejection openings 25 are flown.
- the inflow opening 28 in this case has a diameter which is greater than the opening width of the outlet opening 27 in the valve seat body 16, from which the fuel flows into the inflow opening 28 and ultimately into the ejection openings 25.
- the inflow opening 28 is designed in the immediate inflow region of the injection openings 25 so that the flow is largely at right angles to the longitudinal extent of the injection openings 25, in the FIG. 1 So horizontally corresponding to the spray openings 25 passes.
- the connection of valve seat body 16 and perforated disc 23 is effected, for example, by a circumferential and dense, formed by a laser weld 26, which is placed outside of the inflow opening 28.
- the insertion depth of the valve seat body 16 with the perforated disc 23 in the longitudinal opening 3 determines the size of the stroke of the valve needle 5, since the one end position of the valve needle 5 at non-energized solenoid 10 by the system of the valve closing body 7 at the downstream conically tapered valve seat surface 29 of the valve seat body 16 is set.
- the other end position of the valve needle 5 is fixed in the excited magnet coil 10, for example, by the system of the armature 11 to the core 12. The path between these two end positions of the valve needle 5 thus represents the hub.
- the ejection openings 25 of the perforated disc 23 are in direct flow communication with the inflow opening 28 and are covered by the upper boundary of the inflow opening 28. In other words, there is a complete offset of the inlet opening 27 and the ejection openings 25 defining the inlet of the inflow opening 28. Due to the radial offset of the ejection openings 25 with respect to the outlet opening 27 results in an S-shaped flow pattern of the medium, here the fuel.
- the fluid is additionally positively influenced in its atomization by the specific geometry of the ejection openings 25 in connection with the horizontally inflatable inflow opening 28, wherein a hollow lamellar spray with areas of different droplet size is achievable, with larger droplets forming a sheath envelope in an outer area 35 and smaller Droplets fill the inner portion 36 of the Hohlkegellamelle.
- FIG. 2 again schematically the S-shaped curve in the area of the perforated disc 23 is shown enlarged in a section, wherein by means of this Anströmungsart in conjunction with a special design and alignment of the ejection openings 25 according to the invention a special droplet distribution within a hollow disc spray is possible.
- FIG. 3 shows a first embodiment of a perforated disc 23 in a plan view.
- twelve ejection openings 25 are provided, which are arranged annularly on the perforated disc 23.
- the contour of the ejection openings 25 is triangular. In cross-section, for example, each ejection opening 25 has the shape of an equilateral triangle. All triangular spray-discharge openings 25 are aligned in such a way that the horizontal flow, which flows radially outward from the center of the perforated disc 23, meets the spray-discharge openings 25 at a relatively large leading edge 38. Starting from this leading edge 38, the ejection openings 25 taper radially outward or are constricted in the radial direction.
- the arrows 37 are intended on the one hand indicate that the flow of the spray openings 25 is horizontal to their entry or substantially at right angles to the longitudinal extent of the spray openings 25 and on the other hand show how the spray opening 25 is aligned with its large leading edge 38 to the valve longitudinal axis 2.
- the ejection openings 25 are distinguished insofar by maximizing the effective detachment edge, whereby a desired increased separation effect of the flow in the ejection openings 25 and thus the desired droplet distribution is achieved.
- injection orifices 25 are shown, wherein in FIG. 4 the detail IV off FIG. 3 is shown.
- the ejection openings 25 are contoured in such a way that there is always a tapering of the ejection openings 25 on the side facing away from the inflow side, ie radially outward. Due to the horizontal flow of the ejection openings 25, the flow in the ejection openings 25 is directional diffusely, ie the exiting fluid jet fanning out immediately after leaving the ejection opening 25, but is constricted again by the particular contouring of the ejection openings 25 in the radially outer region 35.
- the contours of the ejection openings 25 can be triangular ( FIG. 4 ), truncated triangular ( FIG. 5 ), semicircular ( FIG. 6 ) or semi-elliptic, truncated semicircular ( FIG. 7 ) or truncated semi-elliptic, rounded truncated triangular ( FIG. 8 ), semicircular or semi-elliptic with rounded leading edge 38 (FIG. FIG. 9 ) or similar.
- FIG. 10 is a valve end with a perforated disc 23 for forming a two-jet spray consisting of two full-blade sprays shown very schematically.
- the according to FIGS. 1 to 7 described inflow and Abspritzö Stammsgeometrien be twice distributed independently be introduced on the perforated disc 23.
- corresponding flow channels are necessary in the region of the valve seat body 16, which transport the fluid from the outset into the two desired spray areas, from where the flow can reach the spray openings 25 by way of the previously described principle via inlet edges 38.
- full-disk sprays with a suitable design of the spray-discharge openings 25 and two hollow disc sprays in duplication of the example according to FIG. 2 be generated.
- Such a fuel injection valve is particularly suitable for the spraying of fuel in the direction of two intake valves.
- the perforated disc 23 can be manufactured by microgalvanic, laser cutting, etching or punching technology.
- the cross-section of the ejection openings 25 is constant or increasing in the flow direction over the entire length of the ejection openings 25, depending on the production method or desired use.
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
Description
Die Erfindung geht aus von einem Brennstoffeinspritzventil nach der Gattung des Hauptanspruchs.The invention relates to a fuel injection valve according to the preamble of the main claim.
Bekannt ist bereits aus der
Aus der
Das erfindungsgemäße Brennstoffeinspritzventil mit den kennzeichnenden Merkmalen des Hauptanspruchs hat den Vorteil, dass auf einfache Art und Weise einerseits eine Feinstzerstäubung des Brennstoffs erreicht wird und andererseits die Abgaswerte einer Brennkraftmaschine wirkungsvoll deutlich reduziert werden. Erfindungsgemäß werden von dem Brennstoffeinspritzventil Brennstoffsprays abgespritzt, die mit Bereichen unterschiedlicher Tropfengröße ausgestattet sind, wobei größere Tröpfchen in einem äußeren Bereich eine Mantelumhüllende bilden und kleinere Tröpfchen den inneren Bereich einer Hohlkegellamelle ausfüllen. Dies wird durch die spezifische Geometrie und Ausrichtung der Abspritzöffnungen in Verbindung mit der horizontalen Anströmung erreicht. In den ersten Startzyklen (Kaltstart) einer fremdgezündeten Brennkraftmaschine schlagen sich die äußeren Tröpfchen der abgespritzten Brennstoffsprays als Wandfilm an den Saugrohrwandungen nieder. Nur die im Strahlzentrum existierenden Tröpfchen und ein entsprechend hoher Brennstoffdampfanteil gelangen in den ersten Startzyklen direkt in den Brennraum. Erst einige Zyklen später läuft der Wandfilm aus dem Saugrohr über die Einlassventile in den Brennraum nach. Im Gegensatz zum Stand der Technik werden in idealer Weise erfindungsgemäß die größeren Tröpfchen diese Wandfilmbildung übernehmen. Dieser schlechter aufbereitete Gemischanteil wird dem Brennraum also erst verspätet zugeführt, so dass gerade im Startzyklus der bestaufbereitete Gemischanteil in den Brennraum eingebracht wird und die Abgasemissionen während dieser Zeit deutlich reduziert sind. Das erfindungsgemäße Brennstoffeinspritzventil ist insofern besonders für die Saugrohreinspritzung zur Erzielung extrem niedriger Kaltstart-Abgasemissionswerte geeignet. Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen des im Hauptanspruch angegebenen Brennstoffeinspritzventils möglich.The fuel injection valve according to the invention with the characterizing features of the main claim has the advantage that in a simple manner on the one hand a super atomization of the fuel is achieved and on the other hand, the exhaust emissions of an internal combustion engine are effectively reduced significantly. According to the invention fuel sprays are sprayed from the fuel injection valve, which are equipped with areas of different droplet size, larger droplets in an outer region form a jacket envelope and smaller droplets fill the inner region of a hollow cone lamella. This is achieved by the specific geometry and orientation of the ejection openings in conjunction with the horizontal flow. In the first start cycles (cold start) of a spark-ignited internal combustion engine, the outer droplets of the sprayed-off fuel sprays strike down as wall film on the Saugrohrwandungen. Only the droplets existing in the jet center and a correspondingly high proportion of fuel vapor reach directly into the combustion chamber during the first start cycles. Only a few cycles later, the wall film from the intake manifold runs over the inlet valves into the combustion chamber. In contrast to the prior art, the larger droplets will ideally take over this wall film formation according to the invention. This poorly prepared mixture content is therefore supplied to the combustion chamber late, so that just in the start cycle, the best-prepared mixture content is introduced into the combustion chamber and the exhaust emissions are significantly reduced during this time. The fuel injection valve according to the invention is particularly suitable for intake manifold injection in order to achieve extremely low cold-start exhaust emission values. The measures listed in the dependent claims advantageous refinements and improvements of the main claim fuel injector are possible.
In vorteilhafter Weise ist im Ventilsitzkörper stromaufwärts der Abspritzöffnungen eine Zuströmöffnung mit einem Anströmhohlraum vorgesehen, die größer ist als eine Austrittsöffnung stromabwärts des Ventilsitzes. Auf diese Weise übernimmt der Ventilsitzkörper bereits die Funktion einer Strömungsbeeinflussung in der Lochscheibe. In besonders vorteilhafter Weise wird durch die Ausbildung der Zuströmöffnung ein S-Schlag in der Strömung zur Zerstäubungsverbesserung des Brennstoffs erreicht, da der Ventilsitzkörper mit der oberen Begrenzung der Zuströmöffnung die Abspritzöffnungen der Lochscheibe überdeckt. Die Abspritzöffnungen sind so ausgerichtet, dass sie sich von einer Eintrittskante für die Strömung ausgehend radial nach außen verjüngen. Die Abspritzöffnungen zeichnen sich insofern durch eine Maximierung der wirksamen Ablösekante aus, wodurch ein gewollter erhöhter Ablöseeffekt der Strömung in den Abspritzöffnungen und somit die gewünschte Tröpfchenverteilung erreicht wird.In an advantageous manner, an inflow opening with an inflow cavity, which is larger than an exit opening downstream of the valve seat, is provided in the valve seat body upstream of the ejection openings. In this way, the valve seat body already assumes the function of influencing the flow in the perforated disc. In a particularly advantageous manner, an S-impact in the flow for atomization improvement of the fuel is achieved by the formation of the inflow opening, since the valve seat body with the upper boundary of the inflow opening covers the ejection openings of the perforated disk. The ejection openings are oriented so that they taper radially outward from an inlet edge for the flow. The spray orifices are characterized in that by maximizing the effective separation edge, whereby a desired increased separation effect of the flow in the spray orifices and thus the desired droplet distribution is achieved.
Ausführungsbeispiele der Erfindung sind in der Zeichnung vereinfacht dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen
In der
Die Betätigung des Einspritzventils erfolgt in bekannter Weise, beispielsweise elektromagnetisch. Zur axialen Bewegung der Ventilnadel 5 und damit zum Öffnen entgegen der Federkraft einer nicht dargestellten Rückstellfeder bzw. Schließen des Einspritzventils dient ein schematisch angedeuteter elektromagnetischer Kreis mit einer Magnetspule 10, einem Anker 11 und einem Kern 12. Der Anker 11 ist mit dem dem Ventilschließkörper 7 abgewandten Ende der Ventilnadel 5 durch z.B. eine mittels eines Lasers ausgebildete Schweißnaht verbunden und auf den Kern 12 ausgerichtet.The actuation of the injection valve takes place in a known manner, for example electromagnetically. For axial movement of the
In dem stromabwärts liegenden Ende des Ventilsitzträgers 1 ist ein Ventilsitzkörper 16 z.B. durch Schweißen dicht montiert. An seiner dem Ventilschließkörper 7 abgewandten, unteren Stirnseite 17 ist der Ventilsitzkörper 16 gestuft ausgeführt, wobei eine flache, z.B. einlagige Lochscheibe 23 an der Stirnseite 17 befestigt ist. Die Lochscheibe 23 weist mindestens vier, idealerweise jedoch acht bis vierzig Abspritzöffnungen 25 auf. Als Verlängerung einer stromabwärts einer Ventilsitzfläche 29 ausgebildeten Austrittsöffnung 27 ist im Ventilsitzkörper 16 eine Zuströmöffnung 28 vorgesehen, über die die einzelnen Abspritzöffnungen 25 angeströmt werden. Die Zuströmöffnung 28 besitzt dabei einen Durchmesser, der größer ist als die Öffnungsweite der Austrittsöffnung 27 im Ventilsitzkörper 16, aus der der Brennstoff kommend in die Zuströmöffnung 28 und letztlich in die Abspritzöffnungen 25 einströmt. Die Zuströmöffnung 28 ist im unmittelbaren Anströmbereich der Abspritzöffnungen 25 so ausgeführt, dass die Strömung weitgehend im rechten Winkel zur Längserstreckung der Abspritzöffnungen 25, in der
Die Einschubtiefe des Ventilsitzkörpers 16 mit der Lochscheibe 23 in der Längsöffnung 3 bestimmt die Größe des Hubs der Ventilnadel 5, da die eine Endstellung der Ventilnadel 5 bei nicht erregter Magnetspule 10 durch die Anlage des Ventilschließkörpers 7 an der sich stromabwärts konisch verjüngenden Ventilsitzfläche 29 des Ventilsitzkörpers 16 festgelegt ist. Die andere Endstellung der Ventilnadel 5 wird bei erregter Magnetspule 10 beispielsweise durch die Anlage des Ankers 11 an dem Kern 12 festgelegt. Der Weg zwischen diesen beiden Endstellungen der Ventilnadel 5 stellt somit den Hub dar.The insertion depth of the
Die Abspritzöffnungen 25 der Lochscheibe 23 stehen mit der Zuströmöffnung 28 in unmittelbare Strömungsverbindung und werden dabei von der oberen Begrenzung der Zuströmöffnung 28 überdeckt. Mit anderen Worten ausgedrückt liegt ein vollständiger Versatz von der den Einlass der Zuströmöffnung 28 festlegenden Austrittsöffnung 27 und den Abspritzöffnungen 25 vor. Aufgrund des radialen Versatzes der Abspritzöffnungen 25 gegenüber der Austrittsöffnung 27 ergibt sich ein S-förmiger Strömungsverlauf des Mediums, hier des Brennstoffs.The
Durch den so genannten S-Schlag vor und innerhalb der Lochscheibe 23 mit mehreren starken Strömungsumlenkungen wird der Strömung eine starke, zerstäubungsfördernde Turbulenz aufgeprägt. Erfindungsgemäß wird durch die spezifische Geometrie der Abspritzöffnungen 25 in Verbindung mit der horizontal anströmbaren Zuströmöffnung 28 das Fluid noch zusätzlich in seiner Zerstäubung positiv beeinflusst, wobei ein Hohllamellenspray mit Bereichen unterschiedlicher Tropfengröße erzielbar ist, wobei größere Tröpfchen in einem äußeren Bereich 35 eine Mantelumhüllende bilden und kleinere Tröpfchen den inneren Bereich 36 der Hohlkegellamelle ausfüllen.Due to the so-called S-blow before and within the
Anhand von
In den
In
Die Lochscheibe 23 kann mikrogalvanisch, laserschneidtechnisch, ätztechnisch oder stanztechnisch hergestellt werden. Der Querschnitt der Abspritzöffnungen 25 ist je nach Herstellungsverfahren bzw. Einsatzwunsch über die gesamte Länge der Abspritzöffnungen 25 konstant oder in Strömungsrichtung zunehmend.The
Claims (5)
- Fuel injection valve for fuel injection systems of internal combustion engines, having a valve longitudinal axis (2), having a valve seat body (16) which has a fixed valve seat (29), having a valve closing body (7) which interacts with the valve seat (29) and which is axially movable along the valve longitudinal axis (2), and having a perforated disc (23) which is arranged downstream of the valve seat (29) and which has a plurality of discharge openings (25), wherein the discharge openings (25) are arranged annularly and the discharge openings (25) have an inlet edge (38) proceeding from which the discharge openings (25) taper in the radially outward direction, characterized in that the discharge openings (25) are arranged and aligned such that at least one hollow lamellar spray can be discharged in which a radially outer region (35) is composed of larger droplets than a radially inner region (36) of the spray, and in that an inflow opening (28) directly upstream of the discharge openings (25) is designed such that a flow approaching the discharge openings (25) runs from radially inside to radially outside substantially at right angles to the longitudinal extent of the discharge openings (25).
- Fuel injection valve according to Claim 1, characterized in that eight to forty discharge openings (25) are provided for forming a fuel spray.
- Fuel injection valve according to one of the preceding claims, characterized in that the contours of the discharge openings (25) are triangular, in the form of truncated triangles, semicircular, semielliptical, in the form of truncated semicircles, in the form of truncated semiellipses, in the form of triangles with a rounded truncation, or semicircular or semielliptical with a rounded inlet edge (38).
- Fuel injection valve according to one of the preceding claims, characterized in that the inflow opening (28) is provided on the lower face side (17) of the valve seat body (16).
- Fuel injection valve according to one of the preceding claims, characterized in that the perforated disc (23) can be produced by means of galvanic metal deposition, by laser cutting or by punching.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102006041475A DE102006041475A1 (en) | 2006-09-05 | 2006-09-05 | Fuel injector |
PCT/EP2007/058553 WO2008028786A1 (en) | 2006-09-05 | 2007-08-17 | Fuel injection valve |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2064438A1 EP2064438A1 (en) | 2009-06-03 |
EP2064438B1 true EP2064438B1 (en) | 2012-10-31 |
Family
ID=38787707
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP07802673A Not-in-force EP2064438B1 (en) | 2006-09-05 | 2007-08-17 | Fuel injection valve |
Country Status (5)
Country | Link |
---|---|
US (1) | US20090321540A1 (en) |
EP (1) | EP2064438B1 (en) |
JP (1) | JP5222294B2 (en) |
DE (1) | DE102006041475A1 (en) |
WO (1) | WO2008028786A1 (en) |
Families Citing this family (8)
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DE102008042116B4 (en) * | 2008-09-15 | 2019-12-24 | Robert Bosch Gmbh | Valve for atomizing fluid |
JP5295311B2 (en) * | 2011-06-09 | 2013-09-18 | 三菱電機株式会社 | Fuel injection valve |
CN102410121A (en) * | 2011-09-08 | 2012-04-11 | 何林霏 | S-shaped atomizing nozzle |
JP5959892B2 (en) | 2012-03-26 | 2016-08-02 | 日立オートモティブシステムズ株式会社 | Spark ignition type fuel injection valve |
US20150014448A1 (en) * | 2013-07-12 | 2015-01-15 | Delphi Technologies, Inc. | Valve seat for gaseous fuel injector |
EP3184799A1 (en) * | 2015-12-22 | 2017-06-28 | Continental Automotive GmbH | Nozzle body for a fluid injector and fluid injector |
JP6339628B2 (en) * | 2016-06-22 | 2018-06-06 | 日立オートモティブシステムズ株式会社 | Fuel injection valve |
CN113153595B (en) * | 2021-03-28 | 2022-02-25 | 南岳电控(衡阳)工业技术股份有限公司 | Low hydraulic swirl injector |
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DE4409848A1 (en) * | 1994-03-22 | 1995-10-19 | Siemens Ag | Device for metering and atomizing fluids |
JP4009889B2 (en) * | 1999-02-16 | 2007-11-21 | 株式会社デンソー | Fuel injection valve |
JP2001046919A (en) * | 1999-08-06 | 2001-02-20 | Denso Corp | Fluid injection nozzle |
US6588399B2 (en) * | 2000-02-22 | 2003-07-08 | Hitachi, Ltd. | Fuel injection method of internal combustion engine and fuel injection apparatus of internal combustion engine |
JP2001317434A (en) * | 2000-02-22 | 2001-11-16 | Hitachi Ltd | Fuel injection method of and fuel injection device for internal combustion engine |
JP2001263206A (en) * | 2000-03-17 | 2001-09-26 | Denso Corp | Fuel injection valve |
JP2001317431A (en) * | 2000-02-25 | 2001-11-16 | Denso Corp | Fluid injection nozzle |
EP1128062B1 (en) * | 2000-02-25 | 2006-04-26 | Denso Corporation | Fluid injection nozzle |
US6817545B2 (en) * | 2002-01-09 | 2004-11-16 | Visteon Global Technologies, Inc. | Fuel injector nozzle assembly |
JP3751264B2 (en) * | 2002-06-19 | 2006-03-01 | 株式会社ケーヒン | Fuel injection valve |
US6966505B2 (en) * | 2002-06-28 | 2005-11-22 | Siemens Vdo Automotive Corporation | Spray control with non-angled orifices in fuel injection metering disc and methods |
US6929197B2 (en) * | 2002-09-25 | 2005-08-16 | Siemens Vdo Automotive Corporation | Generally circular spray pattern control with non-angled orifices in fuel injection metering disc and method |
DE10350548A1 (en) * | 2003-10-29 | 2005-06-02 | Robert Bosch Gmbh | Fuel injector |
JP4030529B2 (en) * | 2004-06-21 | 2008-01-09 | 株式会社ケーヒン | Fuel injection valve |
JP4134966B2 (en) * | 2004-08-17 | 2008-08-20 | 株式会社デンソー | Injection hole member, fuel injection valve, and method for manufacturing injection hole member |
US7198207B2 (en) * | 2004-11-05 | 2007-04-03 | Visteon Global Technologies, Inc. | Low pressure fuel injector nozzle |
-
2006
- 2006-09-05 DE DE102006041475A patent/DE102006041475A1/en not_active Withdrawn
-
2007
- 2007-08-17 WO PCT/EP2007/058553 patent/WO2008028786A1/en active Application Filing
- 2007-08-17 US US12/308,185 patent/US20090321540A1/en not_active Abandoned
- 2007-08-17 EP EP07802673A patent/EP2064438B1/en not_active Not-in-force
- 2007-08-17 JP JP2009526042A patent/JP5222294B2/en not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
DE102006041475A1 (en) | 2008-03-06 |
WO2008028786A1 (en) | 2008-03-13 |
JP5222294B2 (en) | 2013-06-26 |
US20090321540A1 (en) | 2009-12-31 |
JP2010501784A (en) | 2010-01-21 |
EP2064438A1 (en) | 2009-06-03 |
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