EP1627147B1 - Fuel injection valve for combustion engines - Google Patents
Fuel injection valve for combustion engines Download PDFInfo
- Publication number
- EP1627147B1 EP1627147B1 EP03782138A EP03782138A EP1627147B1 EP 1627147 B1 EP1627147 B1 EP 1627147B1 EP 03782138 A EP03782138 A EP 03782138A EP 03782138 A EP03782138 A EP 03782138A EP 1627147 B1 EP1627147 B1 EP 1627147B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- fuel injection
- sealing
- needle
- sealing edge
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
- 238000002347 injection Methods 0.000 title claims description 65
- 239000007924 injection Substances 0.000 title claims description 65
- 239000000446 fuel Substances 0.000 title claims description 42
- 238000002485 combustion reaction Methods 0.000 title claims description 17
- 238000007789 sealing Methods 0.000 claims description 85
- 238000011144 upstream manufacturing Methods 0.000 claims description 5
- 230000005489 elastic deformation Effects 0.000 description 4
- 239000004215 Carbon black (E152) Substances 0.000 description 3
- 229930195733 hydrocarbon Natural products 0.000 description 3
- 150000002430 hydrocarbons Chemical class 0.000 description 3
- 238000004519 manufacturing process Methods 0.000 description 3
- 230000007704 transition Effects 0.000 description 3
- 230000008901 benefit Effects 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
- F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
- F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
- F02M45/08—Injectors peculiar thereto
- F02M45/086—Having more than one injection-valve controlling discharge orifices
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
- F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
- F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
- F02M45/08—Injectors peculiar thereto
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
- F02M61/047—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series the valves being formed by deformable nozzle parts, e.g. flexible plates or discs with fuel discharge orifices
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- 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
-
- 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
- F02M2200/46—Valves, e.g. injectors, with concentric valve bodies
Definitions
- the invention is based on a fuel injection valve for internal combustion engines, as for example from the document DE 103 15 821 A1 is known.
- the known fuel injection valve has a valve seat, from which at least one injection opening goes off.
- a piston-shaped valve needle is arranged, which is designed as a valve outer needle.
- the valve needle has a valve sealing surface, with which the valve needle so cooperates with the valve seat by their longitudinal movement, thereby the injection ports can be opened or closed to control the fuel injection into the combustion chamber.
- Two sealing edges are formed on the valve sealing surface, of which the first sealing edge comes into contact with the valve seat on the valve seat upstream and the second sealing edge downstream of the at least one injection opening on the valve seat. As a result, the injection openings are to be completely sealed against the other fuel in the fuel injection valve.
- a fuel injection valve having an outer and an inner valve needle, wherein the inner valve needle is guided in the outer.
- the outer valve needle has at its valve seat side end an inwardly cantilevered sealing lip on which a sealing edge is formed, which seals the outer injection openings both upstream and downstream together with another sealing edge on the outer valve needle when the outer valve needle in its closed position in contact with the valve seat.
- the fuel injection valve according to the invention with the features of claim 1 has the advantage over that a sealing of the injection openings upstream and downstream is achieved by the valve needle, which compared to the closing forces occurring only small forces are needed.
- the valve needle according to the invention has on its valve seat side end face a recess, so that an elastically or plastically inwardly deformable sealing lip is formed, on which the second sealing edge is formed.
- the sealing lip is easily deformed, without reducing the wall thickness of the valve needle, as far as it is designed as a hollow needle, too far.
- the stability of the valve needle is maintained while good sealing of the injection openings.
- the recess forming the sealing lip can also be used with a valve needle which has no longitudinal bore.
- a further reduction of the fuel-filled volume which is connected in the injection pauses on the injection ports to the combustion chamber.
- the hydrocarbon emissions of the internal combustion engine are significantly reduced.
- the recess is advantageously formed by a radial extension at the valve seat side end of the longitudinal bore.
- the training is as a chamfer, so that the recess has a frusto-conical shape.
- the second sealing edge is precisely formed as a ridge, wherein the second sealing edge simultaneously forms the valve seat side end of the valve needle.
- Decisive is the Schwownng the combustion chamber end of the valve needle, where the second sealing edge is formed, so that a sealing lip is formed, which is so far elastic that it already springs by little effort inside.
- the recess can be designed to have the same cross-section.
- the elastic sealing lip also ensures a corresponding sealing of the injection openings.
- sealing lip triangular in cross-section. This results in the outer edge automatically the second sealing edge, which is so precise to manufacture.
- FIG. 1 a fuel injection valve according to the invention is shown in longitudinal section.
- a valve body 1 In a valve body 1, a bore 5 is formed, which is bounded at its combustion-chamber end by a substantially conical valve seat 18.
- the valve body 1 is in this case pressed by means of a clamping nut 3 against a holding body, not shown in the drawing.
- From the valve seat 18 go from injection openings 20 and inner injection openings 22, which open into the mounting position of the fuel injection valve in the combustion chamber of the internal combustion engine.
- a valve needle 8 In the bore 5, a valve needle 8 is arranged, which is guided in a region remote from the valve seat in the bore 5.
- the valve needle 8 tapers from the guided portion of the valve seat 18 to form a pressure shoulder 12 and merges at its combustion chamber end in a likewise substantially conical valve sealing surface 35, with which the valve needle 8 cooperates with the valve seat 18.
- a pressure chamber 14 is formed which is radially expanded at the level of the pressure shoulder 12. In the radial extension of the pressure chamber 14 opens an extending in the valve body 1 inlet channel 16 through which the pressure chamber 14 can be filled with fuel under high pressure.
- a longitudinal bore 11 is formed, in which an inner needle 10 is arranged longitudinally displaceable.
- the inner needle 10 has at its valve seat-side end an inner valve sealing surface 42, with which it also interacts with the valve seat 18.
- the valve needle 8 and the inner needle 10 cooperate with the valve seat 18 so that upon contact of the valve needle 8 on the valve seat 18, the pressure chamber 14 is sealed against the injection openings 20, 22.
- the inner needle 10 remains in this process, at least for now in its closed position in which it is also held by a closing force.
- the inner needle 10 is now acted upon by the fuel pressure, which leads via corresponding pressure surfaces on the inner needle 10 to an opening force opposing the closing force.
- the inner needle 10 now also lifts off the valve seat 18 and releases the inner injection openings 22 or it remains in its closed position by a correspondingly high closing force.
- fuel can be injected into the combustion chamber through all the injection openings 20, 22 or only through part of the injection openings 20.
- FIG. 2 shows an enlarged view of the designated II section of FIG. 1 in the region of the valve seat, wherein the embodiment shown here corresponds to the already known prior art.
- the valve needle 8 covers with its valve sealing surface 35 from the injection openings 20.
- the seal should be done both against the pressure chamber 14 and against the remaining between the inner needle 10 and the valve needle 8 gap. Otherwise, high hydrocarbon emissions may result, resulting from fuel that enters the combustion chamber from the gap in the injection pauses through the injection openings 20.
- the valve sealing surface 35 with a equip first sealing edge 26 and a second sealing edge 28.
- valve sealing surface 35 is divided into a first conical surface 30, a second conical surface 31, a third conical surface 32 and a fourth conical surface 33, wherein the first sealing edge 26 is formed at the transition of the first conical surface 30 to the second conical surface 31 and the second sealing edge 28 on Transition of the third cone surface 32 to the fourth cone surface 33.
- FIG. 3 is the section of III FIG. 2 shown enlarged again.
- it is known to form the second sealing edge 28 so that it rests on the valve seat 18 first on the valve seat 18 during the movement of the valve needle 8.
- the fuel injection valve according to the invention is, for example, as in FIG. 4 shown constructed.
- a recess 37 is formed, which is formed here by a radial extension of the longitudinal bore 11.
- FIG. 5 shows an enlarged view in the region of the recess 37.
- This recess 37 has the shape of a truncated cone and is formed so that a sealing lip 40 is formed, on which the second sealing edge 28 is formed.
- the sealing lip 40 is approximately triangular and thereby at its the second Sealing edge 28 forming outer edge so flexible that it can deform already by small forces radially inward. So are the sealing edges 26, 28 arranged as well as in the already known embodiment of FIGS. 2 and 3 , so first sets the second sealing edge 28 on the valve seat 18 during the closing movement of the valve needle 8.
- the sealing lip 40 formed by the recess 37 is now pressed radially inwardly already by small axial forces and makes it possible that the first sealing edge 26 touches on the valve seat 18 and the injection openings 20 seals.
- the wall thickness of the valve needle 8 is hardly weakened in the region of the annular groove 24, so that there is still virtually the same stability of the valve needle 8 results.
- the fourth conical surface 33 is omitted by the formation of the recess 37th
- FIGS. 5a to 5f further embodiments will be explained in the following only to the differences from FIG. 5 The unchanged parts will not be explained.
- the recess 37 is under the truncated cone-shaped, but it is designed so that at the valve seat side end of the valve needle 8, an annular surface 44 is formed.
- the second sealing edge 28 is formed on the outer edge of this annular surface 44, which makes the syringe of the valve needle 8 somewhat more stable, but also somewhat less flexible.
- FIG. 5b an embodiment is shown in which the annular surface 44 is slightly inclined, so that the second sealing edge 28 is no longer the valve seat side end of the valve needle 8 forms. However, it is also ensured by the recess 37 that there is sufficient flexibility in this area.
- FIG. 5c shows a further embodiment in which the recess 37 is again formed so that an annular surface 44 is formed.
- the annular groove 24 is not through here formed two conical surfaces, but it has a rounded course. This results, depending on the design of the annular groove 24, a slightly greater flexibility of the sealing lip 40th
- FIG. 5d shows a known from the prior art fuel injection valve, wherein the recess 37 is not frusto-conical, but bell-shaped, so that the sealing lip 40 is even thinner and thus formed with even greater flexibility.
- the annular groove 24 is again formed here by two conical surfaces.
- FIG. 5e a shoulder 34 is formed in the annular groove 24, between the second conical surface 31 and the third conical surface 32.
- the sealing lip 44 can be specifically weakened and thus further increase the flexibility.
- FIG. 5f shows that instead of edge-like, sharp transitions between the conical surfaces 31, 32 and the shoulder 34 to round the shoulder 34 and the third cone surface 32, resulting in a reduction of notch stresses in this area.
- FIG. 6 shows a fuel injection valve, which is known from the prior art.
- the structure is largely the same as in FIG. 1 shown, so that the same components are designated by the same reference numerals.
- the valve needle 8 has no longitudinal bore, so that the inner needle is eliminated.
- the valve needle 8 controls in a known manner the fuel flow from the pressure chamber 14 to the injection openings 20, in which it moves in the longitudinal direction.
- FIG. 7 shows an enlarged view in the region of the valve seat 18 of FIG.
- the valve sealing surface 35 has a first conical surface 30 and a second conical surface 31, which in their opening angle so are formed, that between them a first sealing edge 26 'is formed, between which and the valve seat 18, the sealing of the injection openings 20 takes place to the pressure chamber 14.
- the conical valve seat 18 does not taper to the combustion chamber end of the valve body 1, but opens into a residual volume 46, which has the shape of a hemisphere substantially.
- the residual volume 46 also serves as a tool outlet during the production of the valve seat 18. This residual volume 46 remains connected with the fuel injection valve closed via the injection openings 20 with the combustion chamber, which has a negative effect on the hydrocarbon emissions of the internal combustion engine.
- valve needle 8 according to the invention as in the embodiment of the invention FIG. 8 educated.
- the sealing lip 40 seals in this case the injection openings 20 against the remaining volume 46, whereby the still connected to the injection openings 20, fuel-filled volume to the volume the annular groove 24 is limited.
- the recess 37 may also take various forms here, for example, a bell shape, as in FIG. 5d shown, or a hemispherical shape. Likewise, all in the FIGS. 5a to 5c . 5e and 5f Shown forms of the annular groove 24 are also implemented here.
- the sealing lip 40 is plastically deformable.
- the sealing lip 40 is deformed so far that the two sealing edges 26, 28 rest on the valve seat 18, in which case the small force can be eliminated, which is still necessary to deform the sealing lip 40 inwardly.
- the deformation of the sealing lip 40 is plastically-elastic, ie during the first closing operation, part of the total deformation necessary to bring the first sealing edge 26 into abutment with the valve sealing surface 18 takes place plastically, which results in the subsequently necessary forces further reduced for the elastic deformation of the sealing lip 40.
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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 von einem Kraftstoffeinspritzventil für Brennkraftmaschinen aus, wie es beispielsweise aus der Schrift
Bei dem bekannten Kraftstoffeinspritzventil kommt es hierbei jedoch zu Schwierigkeiten: Um eine sichere Abdichtung an beiden Dichtkanten zu erreichen sind die Dichtkanten so angeordnet, dass bei der Bewegung der Ventilnadel auf die Ventildichtfläche zu zuerst die zweite Dichtkante am Ventilsitz zur Anlage kommt und erst bei höherer Schließkraft und entsprechender elastischer Verformung am ventilsitzseitigen Ende der Ventilnadel auch die erste Dichtkante. Die Kräfte, die hierzu aufgewandt werden müssen, sind beträchtlich: Die Verformung der Ventilnadel radial nach innen kann nur durch eine Stauchung der gesamten Nadel erfolgen, was die hohen Kräfte bedingt. Die Schließkraft auf die Ventilnadel muss neben dem hydraulischen Druck, der bei Common-Rail Anwendungen üblicherweise ständig auf die Ventilnadel wirkt, auch noch diese die Abdichtung bewirkende Kraft aufbringen, was den effektiven Öffnungsdruck erniedrigt. Insbesondere für den Fall, dass sich durch Ermüdung oder plastisches Verformung der Ventilnadel die für die Abdichtung der Ventilnadel nötige Kraft im Laufe der Lebensdauer ändert, ändert sich auch die Öffnungskraft und damit der Öffnungsdruck, was eine Änderung der Einspritzcharakteristik des Kraftstoffeinspritzventils bewirktIn the known fuel injection valve, however, there are difficulties: In order to achieve a secure seal on both sealing edges, the sealing edges are arranged so that upon movement of the valve needle on the valve sealing surface to first the second sealing edge on the valve seat comes to rest and only at higher closing force and more Elastic deformation at the valve seat side end of the valve needle and the first sealing edge. The forces that must be expended for this are considerable: The deformation of the valve needle radially inward can only be done by a compression of the entire needle, which causes the high forces. The closing force on the valve needle, in addition to the hydraulic pressure, which usually acts constantly on the valve needle in common-rail applications, must also apply this seal-causing force, which lowers the effective opening pressure. In particular, in the event that changes due to fatigue or plastic deformation of the valve needle necessary for the sealing of the valve needle force in the course of life, also changes the opening force and thus the opening pressure, causing a change in the injection characteristic of the fuel injection valve
Weiterhin ist aus der
Das erfindungsgemäße Kraftstoffeinspritzventil mit den Merkmalen des Patentanspruchs 1 weist demgegenüber den Vorteil auf, dass eine Abdichtung der Einspritzöffnungen stromaufwärts und stromabwärts durch die Ventilnadel erreicht wird, wobei dazu verglichen mit den auftretenden Schließkräften nur geringe Kräfte nötig sind. Hierzu weist die erfindungsgemäße Ventilnadel an ihrer ventilsitzseitigen Stirnseite eine Ausnehmung auf, so, dass eine elastisch oder plastisch nach innen verformbare Dichtlippe gebildet wird, an dem die zweite Dichtkante ausgebildet ist. Durch diese Ausnehmung wird die Dichtlippe leicht verformbar, ohne die Wandstärke der Ventilnadel, soweit diese als Hohlnadel ausgebildet ist, zu weit zu mindern. Dadurch bleibt die Stabilität der Ventilnadel erhalten bei gleichzeitiger guter Abdichtung der Einspritzöffnungen. Ebenso vorteilhaft lässt sich die die Dichtlippe formende Ausnehmung auch bei einer Ventilnadel anwenden, die keine Längsbohrung aufweist. Hier ergibt sich durch die sonst nicht mögliche Abdichtung sowohl stromaufwärts als auch stromabwärts der Einspritzöffnungen eine weitere Reduzierung des kraftstoffgefüllten Volumens, das in den Einspritzpausen über die Einspritzöffnungen mit dem Brennraum verbunden ist. Hierdurch werden die Kohlenwasserstoffemissionen der Brennkraftmaschine deutlich gesenkt.The fuel injection valve according to the invention with the features of claim 1 has the advantage over that a sealing of the injection openings upstream and downstream is achieved by the valve needle, which compared to the closing forces occurring only small forces are needed. For this purpose, the valve needle according to the invention has on its valve seat side end face a recess, so that an elastically or plastically inwardly deformable sealing lip is formed, on which the second sealing edge is formed. By this recess, the sealing lip is easily deformed, without reducing the wall thickness of the valve needle, as far as it is designed as a hollow needle, too far. As a result, the stability of the valve needle is maintained while good sealing of the injection openings. Likewise, the recess forming the sealing lip can also be used with a valve needle which has no longitudinal bore. Here results from the otherwise impossible sealing both upstream and downstream of the injection openings, a further reduction of the fuel-filled volume, which is connected in the injection pauses on the injection ports to the combustion chamber. As a result, the hydrocarbon emissions of the internal combustion engine are significantly reduced.
Durch die abhängigen Ansprüche sind vorteilhafte Ausgestaltungen des Gegenstandes der Erfindung möglich.By the dependent claims advantageous embodiments of the subject invention are possible.
Soweit die Ventilnadel als eine Hohlnadel mit einer entsprechenden Längsbohrung ausgebildet ist, wird die Ausnehmung vorteilhafterweise durch eine radiale Erweiterung am ventilsitzseitigen Ende der Längsbohrung ausgebildet. Die Ausbildung ist als Anschrägung, so dass die Ausnehmung eine kegelstumpfförmige Form aufweist. Dies ist einfach zu fertigen, und die zweite Dichtkante wird präzise als Grat ausgebildet, wobei die zweite Dichtkante gleichzeitig das ventilsitzseitige Ende der Ventilnadel bildet. Entscheidend ist die Schwächng des brennraumseitigen Endes der Ventilnadel, an dem die zweite Dichtkante ausgebildet ist, so, dass eine Dichtlippe gebildet wird, die soweit elastisch ist, dass sie bereits durch geringen Kraftaufwand nach innen federt.As far as the valve needle is formed as a hollow needle with a corresponding longitudinal bore, the recess is advantageously formed by a radial extension at the valve seat side end of the longitudinal bore. The training is as a chamfer, so that the recess has a frusto-conical shape. This is easy to manufacture, and the second sealing edge is precisely formed as a ridge, wherein the second sealing edge simultaneously forms the valve seat side end of the valve needle. Decisive is the Schwächng the combustion chamber end of the valve needle, where the second sealing edge is formed, so that a sealing lip is formed, which is so far elastic that it already springs by little effort inside.
Ist die Ventilnadel massiv ausgeführt und weist keine Längsbohrung auf, so kann die Ausnehmung im Querschnitt gesehen in gleicher Weise ausgeführt sein. Die elastische Dichtlippe sorgt ebenfalls für eine entsprechende Abdichtung der Einspritzöffnungen.If the valve needle is made solid and has no longitudinal bore, the recess can be designed to have the same cross-section. The elastic sealing lip also ensures a corresponding sealing of the injection openings.
Besonders vorteilhaft ist es, die Dichtlippe im Querschnitt gesehen dreieckförmig auszubilden. Hierdurch ergibt sich an der Außenkante automatisch die zweite Dichtkante, die so präzise zu fertigen ist.It is particularly advantageous to design the sealing lip triangular in cross-section. This results in the outer edge automatically the second sealing edge, which is so precise to manufacture.
In der Zeichnung sind der Stand der Technik und verschiedene Ausführungsbeispiele des erfindungsgemäßen Kraftstoffeinspritzventils dargestellt. Es zeigt
- Figur 1
- ein erfindungsgemäßes Kraftstoffeinspritzventil mit zwei ineinander geführten Ventilnadeln im Längsschnitt,
- Figur 2
- eine Vergrößerung von
Figur 1 im mit II bezeichneten Ausschnitt, - Figur 3
- eine vergrößerte Darstellung von
Figur 2 im mit III bezeichneten Ausschnitt, wobei die Ausgestaltung derFiguren 2 und 3 den Stand der Technik darstellt, - Figur 4
- in derselben Darstellung wie
Figur 2 ein erstes Ausführungsbeispiel der Erfindung, Figur 5- den mit V bezeichneten Ausschnitt von
Figur 4 in vergrößerter Darstellung, - Figur 5a, 5b, 5c, 5e und 5f
- zeigen in derselben Darstellung wie
weitere Ausführungsbeispiele der Erfindung,Figur 5Figur 5d zeigt ein aus dem Stand der Technik bekanntes Kraftstaffeinspritzventil, - Figur 6
- zeigt ein aus dem Stand der Technik bekanntes Kraftstoffeinspritzventil im Längsschnitt, wobei hier nur eine Ventilnadel vorgesehen ist,
- Figur 7
- zeigt eine vergrößerte Darstellung des mit VII bezeichneten Ausschnitts von
Figur 6 , Figur 8- zeigt in derselben Darstellung wie
Figur 7 ein weiteres Ausführungsbeispiel der Erfindung und - Figur 9
- zeigt den mit IX bezeichneten Ausschnitt von
Figur 8 in vergrößerter Darstellung.
- FIG. 1
- a fuel injection valve according to the invention with two valve needles guided in one another in longitudinal section,
- FIG. 2
- an enlargement of
FIG. 1 in the section marked II, - FIG. 3
- an enlarged view of
FIG. 2 in the section designated III, the embodiment of theFIGS. 2 and 3 represents the state of the art, - FIG. 4
- in the same representation as
FIG. 2 a first embodiment of the invention, - FIG. 5
- the section marked V of
FIG. 4 in an enlarged view, - FIGS. 5a, 5b, 5c, 5e and 5f
- show in the same representation as
FIG. 5 further embodiments of the invention,FIG. 5d shows a known from the prior art fuel injection valve, - FIG. 6
- shows a known from the prior art fuel injection valve in longitudinal section, in which case only one valve needle is provided,
- FIG. 7
- shows an enlarged view of the designated VII section of
FIG. 6 . - FIG. 8
- shows in the same illustration as
FIG. 7 a further embodiment of the invention and - FIG. 9
- shows the section of FIG. 8 designated by IX in an enlarged view.
In
In der Ventilnadel 8 ist eine Längsbohrung 11 ausgebildet, in der eine Innennadel 10 längsverschiebbar angeordnet ist. Die Innennadel 10 weist an ihrem ventilsitzseitigen Ende eine innere Ventildichtfläche 42 auf, mit der sie ebenfalls mit dem Ventilsitz 18 zusammenwirkt. Die Ventilnadel 8 und die Innennadel 10 wirken so mit dem Ventilsitz 18 zusammen, dass bei Anlage der Ventilnadel 8 auf dem Ventilsitz 18 der Druckraum 14 gegen die Einspritzöffnungen 20, 22 abgedichtet ist. Hebt die Ventilnadel 8, angetrieben durch die hydraulische Kraft auf die Druckschulter 12 und gegen eine Schließkraft, vom Ventilsitz 18 ab, so fließt Kraftstoff aus dem Druckraum 14 zwischen der Ventildichtfläche 35 und dem Ventilsitz 18 hindurch zu den Einspritzöffnungen 20 und wird durch diese hindurch in den Brennraum eingespritzt. Die Innenadel 10 bleibt bei diesem Vorgang zumindest vorerst in ihrer Schließstellung, in der sie ebenfalls durch eine Schließkraft gehalten wird. Nach dem Abheben der Ventilnadel 8 vom Ventilsitz 18 wird nun auch die Innenadel 10 vom Kraftstoffdruck beaufschlagt, was über entsprechende Druckflächen an der Innennadel 10 zu einer der Schließkraft entgegengerichteten Öffnungskraft führt. Je nach Steuerung der Schließkraft hebt die Innenadel 10 jetzt ebenfalls vom Ventilsitz 18 ab und gibt die inneren Einspritzöffnungen 22 frei oder sie bleibt durch eine entsprechend hohe Schließkraft in ihrer Schließstellung. Auf diese Weise kann durch sämtliche Einspritzöffnungen 20, 22 oder nur durch einen Teil der Einspritzöffnungen 20 Kraftstoff in den Brennraum eingespritzt werden. Durch Erhöhung der Schließkräfte oder durch Drosselung der Kraftstoffzufuhr in den Druckraum 14 wird die Einspritzung beendet und die Ventilnadel 8 und die Innenadel 10 gleiten in Längsrichtung zurück in ihre jeweilige Schließstellung in Anlage am Ventilsitz 18.In the
Um dieses Problem zu beseitigen ist das erfindungsgemäße Kraftstoffeinspritzventil beispielsweise wie in
Bei der Beschreibung der in den
Bei dem in
Die Ausnehmung 37 kann auch hier verschiedene Formen annehmen, beispielsweise eine Glockenform, wie in
Neben der rein elastischen Verformung der Dichtlippe 40 beim Schließvorgang der Ventilnadel 8 kann es auch vorgesehen sein, dass die Dichtlippe 40 plastisch verformbar ist. Beim ersten Schließvorgang des neuen Kraftstoffeinspritzventils wird die Dichtlippe 40 soweit verformt, dass die beiden Dichtkanten 26, 28 auf dem Ventilsitz 18 aufliegen, wobei dann auch die geringe Kraft entfallen kann, die nach wie vor nötig ist, die Dichtlippe 40 nach innen zu verformen. Es ist auch möglich, dass die Verformung der Dichtlippe 40 plastisch-elastisch erfolgt, also beim ersten Schließvorgang ein Teil der gesamten Verformung, die nötig ist, um die erste Dichtkante 26 in Anlage an die Ventildichtfläche 18 zu bringen, plastisch erfolgt, was die anschließend nötigen Kräfte für die elastische Verformung der Dichtlippe 40 weiter reduziert. In addition to the purely elastic deformation of the sealing
Claims (11)
- Fuel injection valve for internal combustion engines, in which is formed a valve seat (18) from which proceeds at least one injection opening (20), and having a valve needle (8) which, with a valve sealing face (35) which is formed on the valve needle (8), interacts with the valve seat (18) and thereby closes and opens the at least one injection opening (20), and having a first sealing edge (26), which is formed on the valve sealing face (35), and a second sealing edge (28), wherein in the closed position of the valve needle (8), the first sealing edge (26) bears sealingly against the valve seat (18) upstream of the at least one injection opening (20) and the second sealing edge (28) bears sealingly against the valve seat (18) downstream of the at least one injection opening (20), characterized in that the valve needle (8), at its end side facing toward the valve seat (18), has a recess (37), in such a way as to form a sealing lip (40) which can be elastically or plastically deformed inwards as a result of the contact of the valve needle (8) against the valve seat (18) and on which the second sealing edge (28) is formed, with the recess (37) being of frustoconical design.
- Fuel injection valve according to Claim 1, characterized in that the valve needle (8) has a longitudinal bore (11) and the recess (37) at the valve-seat-side end of the longitudinal bore (11) is formed as a radial widening.
- Fuel injection valve according to Claim 1, characterized in that the second sealing edge (28) is formed on the valve-seat-side end of the valve needle (8).
- Fuel injection valve according to Claim 3, characterized in that the valve needle (8) has an annular face (44) at its valve-seat-side end.
- Fuel injection valve according to Claim 1 or 2, characterized in that the sealing lip (40) has substantially a triangular shape as viewed in cross section.
- Fuel injection valve according to Claim 1 or 2, characterized in that an annular groove (24) runs between the first sealing edge (26) and the second sealing edge.
- Fuel injection valve according to Claim 6, characterized in that the annular groove (24) is formed by two conical faces (31; 32).
- Fuel injection valve according to Claim 7, characterized in that a shoulder (34) is formed between the two conical faces (31; 32).
- Fuel injection valve according to one of Claims 1 to 8, characterized in that the valve seat (18) is of substantially conical design.
- Fuel injection valve according to one of Claims 1 to 9, characterized in that the valve sealing face (35) is of substantially conical design.
- Fuel injection valve according to one of Claims 1 to 10, characterized in that the valve needle (8), as it moves towards the valve seat (18), firstly bears with the second sealing edge (28) against the valve seat (18), and the first sealing edge (26) comes into contact against the valve seat (18) only after an elastic or plastic deformation of the sealing lip (40).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10322826A DE10322826A1 (en) | 2003-05-19 | 2003-05-19 | Fuel injection valve for internal combustion engines |
PCT/DE2003/004022 WO2004104406A1 (en) | 2003-05-19 | 2003-12-06 | Fuel injection valve for combustion engines |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1627147A1 EP1627147A1 (en) | 2006-02-22 |
EP1627147B1 true EP1627147B1 (en) | 2008-03-05 |
Family
ID=33441048
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP03782138A Expired - Lifetime EP1627147B1 (en) | 2003-05-19 | 2003-12-06 | Fuel injection valve for combustion engines |
Country Status (7)
Country | Link |
---|---|
US (1) | US20070063074A1 (en) |
EP (1) | EP1627147B1 (en) |
JP (1) | JP2006514214A (en) |
KR (1) | KR20060015731A (en) |
CN (1) | CN1771389A (en) |
DE (2) | DE10322826A1 (en) |
WO (1) | WO2004104406A1 (en) |
Families Citing this family (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102004038945A1 (en) * | 2004-08-11 | 2006-02-23 | Mahle International Gmbh | Light metal piston with heat pipes |
TR200402050A2 (en) * | 2004-08-18 | 2006-03-21 | Robert Bosch Gmbh | Dual seating diameter injector with coaxial areal contact |
EP1693561B1 (en) | 2005-01-19 | 2008-03-05 | Delphi Technologies, Inc. | Fuel injector |
DE602005001261T2 (en) | 2005-01-19 | 2008-01-31 | Delphi Technologies, Inc., Troy | Fuel injector |
JP5044556B2 (en) * | 2005-08-25 | 2012-10-10 | キャタピラー インコーポレイテッド | Fuel injector with grooved check member |
CN104234900A (en) * | 2014-09-09 | 2014-12-24 | 浙江展途动力科技有限公司 | Spray hole shaft pin mixed direct driving oil sprayer |
DE102015206467A1 (en) * | 2015-02-17 | 2016-08-18 | Robert Bosch Gmbh | Injection valve for a gaseous or liquid medium and method for producing such an injection valve |
DE102015220550A1 (en) * | 2015-10-21 | 2017-04-27 | Ford Global Technologies, Llc | fuel Injector |
CN106014738A (en) * | 2016-07-12 | 2016-10-12 | 江西汇尔油泵油嘴有限公司 | Obstructing type oil injection method and oil injection nozzle |
WO2019068321A1 (en) * | 2017-10-04 | 2019-04-11 | Robert Bosch Gmbh | Injection valve for metering two fuels |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FI88333C (en) * | 1991-06-25 | 1993-04-26 | Waertsilae Diesel Int | FOERBAETTRAT INSPRUTNINGSVENTILARRANGEMANG FOER BRAENSLE |
JPH11182377A (en) * | 1997-12-24 | 1999-07-06 | Aisan Ind Co Ltd | Fuel injection valve |
DE19931891A1 (en) * | 1999-07-08 | 2001-01-18 | Siemens Ag | Fuel-injection valve for combustion engine |
ATE472677T1 (en) * | 1999-10-06 | 2010-07-15 | Delphi Tech Holding Sarl | FUEL INJECTION VALVE |
DE10000501A1 (en) * | 2000-01-08 | 2001-07-19 | Bosch Gmbh Robert | Fuel injection valve for internal combustion engines |
DE10115216A1 (en) * | 2001-03-28 | 2002-10-10 | Bosch Gmbh Robert | Fuel injection valve for internal combustion engines |
DE10122389A1 (en) * | 2001-05-09 | 2002-11-21 | Bosch Gmbh Robert | Fuel injection device for internal combustion engines |
DE10155227A1 (en) * | 2001-11-09 | 2003-05-22 | Bosch Gmbh Robert | Fuel injection valve for internal combustion engines |
-
2003
- 2003-05-19 DE DE10322826A patent/DE10322826A1/en not_active Withdrawn
- 2003-12-06 EP EP03782138A patent/EP1627147B1/en not_active Expired - Lifetime
- 2003-12-06 KR KR1020057021972A patent/KR20060015731A/en not_active Application Discontinuation
- 2003-12-06 DE DE50309349T patent/DE50309349D1/en not_active Expired - Lifetime
- 2003-12-06 JP JP2004572033A patent/JP2006514214A/en not_active Withdrawn
- 2003-12-06 WO PCT/DE2003/004022 patent/WO2004104406A1/en active IP Right Grant
- 2003-12-06 US US10/557,729 patent/US20070063074A1/en not_active Abandoned
- 2003-12-06 CN CNA2003801103132A patent/CN1771389A/en active Pending
Non-Patent Citations (1)
Title |
---|
None * |
Also Published As
Publication number | Publication date |
---|---|
CN1771389A (en) | 2006-05-10 |
EP1627147A1 (en) | 2006-02-22 |
KR20060015731A (en) | 2006-02-20 |
JP2006514214A (en) | 2006-04-27 |
DE50309349D1 (en) | 2008-04-17 |
DE10322826A1 (en) | 2004-12-09 |
WO2004104406A1 (en) | 2004-12-02 |
US20070063074A1 (en) | 2007-03-22 |
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