EP1457662B1 - Fuel injector - Google Patents
Fuel injector Download PDFInfo
- Publication number
- EP1457662B1 EP1457662B1 EP04002029A EP04002029A EP1457662B1 EP 1457662 B1 EP1457662 B1 EP 1457662B1 EP 04002029 A EP04002029 A EP 04002029A EP 04002029 A EP04002029 A EP 04002029A EP 1457662 B1 EP1457662 B1 EP 1457662B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- fuel injection
- injection valve
- coupler
- valve according
- actuator
- 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
- 239000000446 fuel Substances 0.000 title claims description 38
- 239000012530 fluid Substances 0.000 claims abstract 2
- 238000002347 injection Methods 0.000 claims description 34
- 239000007924 injection Substances 0.000 claims description 34
- 238000007789 sealing Methods 0.000 claims description 17
- 239000012528 membrane Substances 0.000 abstract description 5
- 230000005540 biological transmission Effects 0.000 description 7
- 230000008878 coupling Effects 0.000 description 5
- 238000010168 coupling process Methods 0.000 description 5
- 238000005859 coupling reaction Methods 0.000 description 5
- 230000008901 benefit Effects 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 230000004913 activation Effects 0.000 description 1
- 230000015572 biosynthetic process 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
- 230000017525 heat dissipation Effects 0.000 description 1
- 230000035515 penetration Effects 0.000 description 1
- 230000009467 reduction Effects 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
- F02M51/00—Fuel-injection apparatus characterised by being operated electrically
- F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
- F02M51/0603—Injectors peculiar thereto with means directly operating the valve needle using piezoelectric or magnetostrictive operating means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
- F02M61/167—Means for compensating clearance or thermal expansion
Definitions
- the invention relates to a fuel injection valve according to the preamble of claim 1.
- a fuel injection valve is known, which is actuated by a piezoelectric actuator.
- a hydraulic coupler is provided, in which a hydraulic medium can flow out of a coupler gap via a leakage gap to a compensation chamber.
- the compensation chamber is bounded by a membrane formed as a corrugated tube.
- piezo high-pressure injection valves which use fuel as a coupling medium.
- fuel as a coupling medium.
- the fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage that disturbing changes in length can be avoided by improving the temperature compensation.
- a first compensation chamber of the hydraulic coupler can be separated from a second compensation chamber. Since the actuator is housed in an actuator housing, the hydraulic medium can be acted upon directly by a piston, without causing any sealing problems. In this case, a membrane-like boundary of the compensation chamber is provided, which compensates for the volume difference in the compensation chamber.
- a preloaded compression spring is arranged between the actuator housing and the bottom plate, the hydraulic medium in the rest position of the piezoelectric actuator can always flow into the coupler gaps. Due to the sealing of the two compensation chambers, a simple electrical supply line from the outside to the piezoelectric actuator can be set, which avoids sealing problems and allows reliable operation of the fuel injection valve.
- a fuel injection valve 1 shown in longitudinal section in FIG. 1 has a valve housing 2 which surrounds a piezoelectric actuator 3.
- the actuator 3 is in turn housed in an actuator housing 4 and is supported with an end face 6 on a sealing plate 5, which is part of the actuator housing 4.
- On an opposite end face 7 of the actuator 3 is located on a transmission pin 8.
- the transmission pin 8 has a radially projecting collar 9, on which a pressurized biasing spring 10 is supported.
- the biasing spring 14 is clamped between the collar 9 and an inwardly projecting collar 11 on the actuator housing 4, wherein it acts on the actuator 3 in the direction of the sealing plate 5 with a compressive force.
- valve needle 14 In the axial extension of the transmission bolt 8 is a valve needle 14 which carries at its end remote from the transmission pin 8 a valve closing body 15.
- the discharge valve 17 is formed in the example opening to the outside, but can also be designed to open inwardly.
- a return spring 18 acts on the valve needle 14 with a restoring force in the direction of a closed position of the ejection valve 17.
- the valve housing 2 is sleeve-shaped. Valve side, a bottom 19 is provided, which has a central receiving bore 21. In the central receiving bore 21 a likewise sleeve-shaped projection 20 is inserted. The projection 20 receives the valve needle 14.
- valve housing 2 An end face of the valve housing 2 opposite the bottom 19 is closed by a cover 22.
- cover 22 In the cover 22 there is a supply line 23 for the attached via the ejection valve 17 fuel, which leads to a hollow interior 24 of the fuel injection valve 1.
- a bottom plate 28 is inserted into the valve housing 2.
- the bottom plate 28 is firmly connected to the valve housing 2.
- a longitudinal groove 23a in the bottom plate 28 connects the Supply line 23 to the interior 24, so that the interior 24 is always filled with fuel.
- the actuator housing 4 is surrounded by a sleeve-shaped sealing housing 29 which has a base plate 30 with a passage opening 31 for the axial penetration of the transmission bolt 8.
- a sleeve-shaped sealing membrane 33 is provided, which surrounds the transmission pin 8 partially and prevents fuel from the interior 24 can penetrate into a located within the sealing housing 29 sealing space 34.
- One of the base plate 30 opposite open end of the sealing housing 29 is completely covered by the bottom plate 28.
- a central blind bore 36 is provided in the bottom plate 28.
- a cylindrical nose 37 which partially engages in the blind bore 36 and thereby forms a piston of a hydraulic coupler 40.
- a first coupler diaphragm 41 which is formed hütsenförmig example, by a corrugated tube.
- the first coupler diaphragm 41 is welded on the one hand to the actuator housing 4 on the other hand to the bottom plate 28, so that within the first coupler diaphragm 41, a first compensation chamber 42 is formed.
- a recess 43 is inserted into the bottom plate 28, in which a second coupling membrane 44 is arranged, the valve side, a second compensation chamber 45 limited.
- the second coupler membrane 44 is cup-shaped and first inserted into the recess 43 with a closed underside of the cup.
- a side surface 44a of the second coupler diaphragm 44 is sealingly fixed to the bottom plate 28 at the end.
- the second compensation chamber 45 is connected to the first compensation chamber 42 via an inserted in the bottom plate 28 through opening 46, which serves as a throttle opening.
- first and second compensation chamber 42, 55 is a hydraulic medium, which preferably has a high viscosity and a high vapor pressure in order to ensure a low tendency to vapor bubble formation at reduced pressure.
- An electrical connection line 48 is axiar mein by the cover 22 and the bottom plate 28 in the sealing space 34 between the actuator housing 4 and sealing housing 29 out and from there radially inwardly to the actuator.
- the second embodiment of a fuel injection valve 1 shown in Figure 2 differs only slightly. Identical or equivalent features are identified by the same reference numerals.
- a difference from Figure 1 is that a coaxially projecting from the base plate 30 tube 53 serves as a piston 37. A formed between the tube 53 and the bottom plate 28. Distance represents the coupler gap 50.
- a coupler spring 52 ensures that a sufficient coupler gap 50 always forms in the rest position.
- the tube 53 extends through a bore 54 through to the second coupling diaphragm 44 and limited together with this and the bottom plate 28, the second compensation chamber 45.
- a resulting between pipe 53 and bore 54 gap 55 is analogous to the passage opening 46 as a first compensation space 42, the electrical supply line 48 is in this case over the cover 22 coaxial with the interior of the tube 53 and from there through the actuator housing 4 to the actuator 3 out.
- the second coupler diaphragm 44 is arranged as a double sleeve between the bottom plate 28 and the tube 53, wherein the double sleeve are formed by two mutually parallel axial corrugated tubes, which are interconnected via an annular surface 57.
- the annular surface 57 is acted upon by a diaphragm spring 51 in the direction of the bottom plate 28 and the coupler medium located in the second compensation chamber 45.
- the function of the fuel injection valve 1 is as follows:
- the discharge valve 17 assumes the closed position shown in Figure 1, in which the valve needle 14 is urged by the return spring 18 against the valve seat surface 16.
- a coupler gap 50 filled with coupler medium is formed between the piston 37 and the bottom plate 28, which opens via an annular gap 56 on the radial outer side of the piston 37 into the first compensation chamber 42.
- a diaphragm spring 51 acts on the second coupling diaphragm 44 with a pressure force such that a predetermined pressure prevails within the hydraulic medium. If the piezoelectric actuator 3 is acted upon by voltage, it expands abruptly and transmits this elongation to the transmission bolt 8 and the valve needle 14, so that the ejection valve 17 opens.
- the actuator 3 is supported on the bottom plate 28 via the piston 37 and the hydraulic medium located in the coupler gap 50.
- hydraulic medium flows slowly via the leakage gap 51 into the first compensation chamber 42.
- a balance of hydraulic medium takes place.
- the sleeve or cup-like design of the actuator housing 4, sealing housing 29 and valve housing 2 allows a simple production of the fuel injection valve I, for example by using thermoformed sleeves.
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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)
Abstract
Description
Die Erfindung geht aus von einem Brennstoffeinspritzventil nach der Gattung des Anspruchs 1. Aus der DE 35 33 085 A1 ist ein Brennstoffeinspritzventil bekannt, das von einem Piezo-Aktor betätigt wird. Zur Kompensation von Temperatureinflüssen, Verschleiß und Fertigungstoleranzen ist ein hydraulischer Koppler vorgesehen, bei dem ein Hydraulikmedium aus einem Kopplerspalt über einen Leckspalt zu einem Ausgleichsraum abfließen kann. Der Ausgleichsraum wird dabei von einer als Wellrohr gebildeten Membran begrenzt.The invention relates to a fuel injection valve according to the preamble of claim 1. From DE 35 33 085 A1 discloses a fuel injection valve is known, which is actuated by a piezoelectric actuator. To compensate for temperature influences, wear and manufacturing tolerances, a hydraulic coupler is provided, in which a hydraulic medium can flow out of a coupler gap via a leakage gap to a compensation chamber. The compensation chamber is bounded by a membrane formed as a corrugated tube.
Daneben sind auch Piezo-Hochdruckeinspritzventile bekannt, die als Koppelmedium Kraftstoff verwenden. Infolge der Wärmeabgabe des Aktors und des Unterdrucks im Koppler können sich dabei Dampfblasen im Koppelmedium bilden.In addition, piezo high-pressure injection valves are known which use fuel as a coupling medium. As a result of the heat emission of the actuator and the negative pressure in the coupler vapor bubbles can form in the coupling medium.
Grundsätzliche Probleme ergeben sich für Piezo-Hochdruckeinspritzventile mit hydraulischem Koppler in den Betriebszuständen Kaltstart, Heißstart, Notlauf und niedrigem Systemdruck. In Abhängigkeit des Betriebszustandes können sich lange Ansteuerzeiten ergeben, die einen erhöhten Leckageverlust am Koppler zur Folge haben und dadurch einen Hubverlust an der Ventilnadel bewirken.Fundamental problems arise for piezo high-pressure injection valves with hydraulic coupler in the operating states cold start, hot start, emergency and low system pressure. Depending on the operating state, long activation times can result, which result in increased leakage loss at the coupler and thereby cause a loss of lift at the valve needle.
Die für den Betrieb eines Brennstoffeinspritzventils erforderliche Energie zum Ansteuern des Piezo-Aktors wird in Wärme umgewandelt. Diese Wärme kann unerwünschte Dehnungen im Brennstoffeinspitzventil zur Folge haben. Zudem können erhöhte Leckageverluste am hydraulischen Koppler auftreten, die zu einer Verringerung der maximalen Einspritzmenge führen. Es ist daher erforderlich, die Wärmeabfuhr noch weiter zu verbessern und dabei den Gesamtaufbau des Brennstoffeinspritzventils einfach zu halten und ein ausreichendes Abspritzverhalten möglichst in allen Betriebszuständen sicherzustellen.The energy required to operate the fuel injector to drive the piezo actuator is converted to heat. This heat can result in undesirable expansions in the fuel injector valve. In addition, increased leakage losses can occur at the hydraulic coupler, which leads to a reduction of the lead maximum injection quantity. It is therefore necessary to improve the heat dissipation even further while keeping the overall structure of the fuel injection valve simple and to ensure a sufficient Abspritzverhalten possible in all operating conditions.
Das erfindungsgemäße Brennstoffeinspritzventil mit den kennzeichnenden Merkmalen des Anspruchs 1 hat den Vorteil, dass durch eine Verbesserung des Temperaturausgleichs störende Längenänderungen vermieden werden.The fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage that disturbing changes in length can be avoided by improving the temperature compensation.
Durch die in den abhängigen Ansprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen des im Anspruch 1 angegebenen Brennstoffeinspritzventils möglich.The measures listed in the dependent claims advantageous refinements and improvements of claim 1 fuel injection valve are possible.
Sofern im Ventilgehäuse eine Bodenplatte vorgesehen ist, lässt sich ein erster Ausgleichsraum des hydraulischen Kopplers von einem zweiten Ausgleichsraum trennen. Da der Aktor in einem Aktorgehäuse untergebracht ist, kann das Hydraulikmedium direkt von einem Kolben beaufschlagt werden, ohne dass es zu Dichtproblemen kommt. Dabei ist eine membranartige Begrenzung des Ausgleichsraums vorgesehen, die Volumenunterschied im Ausgleichsraum ausgleicht. Indem zwischen dem Aktorgehäuse und der Bodenplatte eine vorgespannte Druckfeder angeordnet ist, kann das Hydraulikmedium in der Ruhelage des Piezoaktors stets in die Kopplerspalte nachfließen. Auf Grund der Abdichtung der beiden Ausgleichsräume lässt sich eine einfache elektrische Zuleitung von außen zum Piezoaktor legen, die Dichtprobleme vermeidet und einen zuverlässigen Betrieb des Brennstoffeinspritzventils erlaubt.If a bottom plate is provided in the valve housing, a first compensation chamber of the hydraulic coupler can be separated from a second compensation chamber. Since the actuator is housed in an actuator housing, the hydraulic medium can be acted upon directly by a piston, without causing any sealing problems. In this case, a membrane-like boundary of the compensation chamber is provided, which compensates for the volume difference in the compensation chamber. By a preloaded compression spring is arranged between the actuator housing and the bottom plate, the hydraulic medium in the rest position of the piezoelectric actuator can always flow into the coupler gaps. Due to the sealing of the two compensation chambers, a simple electrical supply line from the outside to the piezoelectric actuator can be set, which avoids sealing problems and allows reliable operation of the fuel injection valve.
Ausführungsbeispiele der Erfindung sind in der Zeichnung vereinfacht dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen:
- Figur 1
- eine schematische Schnittdarstellung eines ersten, bevorzugten Ausführungsbeispiels eines erfindungsgemäßen Brennstoffeinspritzventils,
- Figur 2
- eine schematische Schnittdarstellung eines zweiten Ausführungsbeispiels eines erfindungsgemäßen Brennstoffeinspritzventils.
- FIG. 1
- a schematic sectional view of a first preferred embodiment of a fuel injection valve according to the invention,
- FIG. 2
- a schematic sectional view of a second embodiment of a fuel injection valve according to the invention.
Ein in Figur 1 im Längsschnitt dargestelltes Brennstoffeinspritzventil 1 hat ein Ventilgehäuse 2, das einen piezoelektrischen Aktor 3 umgibt. Der Aktor 3 ist seinerseits in einem Aktorgehäuse 4 untergebracht und stützt sich mit einer Stirnseite 6 an einer Dichtplatte 5 ab, die Teil des Aktorgehäuses 4 ist. Auf einer gegenüberliegenden Stirnseite 7 liegt der Aktor 3 an einem Übertragungsbolzen 8 an. Der Übertragungsbolzen 8 hat einen radial vorspringenden Bund 9, an dem sich eine unter Druck stehende Vorspannfeder 10 abstützt. Die Vorspannfeder 14 ist zwischen dem Bund 9 und einem nach innen vorspringenden Kragen 11 am Aktorgehäuse 4 eingespannt, wobei sie den Aktor 3 in Richtung zur Dichtplatte 5 mit einer Druckkraft beaufschlagt.A fuel injection valve 1 shown in longitudinal section in FIG. 1 has a valve housing 2 which surrounds a
In axialer Verlängerung des Übertragungsbolzens 8 befindet sich eine Ventilnadel 14, die an ihrem dem Übertragungsbolzen 8 abgewandten Ende einen Ventilschließkörper 15 trägt. Der Ventilschließkörper 15 bildet zusammen mit einer am Ventilgehäuse 2 ausgebildeten Ventilsitzfläche 16 in bekannter Weise ein Abspritzventü 17. Das Abspritzventil 17 ist im Beispielsfall nach außen öffnend ausgebildet, kann jedoch auch nach innen öffnend ausgeführt sein. Eine Rückstellfeder 18 beaufschlagt die Ventilnadel 14 mit einer Rückstellkraft in Richtung auf eine Schließstellung des Abspritzventils 17.In the axial extension of the transmission bolt 8 is a
Das Ventilgehäuse 2 ist hülsenförmig ausgebildet. Ventilseitig ist ein Boden 19 vorgesehen, der eine zentrale Aufnahmebohrung 21 aufweist. In die zentrale Aufnahmebohrung 21 ist ein ebenfalls hülsenförmiger Ansatz 20 eingesetzt. Der Ansatz 20 nimmt die Ventilnadel 14 auf.The valve housing 2 is sleeve-shaped. Valve side, a
Eine dem Boden 19 gegenüberliegende Stirnseite des Ventilgehäuses 2 ist mit einem Deckel 22 verschlossen. In dem Deckel 22 befindet sich eine Zuleitung 23 für den über das Abspritzventil 17 beigemessenen Kraftstoff, die zu einem hohlen Innenraum 24 des Brennstoffeinspritzventils 1 führt. Zwischen Deckel 22 und Innenraum 24 ist eine Bodenplatte 28 in das Ventilgehäuse 2 eingesetzt. Die Bodenplatte 28 ist dabei fest mit dem Ventilgehäuse 2 verbunden. Eine Längsnut 23a in der Bodenplatte 28 verbindet die Zuleitung 23 mit dem Innenraum 24, so daß der Innenraum 24 stets mit Kraftstoff gefüllt ist.An end face of the valve housing 2 opposite the
Das Aktorgehäuse 4 ist von einem hülsenförmigen Dichtgehäuse 29 umgeben, das eine Grundplatte 30 mit einer Durchgangsöffnung 31 zum axialen Durchgriff des Übertragungsbolzens 8 hat. Zwischen der Grundplatte 30 und einem Absatz 32 an der Ventilnadel 14 ist eine hülsenförmige Dichtmembran 33 vorgesehen, die den Übertragungsbolzen 8 teilweise umgibt und verhindert, dass Kraftstoff aus dem Innenraum 24 in einen innerhalb des Dichtgehäuses 29 befindlichen Dichtraum 34 eindringen kann. Ein der Grundplatte 30 gegenüberliegendes offenes Ende des Dichtgehäuses 29 ist durch die Bodenplatte 28 vollständig abgedeckt.The
Im Ausführungsbeispiel nach Figur 1 ist in der Bodenplatte 28 eine zentrale Sackbohrung 36 vorgesehen. An der Dichtplatte 5 des Aktorgehäuses 4 springt eine zylindrische Nase 37 vor, die teilweise in die Sackbohrung 36 eingreift und dabei einen Kolben eines hydraulischen Kopplers 40 bildet. Zwischen Bodenplatte 28 und Aktorgehäuse 4 erstreckt sich parallel zur Nase 37 eine erste Kopplermembran 41, die hütsenförmig beispielsweise durch ein Wellrohr gebildet ist. Die erste Kopplermembran 41 ist einerseits mit dem Aktorgehäuse 4 andererseits mit der Bodenplatte 28 verschweißt, so dass innerhalb der ersten Kopplermembran 41 ein erster Ausgleichsraum 42 gebildet ist.In the embodiment of Figure 1, a central
Auf einer dem Deckel 22 zugewandten Seite der Bodenplatte 28 ist eine Vertiefung 43 in die Bodenplatte 28 eingebracht, in der eine zweite Kopplermembran 44 angeordnet ist, die ventilseitig einen zweiten Ausgleichsraum 45 begrenzt. Die zweite Kopplermembran 44 ist napfförmig und mit einer geschlossenen Unterseite des Napfes zuerst in die Vertiefung 43 eingesetzt. Eine Seitenfläche 44a der zweiten Kopplermembran 44 ist endseitig an der Bodenplatte 28 dichtend befestigt. Der zweite Ausgleichsraum 45 ist mit dem ersten Ausgleichsraum 42 über eine in der Bodenplatte 28 eingebrachte Durchgangsöffnung 46 verbunden, die als Drosselöffnung dient.On a
Im ersten und zweiten Ausgleichsraum 42, 55 befindet sich ein Hydraulikmedium, das vorzugsweise eine hohe Viskosität und einen hohen Dampfdruck hat, um eine geringe Neigung zur Dampfblasenbildung bei Unterdruck zu gewährleisten.In the first and
Eine elektrische Anschlussleitung 48 ist axiardurch den Deckel 22 und die Bodenplatte 28 in den Dichtraum 34 zwischen Aktorgehäuse 4 und Dichtgehäuse 29 geführt und von dort radial nach innen zum Aktor 3.An
Das in der Figur 2 gezeigte zweite Ausführungsbeispiel eines Brennstoffeinspritzventils 1 unterscheidet sich demgegenüber nur geringfügig. Gleiche bzw. gleich wirkende Merkmale sind durch die gleichen Bezugszeichen gekennzeichnet. Ein Unterschied zur Figur 1 besteht darin, dass ein von der Grundplatte 30 koaxial vorspringes Rohr 53 als Kolben 37 dient. Ein sich zwischen dem Rohr 53 und der Bodenplatte 28 gebildeter. Abstand stellt den Kopplerspalt 50 dar. Eine Kopplerfeder 52 stellt sicher, dass sich in der Ruhestellung stets ein ausreichender Kopplerspalt 50 bildet. Das Rohr 53 erstreckt sich durch eine Bohrung 54 hindurch bis zur zweiten Kopplennembran 44 und begrenzt zusammen mit dieser und der Bodenplatte 28 den zweiten Ausgleichsraum 45. Ein sich zwischen Rohr 53 und Bohrung 54 ergebender Spalt 55 dient analog zur Durchgangsöffnung 46 als eine den ersten Ausgleichsraum 42 mit dem zweiten Ausgleichsraum 45 verbindende Drosselöffnung 46, 55. Die elektrische Zuleitung 48 wird hierbei über den Deckel 22 koaxial zum Inneren des Rohrs 53 und von dort durch das Aktorgehäuse 4 zum Aktor 3 geführt. Die zweite Kopplermembran 44 ist als Doppelhülse zwischen der Bodenplatte 28 und dem Rohr 53 angeordnet, wobei die Doppelhülse durch zwei parallel zueinander liegende axiale Wellrohre gebildet sind, die über eine Ringfläche 57 miteinander verbunden sind. Die Ringfläche 57 ist von einer Membranfeder 51 in Richtung auf die Bodenplatte 28 und das im zweiten Ausgleichsraum 45 befindliche Kopplermedium beaufschlagt ist.The second embodiment of a fuel injection valve 1 shown in Figure 2, however, differs only slightly. Identical or equivalent features are identified by the same reference numerals. A difference from Figure 1 is that a coaxially projecting from the
Die Funktion des Brennstoffeinspritzventils 1 wie folgt:The function of the fuel injection valve 1 is as follows:
Bei unbeaufschlagtem Aktor 3 nimmt das Abspritzventil 17 die in der Figur 1 gezeigte Schließstellung ein, in der die Ventilnadel 14 durch die Rückstellfeder 18 gegen die Ventilsitzfläche 16 gedrängt wird. In der Aufnahmebohrung 36 ist zwischen dem Kolben 37 und der Bodenplatte 28 ein mit Kopplermedium angefüllter Kopplerspalt 50 gebildet, der über einen Ringspalt 56 an der radialen Außenseite des Kolbens 37 in den ersten Ausgleichsraum 42 mündet. Eine Membranfeder 51 beaufschlagt die zweite Kopplermembran 44 derart mit einer Druckkraft, dass innerhalb des Hydraulikmediums ein vorbestimmter Druck herrscht. Wird der Piezoaktor 3 mit Spannung beaufschlagt, dehnt er sich schlagartig aus und überträgt diese Längung auf den Übertragungsbolzen 8 und die Ventilnadel 14, so dass sich das Abspritzventil 17 öffnet. Dabei stützt sich der Aktor 3 über den Kolben 37 und das im Kopplerpalt 50 befindliche Hydraulikmedium an der Bodenplatte 28 ab. Infolge des hohen Drucks im Kopplerspalt 50 fließt Hydraulikmedium langsam über den Leckspalt 51 in den ersten Ausgleichsraum 42 ab. Über die Drosselöffnungen 46 beim Ausführungsbeispiel nach Figur 1 bzw. 56 nach Figur 2 findet ein Ausgleich von Hydraulikmedium statt.When
Die hülsen- bzw. napfartige Ausbildung von Aktorgehäuse 4, Dichtgehäuse 29 und Ventilgehäuse 2 gestattet eine einfach Herstellung des Brennstoffeinspritzventils I beispielsweise durch Verwendung von Tiefziehhülsen.The sleeve or cup-like design of the
Claims (17)
- Fuel injection valve having a piezo-electric, electro-strictive or magneto-strictive actuator (3), a valve needle (14) which is operatively connected to the actuator (3) for the purpose of actuating a valve closing body (15), and a hydraulic coupler (40) which comprises a plunger (37) which engages at least partially in a receptacle opening and forms with it a coupler gap (50, 51) which is filled with a hydraulic fluid and is surrounded by a first equalization space (52) which is bounded by a first coupler diaphragm (41), characterized in that the hydraulic coupler (40) has a second equalization space (45) which is bounded by a second coupler diaphragm (44) and is connected to the first equalization space (45) via at least one through-opening (46, 55).
- Fuel injection valve according to Claim 1, characterized in that the first equalization space (52) is formed between a coupler housing (5) and a base plate (28) which is fixed to the housing.
- Fuel injection valve according to Claim 2, characterized in that the second equalization space (45) is formed on a side of the base plate (28) facing away from the actuator (3).
- Fuel injection valve according to Claim 2 or 3, characterized in that the first coupler diaphragm (41) is arranged in a sleeve shape between the actuator housing (4) and the base plate (28).
- Fuel injection valve according to Claim 3, characterized in that the second equalization space (45) is formed in a depression (43) in the base plate (28).
- Fuel injection valve according to Claim 5, characterized in that the second coupler diaphragm (44) is arranged inside the depression (43).
- Fuel injection valve according to Claim 6, characterized in that the first coupler diaphragm (41) and the second coupler diaphragm (44) are each formed by a corrugated tube having radial expansion folds.
- Fuel injection valve according to Claim 7, characterized in that the throttle opening (46) is formed axially in the base plate (28).
- Fuel injection valve according to Claim 8, characterized in that a plunger (37) which protrudes axially in the direction of the base plate (28), engages in a receptacle bore (36) in the base plate (28) and forms an annular gap (56) with the receptacle bore (36) is attached to the sealing plate (5).
- Fuel injection valve according to Claim 9, characterised in that the throttle opening (46) is embodied as a separate, axial through-bore.
- Fuel injection valve according to Claim 10,
characterized in that the actuator housing (4) is surrounded radially by a sealing housing (29) which disconnects the actuator (3) from an interior space (24) of the fuel injection valve (1) and which forms a sealed space (34) between the sealed housing (29) and the actuator housing (4). - Fuel injection valve according to Claim 11, characterized in that an electrical feed line (48) for the actuator (3) leads axially through the base plate (28) and into the sealed space (34) and from there through the actuator housing (4) and to the actuator (3) .
- Fuel injection valve according to Claim 8, characterized in that an axial bore (54) in which a tube (53) which is attached to the sealing plate (5) is guided is formed in the base plate (28).
- Fuel injection valve according to Claim 13, characterized in that the second coupler diaphragm (44) is arranged as a double sleeve between the base plate (28) and the tube (53), wherein the double sleeve is formed by two parallel axial corrugated tubes which are connected to one another by means of an annular face (57).
- Fuel injection valve according to Claim 14, characterized in that the annular face (57) is loaded by a diaphragm spring (51) in the direction of the base plate (28) and the coupler medium located in the second equalization space (45).
- Fuel injection valve according to Claim 15, characterized in that the electrical feed line (48) for the actuator (3) is led through the tube (51) to the actuator housing (4) and from there to the actuator (3).
- Fuel injection valve according to one of the preceding claims, characterized in that a coupler spring (52) is arranged between the actuator housing (4) and base plate (28).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE10310297A DE10310297A1 (en) | 2003-03-10 | 2003-03-10 | Fuel injector |
| DE10310297 | 2003-03-10 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP1457662A1 EP1457662A1 (en) | 2004-09-15 |
| EP1457662B1 true EP1457662B1 (en) | 2006-01-18 |
Family
ID=32748176
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP04002029A Expired - Lifetime EP1457662B1 (en) | 2003-03-10 | 2004-01-30 | Fuel injector |
Country Status (3)
| Country | Link |
|---|---|
| EP (1) | EP1457662B1 (en) |
| AT (1) | ATE316205T1 (en) |
| DE (2) | DE10310297A1 (en) |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE502004002760D1 (en) * | 2003-09-08 | 2007-03-15 | Siemens Ag | INJECTION VALVE FOR THE INJECTION OF FUEL INTO A COMBUSTION ENGINE |
| DE602005020172D1 (en) * | 2005-12-12 | 2010-05-06 | Continental Automotive Italy S | Injection valve and manufacturing method of such an injection valve |
| DE102007008901B4 (en) * | 2007-02-23 | 2008-10-16 | Compact Dynamics Gmbh | Fluid injection valve |
| DE102007053423A1 (en) * | 2007-11-09 | 2009-05-14 | Robert Bosch Gmbh | Piezoelectric actuator module |
| DE102009046356A1 (en) * | 2009-11-03 | 2011-05-05 | Robert Bosch Gmbh | Actuator module and fuel injector |
| DE102011087005A1 (en) * | 2011-11-24 | 2013-05-29 | Robert Bosch Gmbh | Valve for metering a flowing medium |
| CN107091355B (en) * | 2017-06-28 | 2023-05-30 | 哈尔滨工程大学 | Bypass type piezoelectric type external guide gas injection valve with axial air inlet |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10030232A1 (en) * | 2000-06-20 | 2002-01-17 | Siemens Ag | Device for transmitting a movement with play compensation |
| DE10140796A1 (en) * | 2001-08-20 | 2003-03-06 | Bosch Gmbh Robert | Fuel injector |
| DE50312340D1 (en) * | 2002-04-22 | 2010-03-04 | Continental Automotive Gmbh | DOSING DEVICE FOR FLUIDS, ESPECIALLY MOTOR VEHICLE INJECTION VALVE |
-
2003
- 2003-03-10 DE DE10310297A patent/DE10310297A1/en not_active Withdrawn
-
2004
- 2004-01-30 AT AT04002029T patent/ATE316205T1/en not_active IP Right Cessation
- 2004-01-30 DE DE502004000246T patent/DE502004000246D1/en not_active Expired - Lifetime
- 2004-01-30 EP EP04002029A patent/EP1457662B1/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| DE10310297A1 (en) | 2004-09-23 |
| EP1457662A1 (en) | 2004-09-15 |
| ATE316205T1 (en) | 2006-02-15 |
| DE502004000246D1 (en) | 2006-04-06 |
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