EP1045983B1 - Fuel injection valve for internal combustion engines - Google Patents

Fuel injection valve for internal combustion engines Download PDF

Info

Publication number
EP1045983B1
EP1045983B1 EP99969769A EP99969769A EP1045983B1 EP 1045983 B1 EP1045983 B1 EP 1045983B1 EP 99969769 A EP99969769 A EP 99969769A EP 99969769 A EP99969769 A EP 99969769A EP 1045983 B1 EP1045983 B1 EP 1045983B1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
space
fuel
spring
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
Application number
EP99969769A
Other languages
German (de)
French (fr)
Other versions
EP1045983A1 (en
Inventor
Maximilian Kronberger
Herbert Strahberger
Raphael Combe
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1045983A1 publication Critical patent/EP1045983A1/en
Application granted granted Critical
Publication of EP1045983B1 publication Critical patent/EP1045983B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • 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
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
    • F02M57/023—Injectors structurally combined with fuel-injection pumps characterised by the pump drive mechanical
    • 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
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • F02M61/205—Means specially adapted for varying the spring tension or assisting the spring force to close the injection-valve, e.g. with damping of valve lift
    • 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
    • F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
    • F02M2200/304—Fuel-injection apparatus having mechanical parts, the movement of which is damped using hydraulic means

Definitions

  • the invention relates to a combination of a Fuel injection valve and a high pressure pump for Internal combustion engine according to the preamble of claim 1.
  • Such a combination of a fuel injection valve and a high-pressure pump is known from EP 0 844 384 A.
  • the fuel injection valve axially displaceable valve member, which with his combustion chamber side end to a flow area at least an injection port opens or heads.
  • the Valve member protrudes with its combustion chamber remote end at least indirectly in a fuel-filled spring chamber in which a valve member clamped in the closing direction valve spring is clamped.
  • the Valve spring is supported at one end with its end remote from the valve Evasive piston, which during the supply of high pressure standing fuel to the fuel injection valve by one certain stroke is hineinverschiebbar in the spring chamber and the while increasing the biasing force of the valve spring.
  • the high pressure pump has a Pumping room is on and to control the high-pressure pumping an electric control valve disposed on the high-pressure pump. Due to the throttle as a connection between the spring chamber and the Fuel low pressure chamber will be the outflow of fuel from the Restricted spring space, which in addition to increasing the Preload force of the valve spring by the movement of the bypass piston in the spring chamber into a hydraulic closing force increase is effected on the valve member.
  • the inventive combination of a fuel injection valve and a high-pressure pump has the advantage that the Leadership of the bypass piston is improved and this sure his full stroke in the spring chamber and thus performs a defined Increasing the preload force of the valve spring is achieved.
  • FIG. 1 shows a longitudinal section through the essential part of the invention described Fuel injection valve for internal combustion engines.
  • the illustrated in the figure 1 embodiment of The combination of a fuel injection valve and a high-pressure pump according to the invention shows this Fuel injection valve 1 in a structural unit with the High-pressure fuel pump 3, at which an electric Control valve 5 is arranged and as a unit in a Housing 7 used to be supplied internal combustion engine is.
  • the fuel injection valve 1 has a Valve body 9 on, with its one end in a not closer to the combustion chamber to be supplied Internal combustion engine sticks out and the one with its other end with the interposition of a washer 11 axially against a valve holding body 13 is braced. This takes place this axial clamping means of a clamping nut 15, the a paragraph on the valve body 9 surrounds and in a Thread of a housing 17 of the high-pressure fuel pump 3rd is screwed.
  • the valve body 9 of Fuel injection valve 1 also has a Guide bore 19, in which a piston-shaped Valve member 21 is guided axially displaceable.
  • the Valve member 21 has in a known manner at his combustion chamber-side end of a valve sealing surface 23, with it for controlling an injection opening cross-section with a Valve seat surface 25 at the closed end of Guide bore 19 cooperates. Leading downstream the sealing cross-section between the sealing surface 23 and Valve seat surface 25 injection openings 27 of the Valve seat surface 25 from, in the combustion chamber of Internal combustion engine.
  • the valve member 21 has furthermore a pressure shoulder pointing in opening stroke direction 29 on its shaft, with it into a pressure chamber 31st projects through a cross-sectional extension of the Guide bore 19 is formed. This extends Pressure chamber to the valve seat surface 25 and is by a High-pressure fuel channel 33 with high pressure Fuel fillable.
  • valve member 21 continues to have his combustion chamber remote end on a pressure pin 35, the the intermediate disc 11 extends through and into a cross-section extended spring chamber 37 in the valve holding body 13 opens. It is at the spring-side end of the pressure pin 35 a lower spring plate 39 provided, on the other hand, a in the spring chamber 37 clamped valve spring 41 is applied, the while the valve member 21 in the closing direction for Valve seat surface 25 is acted upon.
  • This valve spring 41 supported on the other hand on an upper spring plate 43, the on his side facing away from the spring on a bypass piston 45 is present.
  • the valve member 21 dives with its thrust pin 35 in a fuel-filled damping chamber 47, by a through the end face of the intermediate disc 11 formed stationary Paragraph 49 is limited to a stroke stop for a Ring shoulder 51 on the valve member 21 forms. It is between the wall of the damping chamber 47 and the pressure pin 35 a Thru-shaped cross-section formed as a mecanicnanschliff 53rd is formed and over which the damping chamber 47 with the Spring chamber 37 is connected.
  • the consultancynanschliff 53 on the pressure pin 35 an axial distance from the annular shoulder 51 on the valve member 21, in the region of the pressure pin 35 the diameter of the receiving opening in the Washer 11 corresponds, so that a control edge 55th is formed, whose crossing over the paragraph 49 the Controlling the hydraulic damping chamber 47 controls.
  • the housing 17 of the high-pressure fuel pump 3 is connected via a Spacer 57 by means of the clamping nut 15 axially against the Valve holding body 13 clamped.
  • the High-pressure fuel pump 3 in a cylinder bore 59th axially displaceable pump piston 61, which with his immersed end face a pump working space 63 in the Cylinder bore 59 limited.
  • the pump piston 61 is the High-pressure fuel delivery from a not closer shown motor-driven cam drive via a Push rod 65 driven axially reciprocatingly.
  • this Intake space 73 leads to a first control line 75 electrical control valve 5, in a known manner as Solenoid valve is formed and not closer illustrated manner the fuel passing into a second Control line 77 depending on the operating parameters the to be supplied internal combustion engine by means of a controls electrical control unit.
  • This second Control line 77 also penetrates the housing 17 the high-pressure fuel pump 3 and opens into the Pump working space 63.
  • the hydraulic working space 81 has two different ones Diameter up, with a first smaller one Diameter range 85 constantly through the bore 79 with the Pump working space 63 of the high-pressure fuel pump 3 connected is.
  • a second, larger diameter area 87 of the hydraulic working space 81 is only after Auf interviewedn a flow area through the Lifting movement of the bypass piston 45 with the pump working space 63 connectable.
  • the bypass piston 45 has two different hydraulic force application surfaces, of which a first smaller force introduction surface 89 the first, smaller in diameter hydraulic Working space part 85 limited.
  • a second bigger one Force introduction surface 91 is on a collar 93 on Evasive piston 45 is formed and limits the larger Diameter range 87 of the hydraulic working space 81.
  • the fuel injection valve according to the invention Internal combustion engine operates in the following way.
  • During the Suction stroke of the high-pressure fuel pump 3, is at up moved pump piston 61 fuel from the suction 73rd via the first control line 75, the opened electric Control valve 5 and the second control line 77 in the Pump workspace 63 sucked.
  • the valve member 21 of the Fuel injection valve 1 is doing by the Valve spring 41 held in the closed position on the valve seat 25.
  • Beginning of the downward conveying stroke of the Pump piston 61 of the high-pressure fuel pump 3 is First, a part of the fuel from the same way the pump working space 63 in the suction 73 back promoted.
  • the electrical Control valve controls the electrical Control valve the time of the beginning and also the end the high-pressure delivery of the high-pressure fuel pump. 3 to the fuel injection valve 1.
  • the Fuel high pressure conveying and in consequence the Fuel injection at the fuel injection valve 1 through the closing of the flow cross-section between the Control lines 75 and 77 on the electric control valve. 5 initiated.
  • a high fuel pressure in Pump workspace 63 constructed, which extends over the bore 79, the channel 83 and the high-pressure fuel channel 33 to in the pressure chamber 31 continues on the fuel injection valve 1.
  • the fuel injection on the invention Fuel injection valve in a pre and a Main injection quantity divided, wherein the valve member 21st initially only a limited one during the pre-injection phase Run through the opening stroke, by passing over the Control edge 55 on the valve member 21 via the shoulder surface 49th the intermediate disc 11 is limited, as a result of the Damper chamber 47 controlled at the fuel injection valve 1 is, so that the closing force on the valve member 21st elevated.
  • the bypass piston 45 starts in the to lift off upcoming injection high pressure from its seat and by the on the first and after taking off the Ausweichkolbens 45 from the seat on the second Force introduction surface 89 and 91 now attacking High fuel pressure shifted in the direction of the spring chamber 37.
  • the size of the additional hydraulic closing force in the Spring chamber 37 and the pressure reduction can be in Dependence on the total stroke of the bypass piston 45 and the Shaft diameter of the valve member 21 through the Set the dimensioning of the throttle bore 99, wherein the Diameter of this throttle bore 99 at a stroke of Ausweichkolbens 45 from about 0.5 to imm preferably between 0.4 to 1.2mm.

Landscapes

  • 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 betrifft eine Kombination aus einem Kraftstoffeinspritzventil und einer Hochdruckpumpe für Brennkraftmaschinen nach dem Oberbegriff des Anspruchs 1.The invention relates to a combination of a Fuel injection valve and a high pressure pump for Internal combustion engine according to the preamble of claim 1.

Eine solche Kombination aus einem Kraftstoffeinspritzventil und einer Hochdruckpumpe ist durch die EP 0 844 384 A bekannt. Bei dieser bekannten Kombination weist das Kraftstoffeinspritzventil ein axial verschiebbares Ventilglied auf, das mit seinem brennraumseitigen Ende einen Durchströmquerschnitt zu wenigstens einer Einspritzöffnung auf- beziehungsweise zusteuert. Das Ventilglied ragt mit seinem brennraumfernen Ende zumindest mittelbar in einen kraftstoffgefüllten Federraum, in dem eine das Ventilglied in Schließrichtung beaufschlagende Ventilfeder eingespannt ist. Die Ventilfeder stützt sich mit ihrem ventilabgewandten Ende an einem Ausweichkolben ab, der während der Zufuhr von unter hohem Druck stehendem Kraftstoff an das Kraftstoffeinspritzventil um einen bestimmten Hubweg in den Federraum hineinverschiebbar ist und der dabei die Vorspannkraft der Ventilfeder erhöht. Zwischen dem Federraum und einem Kraftstoffniederdruckraum ist ein als Drossel ausgebildeter Verbindungskanal vorhanden, wobei der Kraftstoffniederdruckraum einen Ventilhaltekörper des Kraftstoffeinspritzventils umgibt. Die Hochdruckpumpe weist einen Pumpenarbeitsraum auf und zur Steuerung der Hochdruckförderung ist ein elektrisches Steuerventil an der Hochdruckpumpe angeordnet. Infolge der Drossel als Verbindung zwischen dem Federraum und dem Kraftstoffniederdruckraum wird das Abströmen von Kraftstoff aus dem Federraum eingeschränkt, wodurch neben der Erhöhung der Vorspannkraft der Ventilfeder durch die Bewegung des Ausweichkolbens in den Federraum hinein auch eine hydraulische Schließkrafterhöhung auf das Ventilglied bewirkt wird. Such a combination of a fuel injection valve and a high-pressure pump is known from EP 0 844 384 A. at This known combination, the fuel injection valve axially displaceable valve member, which with his combustion chamber side end to a flow area at least an injection port opens or heads. The Valve member protrudes with its combustion chamber remote end at least indirectly in a fuel-filled spring chamber in which a valve member clamped in the closing direction valve spring is clamped. The Valve spring is supported at one end with its end remote from the valve Evasive piston, which during the supply of high pressure standing fuel to the fuel injection valve by one certain stroke is hineinverschiebbar in the spring chamber and the while increasing the biasing force of the valve spring. Between the Spring chamber and a fuel low pressure chamber is on as a throttle trained connecting channel exists, wherein the Fuel low pressure chamber a valve holding body of the Surrounds fuel injector. The high pressure pump has a Pumping room is on and to control the high-pressure pumping an electric control valve disposed on the high-pressure pump. Due to the throttle as a connection between the spring chamber and the Fuel low pressure chamber will be the outflow of fuel from the Restricted spring space, which in addition to increasing the Preload force of the valve spring by the movement of the bypass piston in the spring chamber into a hydraulic closing force increase is effected on the valve member.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Kombination aus einem Kraftstoffeinspritzventil und einer Hochdruckpumpe hat demgegenüber den Vorteil, dass die Führung des Ausweichkolbens verbessert ist und dieser sicher seinen vollen Hub in den Federraum ausführt und somit eine definierte Erhöhung der Vorspannkraft der Ventilfeder erreicht wird. The inventive combination of a fuel injection valve and a high-pressure pump has the advantage that the Leadership of the bypass piston is improved and this sure his full stroke in the spring chamber and thus performs a defined Increasing the preload force of the valve spring is achieved.

Dabei ist das Vorsehen einer Drosselentlastungsbohrung des Federraumes in Verbindung mit einem das Volumen des Federraumes verkleinernden Ausweichkolbens im Ausführungsbeispiel an einer sogenannten Pumpe-Duse-Einheit dargestellt, ist jedoch auch an anderen Einspritzsystemen verwendbar, die einen Ausweichkolben am Federraum des Kraftstoffeinspritzventils vorsehen.It is the provision of a Throttle relief bore of the spring chamber in conjunction with a the volume of the spring space decreasing Ausweichkolbens in the exemplary embodiment of a so-called Pump-Duse unit is shown, however, is also on others Injection systems usable, the an alternate piston on Provide spring space of the fuel injection valve.

Weitere Vorteile und vorteilhafte Ausgestaltungen des Gegenstandes der Erfindung sind der nachfolgenden Beschreibung, der Zeichnung und den Patentansprüchen entnehmbar. Further advantages and advantageous embodiments of Subject of the invention are the following Description, the drawing and the claims removable.

Zeichnungdrawing

Ein Ausführungsbeispiel der erfindungsmäßen Kombination eines Kraftstoffeinspritzventils und einer Hochdruckpumpe ist in der Zeichnung dargestellt und wird im folgenden näher erläutert.An embodiment of the erfindungsmäßen combination of Fuel injection valve and a high-pressure pump is shown in the drawing and will be explained in more detail below.

Es zeigt die Figur 1 einen Längsschnitt durch den erfindungswesentlichen Teil des beschriebenen Kraftstoffeinspritzventils für Brennkraftmaschinen.1 shows a longitudinal section through the essential part of the invention described Fuel injection valve for internal combustion engines.

Beschreibung des AusführungsbeispielsDescription of the embodiment

Das in der Figur 1 dargestellte Ausführungsbeispiel der erfindungsgemäßen Kombination einer Kraftstoffeinsprizventils und einer Hochdruckpumpe zeigt das Kraftstoffeinspritzventil 1 in einer Baueinheit mit der Kraftstoffhochdruckpumpe 3, an der ein elektrisches Steuerventil 5 angeordnet ist und die als Baueinheit in ein Gehäuse 7 der zu versorgenden Brennkraftmaschine eingesetzt ist.The illustrated in the figure 1 embodiment of The combination of a fuel injection valve and a high-pressure pump according to the invention shows this Fuel injection valve 1 in a structural unit with the High-pressure fuel pump 3, at which an electric Control valve 5 is arranged and as a unit in a Housing 7 used to be supplied internal combustion engine is.

Das Kraftstoffeinspritzventil 1 weist dabei einen Ventilkörper 9 auf, der mit seinem einen Ende in einen nicht näher dargestellten Brennraum der zu versorgenden Brennkraftmaschine ragt und der mit seinem anderen Ende unter Zwischenschaltung einer Zwischenscheibe 11 axial gegen einen Ventilhaltekörper 13 verspannt ist. Dabei erfolgt dieses axiale Verspannen mittels einer Spannmutter 15, die einen Absatz am Ventilkörper 9 umgreift und die in ein Gewinde eines Gehäuses 17 der Kraftstoffhochdruckpumpe 3 eingeschraubt ist. Der Ventilkörper 9 des Kraftstoffeinspritzventils 1 weist weiterhin eine Führungsbohrung 19 auf, in der ein kolbenförmiges Ventilglied 21 axial verschiebbar geführt ist. Das Ventilglied 21 weist dabei in bekannter Weise an seinem brennraumseitigen Ende eine Ventildichtfläche 23 auf, mit der es zur Steuerung eines Einspritzöffnungsquerschnittes mit einer Ventilsitzfläche 25 am geschlossenen Ende der Führungsbohrung 19 zusammenwirkt. Dabei führen stromabwärts des Dichtquerschnittes zwischen Dichtfläche 23 und Ventilsitzfläche 25 Einspritzöffnungen 27 von der Ventilsitzfläche 25 ab, die in den Brennraum der Brennkraftmaschine münden. Das Ventilglied 21 weist weiterhin eine in Öffnungshubrichtung weisende Druckschulter 29 an seinem Schaft auf, mit der es in einen Druckraum 31 ragt, der durch eine Querschnittserweiterung der Führungsbohrung 19 gebildet ist. Dabei erstreckt sich dieser Druckraum bis an die Ventilsitzfläche 25 und ist durch einen Kraftstoffhochdruckkanal 33 mit unter hohem Druck stehenden Kraftstoff befüllbar. Das Ventilglied 21 weist weiterhin an seinem brennraumfernen Ende einen Druckzapfen 35 auf, der die Zwischenscheibe 11 durchragt und in einen im Querschnitt erweiterten Federraum 37 im Ventilhaltekörper 13 mündet. Dabei ist am federraumseitigen Ende des Druckzapfens 35 ein unterer Federteller 39 vorgesehen, an dem andererseits eine im Federraum 37 eingespannte Ventilfeder 41 anliegt, die dabei das Ventilglied 21 in Schließrichtung zur Ventilsitzfläche 25 hin beaufschlagt. Diese Ventilfeder 41 stützt sich andererseits an einem oberen Federteller 43 ab, der an seiner federabgewandten Seite an einem Ausweichkolben 45 anliegt.The fuel injection valve 1 has a Valve body 9 on, with its one end in a not closer to the combustion chamber to be supplied Internal combustion engine sticks out and the one with its other end with the interposition of a washer 11 axially against a valve holding body 13 is braced. This takes place this axial clamping means of a clamping nut 15, the a paragraph on the valve body 9 surrounds and in a Thread of a housing 17 of the high-pressure fuel pump 3rd is screwed. The valve body 9 of Fuel injection valve 1 also has a Guide bore 19, in which a piston-shaped Valve member 21 is guided axially displaceable. The Valve member 21 has in a known manner at his combustion chamber-side end of a valve sealing surface 23, with it for controlling an injection opening cross-section with a Valve seat surface 25 at the closed end of Guide bore 19 cooperates. Leading downstream the sealing cross-section between the sealing surface 23 and Valve seat surface 25 injection openings 27 of the Valve seat surface 25 from, in the combustion chamber of Internal combustion engine. The valve member 21 has furthermore a pressure shoulder pointing in opening stroke direction 29 on its shaft, with it into a pressure chamber 31st projects through a cross-sectional extension of the Guide bore 19 is formed. This extends Pressure chamber to the valve seat surface 25 and is by a High-pressure fuel channel 33 with high pressure Fuel fillable. The valve member 21 continues to have his combustion chamber remote end on a pressure pin 35, the the intermediate disc 11 extends through and into a cross-section extended spring chamber 37 in the valve holding body 13 opens. It is at the spring-side end of the pressure pin 35 a lower spring plate 39 provided, on the other hand, a in the spring chamber 37 clamped valve spring 41 is applied, the while the valve member 21 in the closing direction for Valve seat surface 25 is acted upon. This valve spring 41 supported on the other hand on an upper spring plate 43, the on his side facing away from the spring on a bypass piston 45 is present.

Das Ventilglied 21 taucht mit seinem Druckzapfen 35 in einen kraftstoffgefüllten Dämpfungsraum 47, der von einem durch die Stirnfläche der Zwischenscheibe 11 gebildeten ortsfesten Absatz 49 begrenzt ist, der dabei einen Hubanschlag für eine Ringschulter 51 am Ventilglied 21 bildet. Dabei ist zwischen der Wand des Dämpfungsraumes 47 und dem Druckzapfen 35 ein Drosselquerschnitt gebildet, der als Flächenanschliff 53 ausgebildet ist und über den der Dämpfungsraum 47 mit dem Federraum 37 verbunden ist. Dabei weist der Flächenanschliff 53 am Druckzapfen 35 einen axialen Abstand zur Ringschulter 51 am Ventilglied 21 auf, in dessen Bereich der Druckzapfen 35 dem Durchmesser der Aufnahmeöffnung in der Zwischenscheibe 11 entspricht, so daß eine Steuerkante 55 gebildet ist, deren Überfahren über den Absatz 49 das Zusteuern des hydraulischen Dämpfungsraumes 47 steuert.The valve member 21 dives with its thrust pin 35 in a fuel-filled damping chamber 47, by a through the end face of the intermediate disc 11 formed stationary Paragraph 49 is limited to a stroke stop for a Ring shoulder 51 on the valve member 21 forms. It is between the wall of the damping chamber 47 and the pressure pin 35 a Thru-shaped cross-section formed as a Flächenanschliff 53rd is formed and over which the damping chamber 47 with the Spring chamber 37 is connected. In this case, the Flächenanschliff 53 on the pressure pin 35 an axial distance from the annular shoulder 51 on the valve member 21, in the region of the pressure pin 35 the diameter of the receiving opening in the Washer 11 corresponds, so that a control edge 55th is formed, whose crossing over the paragraph 49 the Controlling the hydraulic damping chamber 47 controls.

Das Gehäuse 17 der Kraftstoffhochdruckpumpe 3 ist über ein Zwischenstück 57 mittels der Spannmutter 15 axial gegen den Ventilhaltekörper 13 verspannt. Dabei weist die Kraftstoffhochdruckpumpe 3 einen in einer Zylinderbohrung 59 axial verschiebbaren Pumpenkolben 61 auf, der mit seiner eingetauchten Stirnfläche einen Pumpenarbeitsraum 63 in der Zylinderbohrung 59 begrenzt. Der Pumpenkolben 61 wird zur Kraftstoffhochdruckförderung von einem nicht näher dargestellten motorangetriebenen Nockenantrieb über eine Stößelstange 65 axial hin- und hergehend angetrieben. Die Zuführung von Kraftstoff niederen Druckes erfolgt über eine Zulaufleitung 67 im Motorgehäuse 7 in einen das Kraftstoffeinspritzventil 1 umgebenden Ringraum 69, der über Filteröffnungen 71 in der Spannmutter 15 mit einem Ansaugraum 73 verbunden ist, der zwischen der Spannmutter 15 und dem Ventilhaltekörper 13 gebildet ist. Von diesem Ansaugraum 73 führt eine erste Steuerleitung 75 zum elektrischen Steuerventil 5, das in bekannter Weise als Magnetventil ausgebildet ist und in nicht näher dargestellter Weise den Kraftstoffübertritt in eine zweite Steuerleitung 77 in Abhängigkeit von den Betriebsparametern der zu versorgenden Brennkraftmaschine mittels eines elektrischen Steuergerätes steuert. Diese zweite Steuerleitung 77 durchdringt dabei ebenfalls das Gehäuse 17 der Kraftstoffhochdruckpumpe 3 und mündet in den Pumpenarbeitsraum 63. Vom Pumpenarbeitsraum 63 führt weiterhin eine Bohrung 79 ab, die in eine Durchgangsöffnung im Zwischenstück 57 mündet, die dabei einen hydraulischen Arbeitsraum 81 bildet. Zudem ist die Bohrung 79 über Verbindungskanäle 83 an den Kraftstoffhochdruckkanal 33 angeschlossen, der den Ventilkörper 9 und den Ventilhaltekörper 13 durchdringt, und so die hydraulische Verbindung zwischen dem Pumpenarbeitsraum 63 und dem Druckraum 31 beziehungsweise weiter zu dem Ventilsitz 25 herstellt.The housing 17 of the high-pressure fuel pump 3 is connected via a Spacer 57 by means of the clamping nut 15 axially against the Valve holding body 13 clamped. In this case, the High-pressure fuel pump 3 in a cylinder bore 59th axially displaceable pump piston 61, which with his immersed end face a pump working space 63 in the Cylinder bore 59 limited. The pump piston 61 is the High-pressure fuel delivery from a not closer shown motor-driven cam drive via a Push rod 65 driven axially reciprocatingly. The Supply of low pressure fuel via a Supply line 67 in the motor housing 7 in a the Fuel injector 1 surrounding annular space 69, the over Filter openings 71 in the clamping nut 15 with a Intake chamber 73 is connected, between the clamping nut 15th and the valve holding body 13 is formed. Of this Intake space 73 leads to a first control line 75 electrical control valve 5, in a known manner as Solenoid valve is formed and not closer illustrated manner the fuel passing into a second Control line 77 depending on the operating parameters the to be supplied internal combustion engine by means of a controls electrical control unit. This second Control line 77 also penetrates the housing 17 the high-pressure fuel pump 3 and opens into the Pump working space 63. From the pump working chamber 63 leads further from a bore 79, which in a through hole in the intermediate piece 57 opens, while doing a hydraulic Working space 81 forms. In addition, the bore 79 is over Connecting channels 83 to the high-pressure fuel passage 33rd connected, the valve body 9 and the Valve holding body 13 penetrates, and so the hydraulic Connection between the pump working space 63 and the Pressure chamber 31 and on to the valve seat 25th manufactures.

Der hydraulische Arbeitsraum 81 weist zwei unterschiedliche Durchmesser auf, wobei ein erster kleinerer Durchmesserbereich 85 ständig über die Bohrung 79 mit dem Pumpenarbeitsraum 63 der Kraftstoffhochdruckpumpe 3 verbunden ist. Ein zweiter, im Durchmesser größerer Bereich 87 des hydraulischen Arbeitsraumes 81 ist dabei erst nach Aufsteuern eines Durchströmquerschnittes durch die Hubbewegung des Ausweichkolbens 45 mit dem Pumpenarbeitsraum 63 verbindbar. Der Ausweichkolben 45 weist dazu zwei unterschiedliche hydraulische Krafteinleitungsflächen auf, von denen eine erste kleinere Krafteinleitungsfläche 89 den ersten, im Durchmesser kleineren hydraulischen Arbeitsraumteil 85 begrenzt. Eine zweite größere Krafteinleitungsfläche 91 ist an einem Ringbund 93 am Ausweichkolben 45 gebildet und begrenzt den größeren Durchmesserbereich 87 des hydraulischen Arbeitsraumes 81. Mit seiner unteren, der Krafteinleitungsfläche 91 abgewandten Ringstirnfläche bildet der Ringbund 93 eine Anschlagfläche 95, die zur Begrenzung der Hubbewegung des Ausweichkolbens 45 mit einer ortsfesten Hubanschlagfläche 97 zusammenwirkt. Die Hubanschlagfläche 97 ist dabei an der brennraumabgewandten Stirnfläche des Ventilhaltekörpers 13 gebildet. Mit seinem unteren, dem Pumpenarbeitsraum 63 abgewandten Ende ragt der Ausweichkolben 45 in den Federraum 37 und ist dort mit dem oberen Federteller 43 verbunden. The hydraulic working space 81 has two different ones Diameter up, with a first smaller one Diameter range 85 constantly through the bore 79 with the Pump working space 63 of the high-pressure fuel pump 3 connected is. A second, larger diameter area 87 of the hydraulic working space 81 is only after Aufsteuern a flow area through the Lifting movement of the bypass piston 45 with the pump working space 63 connectable. The bypass piston 45 has two different hydraulic force application surfaces, of which a first smaller force introduction surface 89 the first, smaller in diameter hydraulic Working space part 85 limited. A second bigger one Force introduction surface 91 is on a collar 93 on Evasive piston 45 is formed and limits the larger Diameter range 87 of the hydraulic working space 81. With its lower, the force introduction surface 91 facing away from the annular end face of the annular collar 93 forms a Stop surface 95, which limits the stroke of the Ausweichkolbens 45 with a fixed Hubanschlagfläche 97th interacts. The Hubanschlagfläche 97 is at the Brennraumabgewandten end face of the valve holding body 13th educated. With its lower, the pump working space 63 facing away from the bypass piston 45 projects into the spring chamber 37 and is connected there to the upper spring plate 43.

Zur Beeinflussung der Öffnungshubcharakteristik und somit der Charakteristik des Einspritzstrahles am Kraftstoffeinspritzventil 1 ist ein Verbindungskanal zwischen dem Federraum 37 und dem einen Kraftstoffniederdruckraum bildenden Ansaugraum 73 als Drosselbohrung 99 ausgebildet, über deren Durchmesser sich die zusätzliche hydraulische Schließkraft am Kraftstoffeinspritzventil 1 einstellen läßt.For influencing the Öffnungshubcharakteristik and thus the characteristic of the injection jet on Fuel injection valve 1 is a connection channel between the spring chamber 37 and the one Fuel low-pressure space forming intake chamber 73 than Throttle bore 99 formed over the diameter of itself the additional hydraulic closing force on Fuel injector 1 can be set.

Das erfindungsgemäße Kraftstoffeinspritzventil für Brennkraftmaschinen arbeitet in folgender Weise. Während des Saughubes der Kraftstoffhochdruckpumpe 3, wird bei nach oben bewegtem Pumpenkolben 61 Kraftstoff aus dem Ansaugraum 73 über die erste Steuerleitung 75, das geöffnete elektrische Steuerventil 5 und die zweite Steuerleitung 77 in den Pumpenarbeitsraum 63 angesaugt. Das Ventilglied 21 des Kraftstoffeinspritzventils 1 wird dabei durch die Ventilfeder 41 in Schließlage am Ventilsitz 25 gehalten. Mit Beginn des nach unten gerichteten Förderhubes des Pumpenkolbens 61 der Kraftstoffhochdruckpumpe 3 wird zunächst über den gleichen Weg ein Teil des Kraftstoffes aus dem Pumpenarbeitsraum 63 in den Ansaugraum 73 zurück gefördert. In Abhängigkeit von Betriebsparametern der zu versorgenden Brennkraftmaschine steuert das elektrische Steuerventil den Zeitpunkt des Beginnes und auch des Endes der Hochdruckförderung von der Kraftstoffhochdruckpumpe 3 zum Kraftstoffeinspritzventil 1. Dabei wird die Kraftstoffhochdruckförderung und in Folge die Kraftstoffeinspritzung am Kraftstoffeinspritzventil 1 durch das Verschließen des Durchströmquerschnittes zwischen den Steuerleitungen 75 und 77 am elektrischen Steuerventil 5 eingeleitet. In dessen Folge wird bei abwärts gerichtetem Förderhub des Pumpenkolbens 61 ein Kraftstoffhochdruck im Pumpenarbeitsraum 63 aufgebaut, der sich über die Bohrung 79, dem Kanal 83 und den Kraftstoffhochdruckkanal 33 bis in den Druckraum 31 am Kraftstoffeinspritzventil 1 fortsetzt. Dabei erfolgt dort nach Überschreiten des notwendigen Einspritzöffnungsdruckes in bekannter Weise das Öffnen des Kraftstoffeinspritzventils durch das Abheben des Ventilgliedes 21 vom Ventilsitz 25, so daß der unter hohem Druck stehende Kraftstoff aus dem Druckraum 31 über die Einspritzöffnungen 27 zur Einspritzung in den Brennraum der Brennkraftmaschine gelangt.The fuel injection valve according to the invention Internal combustion engine operates in the following way. During the Suction stroke of the high-pressure fuel pump 3, is at up moved pump piston 61 fuel from the suction 73rd via the first control line 75, the opened electric Control valve 5 and the second control line 77 in the Pump workspace 63 sucked. The valve member 21 of the Fuel injection valve 1 is doing by the Valve spring 41 held in the closed position on the valve seat 25. With Beginning of the downward conveying stroke of the Pump piston 61 of the high-pressure fuel pump 3 is First, a part of the fuel from the same way the pump working space 63 in the suction 73 back promoted. Depending on operating parameters of the too supplying internal combustion engine controls the electrical Control valve the time of the beginning and also the end the high-pressure delivery of the high-pressure fuel pump. 3 to the fuel injection valve 1. In this case, the Fuel high pressure conveying and in consequence the Fuel injection at the fuel injection valve 1 through the closing of the flow cross-section between the Control lines 75 and 77 on the electric control valve. 5 initiated. In consequence of which is at downward Delivery stroke of the pump piston 61 is a high fuel pressure in Pump workspace 63 constructed, which extends over the bore 79, the channel 83 and the high-pressure fuel channel 33 to in the pressure chamber 31 continues on the fuel injection valve 1. It takes place there after exceeding the necessary Injection opening pressure in a known manner opening the Fuel injection valve by lifting the Valve member 21 from the valve seat 25, so that the high Pressurized fuel from the pressure chamber 31 via the Injection openings 27 for injection into the combustion chamber of Internal combustion engine passes.

Dabei ist die Kraftstoffeinspritzung am erfindungsgemäßen Kraftstoffeinspritzventil in eine Vor- und eine Haupteinspritzmenge unterteilt, wobei das Ventilglied 21 während der Voreinspritzphase zunächst nur einen begrenzten Öffnungshubweg durchläuft, der durch das Überfahren der Steuerkante 55 am Ventilglied 21 über die Absatzfläche 49 der Zwischenscheibe 11 begrenzt wird, in dessen Folge der Dämpfungsraum 47 am Kraftstoffeinspritzventil 1 zugesteuert wird, so daß sich die Schließkraft auf das Ventilglied 21 erhöht. Gleichzeitig beginnt der Ausweichkolben 45 bei dem nun anstehenden Einspritzhochdruck von seinem Sitz abzuheben und wird durch den an der ersten und nach Abheben des Ausweichkolbens 45 vom Sitz an der zweiten Krafteinleitungsfläche 89 und 91 nun angreifenden Kraftstoffhochdruck in Richtung Federraum 37 verschoben. Dabei bewirkt dieses Verschieben des Ausweichkolbens 45 in Richtung Federraum 37 eine Erhöhung der Federvorspannkraft der Ventilfeder 41 und zudem aufgrund des gedrosselten Kraftstoffablaufes aus dem Federraum 37 eine Erhöhung des hydraulischen Druckes im Federraum 37 durch dessen Volumenverkleinerung, so daß die nunmehr auf das Ventilglied 21 wirkenden Gesamtschließkräfte die anliegende Öffnungskraft übersteigen und so das Ventilglied 21 an seinen Ventilsitz 25 zurückverschieben, so daß die Voreinspritzphase beendet ist. Nunmehr steigt im weiteren Verlauf des Kraftstoffhochdruckförderhubes des Pumpenkolbens 61 der Kraftstoffhochdruck im Pumpenarbeitsraum 63 und an den angeschlossenen Räumen des Kraftstoffeinspritzventils 1 weiter an, bis der für die Haupteinspritzung notwendige Einspritzöffnungsdruck erreicht wird. Dieser für die Haupteinspritzung notwendige Einspritzöffnungsdruck bestimmt sich dabei aus der nunmehr erhöhten Federkraft der Ventilfeder 41 sowie dem Gesamthub des Ausweichkolbens 45 und dem Drosseldurchmesser der Drosselbohrung 99, die die zusätzliche hydraulische Schließkraft im Federraum 37 bestimmen. Nach Überschreiten des für die Haupteinspritzung notwendigen Einspritzöffnungsdruckes erfolgt nunmehr wiederum ein Abheben des Ventilgliedes 21 vom Ventilsitz 25, so daß nun die Haupteinspritzmenge in bekannter Weise über die Einspritzöffnungen 27 zur Einspritzung gelangt. Dabei ist es durch den genannten zusätzlichen hydraulischen Schließdruck am Ventilglied 21 möglich, den notwendigen Einspritzöffnungsdruck der Haupteinspritzung etwa zu verdoppeln, so daß die Haupteinspritzmenge insbesondere bei kleinen und mittleren Drehzahlen mit einem höheren Einspritzdruck und somit in einem kürzeren Zeitintervall eingespritzt werden kann. Dabei beginnt diese Haupteinspritzphase in vorteilhafter Weise kurz vor dem Erreichen des Hubanschlages 97 durch den Ausweichkolben 45. Die Haupteinspritzung wird in bekannter Weise durch das Aufsteuern des elektrischen Steuerventils 5 beendet, bei dem die hydraulische Verbindung zwischen den Steuerleitungen 77 und 75 wieder geöffnet wird, so daß der Kraftstoffhochdruck im Pumpenarbeitsraum 63 und in den Hochdruckleitungen innerhalb des Kraftstoffeinspritzventils 1 zusammenbricht. Dabei unterstützt der zusätzliche hydraulische Schließdruck im Federraum 37, der sich infolge der Drossel 99 nur relativ langsam abbauen kann ein rasches und sicheres Schließen des Kraftstoffeinspritzventils, das heißt ein rasches und schnelles Rückverschieben des Ventilgliedes 21 in Anlage an die Ventilsitzfläche 25. In this case, the fuel injection on the invention Fuel injection valve in a pre and a Main injection quantity divided, wherein the valve member 21st initially only a limited one during the pre-injection phase Run through the opening stroke, by passing over the Control edge 55 on the valve member 21 via the shoulder surface 49th the intermediate disc 11 is limited, as a result of the Damper chamber 47 controlled at the fuel injection valve 1 is, so that the closing force on the valve member 21st elevated. At the same time, the bypass piston 45 starts in the to lift off upcoming injection high pressure from its seat and by the on the first and after taking off the Ausweichkolbens 45 from the seat on the second Force introduction surface 89 and 91 now attacking High fuel pressure shifted in the direction of the spring chamber 37. This displacement of the bypass piston 45 in Direction spring chamber 37, an increase in the spring biasing force the valve spring 41 and also due to the throttled Fuel drain from the spring chamber 37, an increase in the hydraulic pressure in the spring chamber 37 by the Volume reduction, so that now on the valve member 21 acting total closing forces the adjacent Opening force and thus exceed the valve member 21 at move back his valve seat 25, so that the Pre-injection phase is completed. Now rises in the further Course of the high-pressure fuel delivery stroke of the pump piston 61, the fuel high pressure in the pump working space 63 and at the connected spaces of the fuel injection valve. 1 continue until necessary for the main injection Injection opening pressure is reached. This one for the Main injection necessary injection opening pressure determined itself from the now increased spring force of Valve spring 41 and the total stroke of the bypass piston 45th and the throttle diameter of the throttle bore 99, which the additional hydraulic closing force in the spring chamber 37 determine. After exceeding that for the main injection necessary injection opening pressure is now in turn a lifting of the valve member 21 from the valve seat 25, so that now the main injection quantity in a known manner the injection openings 27 reaches the injection. there is it by the said additional hydraulic Closing pressure on the valve member 21 possible, the necessary Injection opening pressure of the main injection about to doubled, so that the main injection quantity in particular at small and medium speeds with a higher Injection pressure and thus in a shorter time interval can be injected. This starts this Main injection phase advantageously just before the Reaching the stroke stop 97 by the bypass piston 45th The main injection is in a known manner by the Aufsteuern the electrical control valve 5 is terminated, in the the hydraulic connection between the control lines 77 and 75 is reopened so that the fuel high pressure in the pump working space 63 and in the high-pressure lines collapses within the fuel injection valve 1. The additional hydraulic closing pressure supports this in the spring chamber 37, which is due to the throttle 99 only relatively Slowly break down can be a quick and safe closing of the Fuel injection valve, that is, a rapid and quick return movement of the valve member 21 in Appendix the valve seat surface 25.

Die Größe der zusätzlichen hydraulischen Schließkraft im Federraum 37 und deren Druckabbau läßt sich dabei in Abhängigkeit vom Gesamthub des Ausweichkolbens 45 und dem Schaftdurchmesser des Ventilgliedes 21 durch die Dimensionierung der Drosselbohrung 99 einstellen, wobei der Durchmesser dieser Drosselbohrung 99 bei einem Hubweg des Ausweichkolbens 45 von etwa 0,5 bis imm vorzugsweise zwischen 0,4 bis 1,2mm liegt.The size of the additional hydraulic closing force in the Spring chamber 37 and the pressure reduction can be in Dependence on the total stroke of the bypass piston 45 and the Shaft diameter of the valve member 21 through the Set the dimensioning of the throttle bore 99, wherein the Diameter of this throttle bore 99 at a stroke of Ausweichkolbens 45 from about 0.5 to imm preferably between 0.4 to 1.2mm.

Somit läßt sich mit dem erfindungsgemäßen Kraftstoffeinspritzventil der Einspritzöffnungsdruck am Kraftstoffeinspritzventil während der Haupteinspritzphase gegenüber herkömmlichen Kraftstoffeinspritzventilen erheblich erhöhen, ohne dazu wesentliche Änderungen an der Auslegung des Kraftstoffeinspritzventils und insbesondere der Ventilfeder 41 vornehmen zu müssen.Thus can be with the inventive Fuel injection valve the injection port pressure at Fuel injection valve during the main injection phase compared to conventional fuel injection valves increase significantly without making any significant changes to the Design of the fuel injection valve and in particular to make the valve spring 41.

Claims (6)

  1. Combination of a fuel injection valve and a high-pressure pump for internal combustion engines, the fuel injection valve (1) having an axially displaceable valve element (21) which, with its combustion-chamber end, opens or closes a through-flow cross section to at least one injection opening (27) and projects, with its end remote from the combustion chamber, at least indirectly into a spring space (37) which is filled with fuel and in which a valve spring (41) which acts on the valve element (21) in the closing direction is fixed, said valve spring (41) being supported with its end facing away from the valve element on a deflection piston (45) which, while fuel is being supplied under high pressure to the fuel injection valve (1), can be pushed into the spring space (37) by a specific stroke distance and which in the process increases the prestressing force of the valve spring (41), and having a connecting duct which is formed as a throttle (99) between the spring space (37) and a fuel low-pressure space (73), wherein the fuel low-pressure space (73) surrounds a valve-securing body (13) of the fuel injection valve (1), wherein the high-pressure pump (3) which feeds the fuel at high pressure forms, with the fuel injection valve (1), a unit which can be installed in a housing (7) of the internal combustion engine which is to be supplied, and wherein an electric control valve (5) is arranged on the high-pressure pump (3) in order to control the high-pressure feeding of the high-pressure pump, characterized in that the deflection piston (45) is guided in a hydraulic working space (81) which has two different diameters, wherein a first smaller diameter region (85) is continuously connected to the pump working space (63) of the high-pressure pump (3), and a second larger diameter region (87) cannot be connected to the pump working space (63) until after the through-flow cross section has been opened by a stroke movement of the deflection piston (45), and in that the deflection piston (45) has two different hydraulic force application faces, a first smaller force application face (89) of which bounds the first smaller diameter region of the hydraulic working space (81) and a second larger force application face (91) of which is arranged in the second larger diameter region (87) of the hydraulic working space (81).
  2. Combination according to Claim 1, characterized in that the throttle (99) is embodied as a throttle bore whose diameter is preferably in a range between 0.4 to 1.2 mm.
  3. Combination according to Claim 2, characterized in that the throttle bore (99) starts from the spring space (37) and opens into an intake space (73) which surrounds the valve-securing body (13) of the fuel injection valve and forms the fuel low-pressure space.
  4. Combination according to Claim 1, characterized in that the valve element (21) has, on its end remote from the combustion chamber, a pressure pin (35) which dips into a damping space (47) which is filled with fuel and which is bounded by a fixed shoulder (49) which forms a stroke stop for an annular shoulder (51) on the valve element (21), wherein a throttle cross section is formed between the wall of the damping space (47) and the pressure pin (35), which throttle cross section opens into the spring space (37) and can be closed during the stroke movement of the valve element (21).
  5. Combination according to Claim 1, characterized in that the deflection piston (45) has an annular collar (93) which bounds the hydraulic working space (81) and whose annular end face which faces the pump working space (63) forms the second larger force application face (91) and whose annular end face which faces away from the pump working space (63) forms a stop face (95) which interacts with a fixed stroke stop face (97) in order to bound the stroke movement of the deflection piston (45).
  6. Combination according to Claim 1, characterized in that the deflection piston has, at its end facing away from the pump working space (63), an upper disc spring (43) which projects into the spring space (37) and which forms an adjustable abutment for the valve spring (41).
EP99969769A 1998-09-30 1999-09-29 Fuel injection valve for internal combustion engines Expired - Lifetime EP1045983B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19844891 1998-09-30
DE19844891A DE19844891A1 (en) 1998-09-30 1998-09-30 Fuel injection valve for internal combustion engines
PCT/DE1999/003140 WO2000019089A1 (en) 1998-09-30 1999-09-29 Fuel injection valve for internal combustion engines

Publications (2)

Publication Number Publication Date
EP1045983A1 EP1045983A1 (en) 2000-10-25
EP1045983B1 true EP1045983B1 (en) 2005-02-23

Family

ID=7882830

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99969769A Expired - Lifetime EP1045983B1 (en) 1998-09-30 1999-09-29 Fuel injection valve for internal combustion engines

Country Status (6)

Country Link
US (1) US6305359B1 (en)
EP (1) EP1045983B1 (en)
JP (1) JP4443051B2 (en)
KR (1) KR100642172B1 (en)
DE (2) DE19844891A1 (en)
WO (1) WO2000019089A1 (en)

Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10062896B4 (en) * 2000-12-16 2009-12-17 Robert Bosch Gmbh Fuel injection device for an internal combustion engine
DE10203264A1 (en) * 2001-02-20 2002-11-07 Volkswagen Ag Fuel injection nozzle has means of damping designed so that movement of deflection piston takes place cavitation-free, with degree of damping of piston's movement increasing as piston gets nearer to corresponding end position
DE10119602A1 (en) * 2001-04-21 2002-10-24 Bosch Gmbh Robert Fuel injection unit consists of fuel pump with piston and chamber, control valve, closure spring, stop, shaft part, connecting hole and smaller and larger diameter shaft parts
DE20110130U1 (en) * 2001-06-19 2002-10-24 Robert Bosch Gmbh, 70469 Stuttgart Fuel injection device for an internal combustion engine
US6595188B2 (en) * 2001-12-04 2003-07-22 Caterpillar Inc Compact valve assembly and fuel injector using same
DE10160080A1 (en) * 2001-12-07 2003-06-26 Siemens Ag Pump-nozzle unit
DE10201529A1 (en) * 2002-01-17 2003-07-31 Volkswagen Ag Pump-nozzle element for vehicle internal combustion engine has damping piston and/or plate control edge profile joining sides, bridging angle, facing other control edge as outer edge contour
DE10207974A1 (en) * 2002-02-25 2003-09-18 Bosch Gmbh Robert Noise-optimized device for injecting fuel
WO2004057176A1 (en) 2002-12-20 2004-07-08 Volkswagen Mechatronic Gmbh & Co. Kg Pump-nozzle unit
DE10311522A1 (en) * 2003-03-17 2004-09-30 Robert Bosch Gmbh Fuel injection device for an internal combustion engine
DE102004034672A1 (en) 2004-07-17 2006-02-16 Robert Bosch Gmbh Fuel injection device for an internal combustion engine
AT501668B1 (en) * 2004-08-24 2007-03-15 Bosch Gmbh Robert CONTROL VALVE FOR AN INJECTION NOZZLE
DE102004047143A1 (en) * 2004-09-29 2006-04-06 Robert Bosch Gmbh Piezoelectric combustion chamber pressure sensor with a pressure transfer pin
DE102005004069A1 (en) 2005-01-28 2006-08-03 Volkswagen Mechatronic Gmbh & Co. Kg Injection device e.g. pump-nozzle-injection device, for e.g. diesel engine, has sealing arrangement with O-rings to effect sealing of interface, which includes sealing surface with grooves to accommodate O-rings, at cavity or channel
JP4227965B2 (en) * 2005-02-28 2009-02-18 三菱重工業株式会社 Electromagnetic control fuel injection device
JP5308477B2 (en) * 2011-05-24 2013-10-09 ヤマハ発動機株式会社 4-cycle engine

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6036772A (en) * 1983-08-10 1985-02-25 Diesel Kiki Co Ltd Fuel injection valve
JP2523759B2 (en) * 1987-02-04 1996-08-14 フエスト − アルピネ オウトモチブ ゲゼルシャフト ミットベシュレンクテル ハフツンク Fuel injection nozzle
DE3900763C2 (en) * 1989-01-12 1994-05-19 Robert Bosch Ag Wien Fuel injection nozzle, in particular pump nozzle, for an internal combustion engine
EP0404917A1 (en) * 1989-01-12 1991-01-02 VOEST-ALPINE AUTOMOTIVE Gesellschaft m.b.H. Fuel injection nozzle
DE19641824A1 (en) * 1996-10-10 1998-04-16 Bosch Gmbh Robert Fuel injection valve for internal combustion engines
GB9624513D0 (en) * 1996-11-26 1997-01-15 Lucas Ind Plc Injector
DE19706469A1 (en) * 1997-02-19 1998-08-27 Daimler Benz Ag Accumulator injection system for a multi-cylinder internal combustion engine with solenoid-controlled fuel injection valves
US5947382A (en) * 1997-06-11 1999-09-07 Stanadyne Automotive Corp. Servo controlled common rail injector

Also Published As

Publication number Publication date
WO2000019089A1 (en) 2000-04-06
JP2002525496A (en) 2002-08-13
DE19844891A1 (en) 2000-04-06
KR20010024670A (en) 2001-03-26
EP1045983A1 (en) 2000-10-25
JP4443051B2 (en) 2010-03-31
US6305359B1 (en) 2001-10-23
KR100642172B1 (en) 2006-11-03
DE59911660D1 (en) 2005-03-31

Similar Documents

Publication Publication Date Title
EP0657642B1 (en) Fuel injection device for internal combustion engines
EP1045983B1 (en) Fuel injection valve for internal combustion engines
EP1332282B1 (en) Electromagnetic valve for controlling an injection valve of an internal combustion engine
EP1613856B1 (en) Fuel injector provided with a pressure transmitter controlled by a servo valve
EP1342005B1 (en) Fuel injection system for internal combustion engines
EP1379775A1 (en) Valve for controlling liquids
DE10100390A1 (en) Injector
DE10033428A1 (en) Pressure controlled injector for injecting fuel
DE10141679A1 (en) Fuel injection device for an internal combustion engine
EP1910663B1 (en) Fuel injection device for an internal combustion engine using direct fuel injection
EP1241347A2 (en) Fuel injection system for internal combustion engines
DE10123995A1 (en) Fuel injection device has third electrically operated control valve to control second connection between pump working cavity and relief cavity
DE10307002A1 (en) Fuel injection nozzle has outer nozzle needle and control element in form of inner nozzle needle with first and second lower and higher fuel outlet cross-section positions
DE10132248A1 (en) Fuel injector with 2-way valve control
DE19843546A1 (en) Fuel injection device for internal combustion engines
EP1606511B1 (en) Fuel injection device for a combustion engine
DE10124510B4 (en) A method for driving a solenoid valve controlled fuel pump of an internal combustion engine
DE102008000596A1 (en) Common rail injector for injecting fuel into combustion chamber of internal combustion engine, has nozzle needle comprising nozzle-sided part with extension, which is axially, displaceably guided into recess or hole on nozzle body
WO2001014721A1 (en) Fuel injection device for fuel internal combustion engines
EP1370766A1 (en) Fuel-injection valve for internal combustion engines
WO2003027490A1 (en) Fuel injection device for an internal combustion engine
EP2133552B1 (en) Fuel injector
EP1284360A2 (en) Fuel injection device for an internal combustion engine
WO2005026525A1 (en) Fuel-injection valve for internal combustion engines
DE102004048322A1 (en) fuel injector

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

17P Request for examination filed

Effective date: 20001006

17Q First examination report despatched

Effective date: 20021218

RBV Designated contracting states (corrected)

Designated state(s): DE FR GB IT

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20050223

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: GERMAN

REF Corresponds to:

Ref document number: 59911660

Country of ref document: DE

Date of ref document: 20050331

Kind code of ref document: P

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20050608

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20051124

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20120920

Year of fee payment: 14

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20121008

Year of fee payment: 14

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20131121

Year of fee payment: 15

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20130929

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20140530

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20130929

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20130930

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 59911660

Country of ref document: DE

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 59911660

Country of ref document: DE

Effective date: 20150401

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150401