EP1657428B1 - Fuel injection apparatus - Google Patents

Fuel injection apparatus Download PDF

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Publication number
EP1657428B1
EP1657428B1 EP05106765A EP05106765A EP1657428B1 EP 1657428 B1 EP1657428 B1 EP 1657428B1 EP 05106765 A EP05106765 A EP 05106765A EP 05106765 A EP05106765 A EP 05106765A EP 1657428 B1 EP1657428 B1 EP 1657428B1
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EP
European Patent Office
Prior art keywords
pressure
damping
fuel
space
chamber
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 - Fee Related
Application number
EP05106765A
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German (de)
French (fr)
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EP1657428A1 (en
Inventor
Hans-Christoph Magel
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP1657428A1 publication Critical patent/EP1657428A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M57/025—Injectors structurally combined with fuel-injection pumps characterised by the pump drive hydraulic, e.g. with pressure amplification
    • F02M57/026—Construction details of pressure amplifiers, e.g. fuel passages or check valves arranged in the intensifier piston or head, particular diameter relationships, stop members, arrangement of ports or conduits
    • 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
    • F02M57/025—Injectors structurally combined with fuel-injection pumps characterised by the pump drive hydraulic, e.g. with pressure amplification
    • 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/105—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive hydraulic drive

Definitions

  • the invention relates to a device for injecting fuel into a combustion chamber of an internal combustion engine with a fuel injector, according to the features of the preamble of claim 1.
  • a fuel injection device with a fuel injector with the features of the preamble is made WO 2004/088122 A1 and WO 2004/003377 A1 out.
  • the fuel injector in this case has an injection valve member with a nozzle needle, a pressure booster with a pressure booster piston and a metering valve device, wherein the pressure booster is controlled by means of the metering valve device.
  • the pressure intensifier piston is exposed to a pressure booster working space, a pressure booster control chamber and a pressure booster pressure space.
  • the injection valve member is exposed by means of a rear pressure surface of a nozzle spring chamber, which communicates via a control line, which includes a throttle, with the pressure booster control chamber.
  • a hydraulic connection leads to a pressure shoulder formed on the nozzle needle, which points the nozzle needle in the direction of the nozzle spring chamber in the opening direction.
  • a hydraulic filling path with a check valve leads from Nozzle spring chamber in the pressure booster pressure chamber.
  • One of the nozzle needle associated damping piston is exposed to a damping chamber which is hydraulically connected via a guided through the damping piston damping and filling path with the nozzle spring chamber, by actuation of the metering valve means the pressure intensifier control chamber is relieved in a low pressure / return system, so that on an opposite surface of the Pressure intensifier piston attacking system pressure pushes the pressure intensifier piston with its smaller area in the pressure booster pressure chamber.
  • EP 1598 551 A2 known fuel injector performs a connected to the pressure booster control chamber control line directly into a damping chamber, from which a hydraulic connection with a nozzle control chamber is realized via a damping path.
  • a device for injecting fuel into a combustion chamber of an internal combustion engine with a fuel injector known which can be acted upon by a high-pressure source with high-pressure fuel and actuated via a metering valve.
  • An injection valve member which is acted upon in the closing direction by a closing force, is enclosed by a pressure chamber.
  • the injection valve member is associated with a independently movable damping element which defines a damping chamber and at least one overflow channel for connecting the damping chamber with another hydraulic. Has room.
  • the damping element may be formed as a damping piston, which is surrounded by the other hydraulic space.
  • the damping chamber which may be bounded by a separate damping piston or the injection valve member, and the damping path with the damping throttle are also referred to as damping module.
  • damping module In the context of the present invention, it has been found that during operation of the fuel injector, the temperature in the damping module increases.
  • the temperature increase in the damping module can be attributed to the compression of the fuel volume enclosed in the damping chamber and the expansion losses in the damping throttle.
  • the increased temperature in the damping module can lead to variable damping properties and to unstable injector behavior.
  • Object of the present invention is to make arrangements so that the heated fuel for the reasons mentioned does not remain in the damping module.
  • the damping room which may be limited by a separate damping piston or the injection valve member, and the damping path with the damping throttle are also referred to as damping module.
  • damping module In the context of the present invention, it has been found that during operation of the fuel injector, the temperature in the damping module increases. The temperature increase in the damping module can be attributed to the compression of the fuel volume enclosed in the damping chamber and the expansion losses in the damping throttle. The increased temperature in the damping module can lead to variable damping properties and to unstable injector behavior.
  • the inventive connection of the damping path to the filling path is achieved that the displaced from the damping chamber, heated fuel passes in the next filling of the pressure booster pressure chamber via the filling path in the pressure booster pressure chamber and is injected in sequence. The heated fuel thus does not remain in the damping module.
  • conduit is used synonymously with the term flow connection means. That is, a line according to the invention may also be a bore or a channel.
  • the damping path is significantly shorter than the filling path, in particular as the filling path section.
  • a preferred embodiment of the fuel injection device is characterized in that the damping chamber is delimited by a damping piston having a Dämpfungsraum spallpfad over which the damping chamber is filled.
  • the damping chamber fill path independent of the damping path ensures that the damping chamber is filled with new, cold fuel. This ensures a good flushing of the damping chamber.
  • Further preferred embodiments of the fuel injection device are characterized in that the metering valve device and / or the injection valve member and / or the pressure intensifier piston is / are integrated in the fuel injector. This creates a compact, multifunctional injector.
  • FIG. 1 is a longitudinal section through a common rail injector 1 shown, which is supplied via an only schematically indicated high-pressure accumulator chamber 2 with high pressure fuel.
  • the high-pressure storage space 2 is also referred to as a common rail or as a high-pressure fuel source.
  • a fuel supply line 3 extends to a pressure booster 5, which is also referred to as a pressure booster and is integrated into the fuel injector 1.
  • the pressure booster 5 is enclosed by an injector 6, which in the FIGS. 1 and 2 is indicated only schematically.
  • the injector housing 6 comprises an injector body 7, from which in the FIGS. 1 and only the interior is shown, and a nozzle body 8 having a central guide bore 9.
  • an injection valve member 10 is guided reciprocally movable, which is also referred to as a nozzle needle.
  • the nozzle needle 10 has a tip 11, on which a sealing surface is formed, which cooperates with a sealing seat, which is formed at the projecting into the combustion chamber end of the nozzle body 8.
  • a sealing seat which is formed at the projecting into the combustion chamber end of the nozzle body 8.
  • a metering valve device 12 which in turn is controlled by a solenoid valve.
  • the metering valve device 12 is a 3/2-way valve, which is integrated in the fuel injector 1.
  • a pressure shoulder 14 is formed, which is arranged in the nozzle body 8 in a pressure chamber 15, which is also referred to as Einspritzventilglieddruckraum.
  • the nozzle needle 10 is biased by a nozzle spring 16 with its tip 11 against the associated nozzle needle seat.
  • the nozzle spring 16 is received in a nozzle spring chamber 17 which is recessed in the injector body 7.
  • the pressure chamber 15 is connected via a connecting channel 18 with a pressure booster pressure chamber 22 in connection.
  • the pressure booster pressure chamber 22 is formed by a portion of a central bore in the injector body 7, which is formed as a blind bore toward the combustion chamber. At its combustion chamber remote end, the bore expands to form a pressure booster control chamber 23. In the blind bore, an end 24 of a pressure booster piston 25 is received reciprocally movable.
  • the end 24 of the pressure booster piston 25 has the shape of a circular cylinder, which has a smaller diameter than a subsequent collar 21 of the pressure booster piston 25. From the combustion chamber distant end face of the collar 21 protrudes a punch 20, at the end of a spring plate 19 is formed in a pressure booster working space 26, which is connected via the fuel supply line 3 with the high-pressure fuel source 2 in conjunction.
  • the pressure intensifier pressure chamber 22 is limited by the combustion chamber near the end of the circular cylinder 24 of the booster piston 25.
  • the pressure intensifier control chamber 23 has the shape of an annular space which extends around the circular cylinder 24 in the injector body 7 and is limited by the combustion chamber near end face of the collar 21 of the pressure intensifier piston 25.
  • the combustion chamber-remote end face of the collar 21 of the pressure booster piston 25 limits the pressure booster working space 26.
  • a nozzle spring 27 is clamped by the combustion chamber distal end of the pressure booster piston 25 is biased against the injector.
  • the pressure booster control chamber 23 communicates with the nozzle spring chamber 17 via a control line 28, in which a throttle 29 is provided.
  • the pressure booster control chamber 23 is connected via a connecting line 30 and the metering valve 12 and the supply line 3 to the high-pressure accumulator 2 in connection.
  • the pressure booster piston 25 is pressure balanced and the injector 1 is in the idle state.
  • the connecting line 30 When the metering valve 12 is brought to its second position, the connecting line 30 is brought into communication with a return line 31, which communicates with a low pressure area.
  • a connecting line 32 From the control line 28 is a connecting line 32, in which a check valve 34 is disposed, and in the connecting channel 18 opens, which is in communication with the pressure booster pressure chamber 22.
  • the pressure booster pressure chamber 22 Via the connecting line 32 and the check valve 34, the pressure booster pressure chamber 22 is filled with fuel from the high-pressure reservoir 2.
  • the check valve 34 prevents a backflow of fuel from the pressure booster pressure chamber 22nd
  • a connecting line with a throttle 36 leads into an injection valve member control chamber 38 which is delimited in the nozzle body 8 by the combustion chamber distal end 41 of a damper piston 42.
  • the combustion chamber near end 43 of the damper piston 42 is formed spherical and is located at the combustion chamber remote end of the nozzle needle 10 at.
  • a central through-bore 45 with a throttle in the damper piston 42 is closed.
  • the damper piston 42 is pressed by the nozzle spring 16 with its combustion chamber near end 43 against the combustion chamber distal end of the nozzle needle 10.
  • a damping path in which the throttle 36 is arranged designated 46.
  • the damping path 46 opens into the connecting line 32 which extends between the check valve 34 and the control line 28.
  • a filling path for the pressure booster pressure chamber 22 is in FIG. 1 denoted by 47.
  • FIG. 1 shown fuel injector 1 is controlled via the 3/2-way valve 12.
  • the pressure booster control chamber 23 is acted upon via the connecting line 30 and the metering valve 12 with the same system pressure as the pressure booster working chamber 26.
  • the connection to the return 31 is closed.
  • the intensifier piston unit 25 is pressure compensated and there is no pressure boosting.
  • the nozzle needle 10 is closed.
  • the pressure booster control chamber 23 is depressurized.
  • the pressure booster control chamber 23 is decoupled from the pressure source 2 and relieved of pressure via the connecting line 30 in the return 31.
  • the pressure in the pressure booster pressure chamber 22 is thereby increased according to the transmission ratio of the pressure booster 25 and forwarded via the connecting line 18 into the pressure chamber 15 at the nozzle needle 10.
  • the nozzle needle 10 begins to open, taking fuel must be displaced from the damping chamber 38 via the throttle 36. This reduces the needle opening speed.
  • the fuel which is heated in the damping path 46 during the expansion via the throttle 36 is conducted into the filling path 47 in front of the check valve 34.
  • the pressure booster control chamber 23, which is also referred to as the back space of the pressure booster piston 25, is depressurized, the pressure booster 25 remains activated and compresses the fuel in the pressure booster pressure chamber 22.
  • the compressed fuel is forwarded to the nozzle needle 10 and injected.
  • the injection is separated by the control valve 12, which is also referred to as a metering valve, the rear space 23 from the return line 31 and acted upon by the supply pressure of the high-pressure fuel source 2.
  • the control valve 12 which is also referred to as a metering valve
  • 23 rail pressure builds up in the connecting line 30 and the rear space.
  • the pressure in the pressure booster pressure chamber 22 and the pressure chamber 15 drops to rail pressure.
  • the nozzle needle 10 closes. In this case, the nozzle needle 10 separates from the damping piston 42 and performs a fast closing movement.
  • the damping piston 42 is then reset by the nozzle spring 16.
  • the damping chamber 38 is filled via the central through-bore 45, which is also referred to as Dämpfungsraum spallpfad, and the open sealing seat between the damping piston 42 and the nozzle needle 10.
  • the Dämpfungsraum spallpfad 45 is so to the control line 28 that it is filled with new, cold fuel. This results in a forced flushing of the damping chamber 38th
  • the pressure booster piston 25 is returned by the pressure booster spring 27 in its initial position, wherein the pressure booster pressure chamber 22 is filled via the filling path 47 with the check valve 34.
  • This filling flow is designed so that thereby the heated amount from the damping chamber 38 and the damping path 46 is conveyed into the pressure booster pressure chamber and injected in sequence.

Description

Die Erfindung betrifft eine Einrichtung zum Einspritzen von Kraftstoff in einen Brennraum einer Brennkraftmaschine mit einem Kraftstoffinjektor, nach den Merkmalen des Oberbegriffs des Anspruchs 1.The invention relates to a device for injecting fuel into a combustion chamber of an internal combustion engine with a fuel injector, according to the features of the preamble of claim 1.

Stand der TechnikState of the art

Eine Kraftstoffeinspritzeinrichtung mit einem Kraftstoffinjektor mit den Merkmalen des Oberbegriffs geht aus WO 2004/088122 A1 und WO 2004/003377 A1 hervor. Der Kraftstoffinjektor weist dabei ein Einspritzventilglied mit einer Düsennadel, einen Druckverstärker mit einem Druckverstärkerkolben und eine Zumessventileinrichtung auf, wobei der Druckverstärker mittels der Zumessventileinrichtung angesteuert wird. Der Druckverstärkerkolben ist einem Druckverstärkerarbeitsraum, einem Druckverstärkersteuerraum und einem Druckverstärkerdruckraum ausgesetzt. Das Einspritzventilgliede ist mittels einer rückwärtigen Druckfläche einem Düsenfederraum ausgesetzt, der über eine Steuerleitung, die eine Drossel einschließt, mit dem Druckverstärkersteuerraum in Verbindung steht. Vom Druckverstärkerdruckraum führt eine hydraulische Verbindung zu einer an der Düsennadel ausgebildeten Druckschulter, die die Düsennadel in Richtung des Düsenfederraums in Öffnungsrichtung weist. Ein hydraulischer Füllpfad mit einem Rückschlagventil führt vom Düsenfederraum in den Druckverstärkerdruckraum. Ein der Düsenadel zugeordneter Dämpfungskolben ist einem Dämpfungsraum ausgesetzt, der über einen durch den Dämpfungskolben geführten Dämpfungs- und Füllpfad mit dem Düsenfederraum hydraulisch verbunden ist, Durch Betätigung der Zumessventileinrichtung wird der Druckverstärkersteuerraum in ein Niederdruck/Rücklaufsystem entlastet, so dass der an einer gegenüberliegenden Fläche des Druckverstärkerkolbens angreifende Systemdruck den Druckverstärkerkolben mit seiner kleineren Fläche in den Druckverstärkerdruckraum drückt. Dadurch wird der Druck in diesem Raum erhöht, der sich über die hydraulische Verbindung in den Düsennadeldruckraum fortsetzt und durch den erhöhten Druck die Düsennadel vom Düsennadelsitz abhebt. Die Öffnungsbewegung der Düsennadel wird durch den dem Dämpfungsraum ausgesetzten Dämpfungskolben gedämpft.A fuel injection device with a fuel injector with the features of the preamble is made WO 2004/088122 A1 and WO 2004/003377 A1 out. The fuel injector in this case has an injection valve member with a nozzle needle, a pressure booster with a pressure booster piston and a metering valve device, wherein the pressure booster is controlled by means of the metering valve device. The pressure intensifier piston is exposed to a pressure booster working space, a pressure booster control chamber and a pressure booster pressure space. The injection valve member is exposed by means of a rear pressure surface of a nozzle spring chamber, which communicates via a control line, which includes a throttle, with the pressure booster control chamber. From the pressure booster pressure chamber, a hydraulic connection leads to a pressure shoulder formed on the nozzle needle, which points the nozzle needle in the direction of the nozzle spring chamber in the opening direction. A hydraulic filling path with a check valve leads from Nozzle spring chamber in the pressure booster pressure chamber. One of the nozzle needle associated damping piston is exposed to a damping chamber which is hydraulically connected via a guided through the damping piston damping and filling path with the nozzle spring chamber, by actuation of the metering valve means the pressure intensifier control chamber is relieved in a low pressure / return system, so that on an opposite surface of the Pressure intensifier piston attacking system pressure pushes the pressure intensifier piston with its smaller area in the pressure booster pressure chamber. As a result, the pressure in this space is increased, which continues via the hydraulic connection in the nozzle needle pressure chamber and lifted by the increased pressure, the nozzle needle from the nozzle needle seat. The opening movement of the nozzle needle is damped by the damping piston exposed to the damping chamber.

Bei der aus dem nachveröffentlichten Dokument EP 1598 551 A2 bekannten Kraftstoffeinspritzeinrichtung führt eine mit dem Druckverstärkersteuerraum verbundene Steuerleitung direkt in einen Dämpfungsraum, von dem aus über einen Dämpfungspfad eine hydraulische Verbindung mit einem Düsensteuerraum realisiert ist.At the post-published document EP 1598 551 A2 known fuel injector performs a connected to the pressure booster control chamber control line directly into a damping chamber, from which a hydraulic connection with a nozzle control chamber is realized via a damping path.

Aus der deutschen Offenlegungsschrift DE 102 29 415 A1 ist weiterhin eine Einrichtung zum Einspritzen von Kraftstoff in einen Brennraum einer Verbrennungskraftmaschine, mit einem Kraftstoffinjektor bekannt, der über eine Hochdruckquelle mit unter hohem Druck stehenden Kraftstoff beaufschlagbar und über ein Zumessventil betätigbar ist. Ein Einspritzventilglied, das in Schließrichtung durch eine Schließkraft beaufschlagt ist, ist von einem Druckraum umschlossen. Um die Öffnungsgeschwindigkeit des Einspritzventilglieds, zum Beispiel einer Düsennadel, zu dämpfen, ohne dass ein schnelles Schließen des Einspritzventilglieds beeinträchtigt würde, ist dem Einspritzventilglied ein von diesem unabhängig bewegbares Dämpfungselement zugeordnet, das einen Dämpfungsraum begrenzt und mindestens einen Überströmkanal zur Verbindung des Dämpfungsraums mit einem weiteren hydraulischen. Raum aufweist. Das Dämpfungselement kann als Dämpfungskolben ausgebildet sein, der von dem weiteren hydraulischen Raum umgeben ist.From the German Offenlegungsschrift DE 102 29 415 A1 Furthermore, a device for injecting fuel into a combustion chamber of an internal combustion engine, with a fuel injector known which can be acted upon by a high-pressure source with high-pressure fuel and actuated via a metering valve. An injection valve member, which is acted upon in the closing direction by a closing force, is enclosed by a pressure chamber. In order to dampen the opening speed of the injection valve member, for example a nozzle needle, without a rapid closing of the injection valve member would be impaired, the injection valve member is associated with a independently movable damping element which defines a damping chamber and at least one overflow channel for connecting the damping chamber with another hydraulic. Has room. The damping element may be formed as a damping piston, which is surrounded by the other hydraulic space.

Der Dämpfungsraum, der von einem separaten Dämpfungskolben oder dem Einspritzventilglied begrenzt sein kann, und der Dämpfungspfad mit der Dämpfungsdrossel werden auch als Dämpfungsmodul bezeichnet. Im Rahmen der vorliegenden Erfindung wurde herausgefunden, dass im Betrieb der Kraftstoffeinspritzeinrichtung die Temperatur in dem Dämpfungsmodul ansteigt. Der Temperaturanstieg im Dämpfungsmodul kann auf die Komprimierung des in dem Dämpfungsraum eingeschlossenen Kraftstoffvolumens und die Entspannungsverluste in der Dämpfungsdrossel zurückgeführt werden. Die erhöhte Temperatur im Dämpfungsmodul kann zu variablen Dämpfungseigenschaften und zu einem instabilen Injektorverhalten führen.The damping chamber, which may be bounded by a separate damping piston or the injection valve member, and the damping path with the damping throttle are also referred to as damping module. In the context of the present invention, it has been found that during operation of the fuel injector, the temperature in the damping module increases. The temperature increase in the damping module can be attributed to the compression of the fuel volume enclosed in the damping chamber and the expansion losses in the damping throttle. The increased temperature in the damping module can lead to variable damping properties and to unstable injector behavior.

Aufgabe der vorliegenden Erfindung ist es, Vorkehrungen zu treffen, damit der aus den genannten Gründen erwärmte Kraftstoff nicht im Dämpfungsmodul verbleibt.Object of the present invention is to make arrangements so that the heated fuel for the reasons mentioned does not remain in the damping module.

Darstellung der ErfindungPresentation of the invention

Die Aufgabe der Erfindung wird mit den kennzeichnenden Merkmalen des Anspruchs 1 gelöst.The object of the invention is achieved with the characterizing features of claim 1.

Der Dämpfungsraum, der von einem separaten Dämpfungskolben oder dem Einspritzventilglied begrenzt sein kann, und der Dämpfungspfad mit der Dämpfungsdrossel werden auch als Dämpfungsmodul bezeichnet. Im Rahmen der vorliegenden Erfindung wurde herausgefunden, dass im Betrieb der Kraftstoffeinspritzeinrichtung die Temperatur in dem Dämpfungsmodul ansteigt. Der Temperaturanstieg im Dämpfungsmodul kann auf die Komprimierung des in dem Dämpfungsraum eingeschlossenen Kraftstoffvolumens und die Entspannungsverluste in der Dämpfungsdrossel zurückgeführt werden. Die erhöhte Temperatur im Dämpfungsmodul kann zu variablen Dämpfungseigenschaften und zu einem instabilen Injektorverhalten führen. Durch die erfindungsgemäße Anbindung des Dämpfungspfads an den Füllpfad wird erreicht, dass der aus dem Dämpfungsraum verdrängte, erwärmte Kraftstoff bei der nächsten Befüllung des Druckverstärkerdruckraums über den Füllpfad in den Druckverstärkerdruckraum gelangt und in Folge eingespritzt wird. Der erwärmte Kraftstoff verbleibt also nicht in dem Dämpfungsmodul. Im Rahmen der vorliegenden Erfindung wird der Begriff Leitung gleichbedeutend mit dem Begriff Strömungsverbindungsmittel verwendet. Das heißt, bei einer Leitung im Sinne der Erfindung kann es sich auch um eine Bohrung oder einen Kanal handeln.The damping room, which may be limited by a separate damping piston or the injection valve member, and the damping path with the damping throttle are also referred to as damping module. In the context of the present invention, it has been found that during operation of the fuel injector, the temperature in the damping module increases. The temperature increase in the damping module can be attributed to the compression of the fuel volume enclosed in the damping chamber and the expansion losses in the damping throttle. The increased temperature in the damping module can lead to variable damping properties and to unstable injector behavior. By the inventive connection of the damping path to the filling path is achieved that the displaced from the damping chamber, heated fuel passes in the next filling of the pressure booster pressure chamber via the filling path in the pressure booster pressure chamber and is injected in sequence. The heated fuel thus does not remain in the damping module. In the context of the present invention, the term conduit is used synonymously with the term flow connection means. That is, a line according to the invention may also be a bore or a channel.

Über die Steuerleitung und den Füllpfadabschnitt gelangt, in Abhängigkeit von der Schaltstellung der Zumessventileinrichtung, mit Hochdruck beaufschlagter Kraftstoff in den Druckverstärkerdruckraum.Via the control line and the filling path section passes, in response to the switching position of the metering valve, high-pressure fuel in the pressure booster pressure chamber.

Vorzugsweise ist der Dämpfungspfad deutlich kürzer als der Füllpfad, insbesondere als der Füllpfadabschnitt.Preferably, the damping path is significantly shorter than the filling path, in particular as the filling path section.

Ein bevorzugtes Ausführungsbeispiel der Kraftstoffeinspritzeinrichtung ist dadurch gekennzeichnet, dass der Dämpfungsraum von einem Dämpfungskolben begrenzt wird, der einen Dämpfungsraumfüllpfad aufweist, über den der Dämpfungsraum befüllt wird. Der von dem Dämpfungspfad unabhängige Dämpfungsraumfüllpfad gewährleistet, dass der Dämpfungsraum mit neuem, kaltem Kraftstoff befüllt wird. Dadurch wird eine gute Durchspülung des Dämpfungsraums gewährleistet.A preferred embodiment of the fuel injection device is characterized in that the damping chamber is delimited by a damping piston having a Dämpfungsraumfüllpfad over which the damping chamber is filled. The damping chamber fill path independent of the damping path ensures that the damping chamber is filled with new, cold fuel. This ensures a good flushing of the damping chamber.

Weitere bevorzugte Ausführungsbeispiele der Kraftstoffeinspritzeinrichtung sind dadurch gekennzeichnet, dass die Zumessventileinrichtung und/oder das Einspritzventilglied und/oder der Druckverstärkerkolben in den Kraftstoffinjektor integriert sind/ist. Dadurch wird ein kompakter, multifunktioneller Injektor geschaffen.Further preferred embodiments of the fuel injection device are characterized in that the metering valve device and / or the injection valve member and / or the pressure intensifier piston is / are integrated in the fuel injector. This creates a compact, multifunctional injector.

Weitere Vorteile, Merkmale und Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung, in der unter Bezugnahme auf die Zeichnung verschiedene Ausführungsbeispiele im Einzelnen beschrieben sind. Dabei können die in den Ansprüchen und in der Beschreibung erwähnten Merkmale jeweils einzeln für sich oder in beliebiger Kombination erfindungswesentlich sein.Further advantages, features and details of the invention will become apparent from the following description in which, with reference to the drawings, various embodiments are described in detail. The features mentioned in the claims and in the description may each be essential to the invention individually or in any desired combination.

Zeichnungdrawing

Es zeigen:

Figur 1
eine schematische Darstellung einer erfindungsgemäßen Kraftstoffeinspritzeinrichtung im Längsschnitt durch einen Injektor.
Show it:
FIG. 1
a schematic representation of a fuel injection device according to the invention in longitudinal section through an injector.

Beschreibung der AusführungsbeispieleDescription of the embodiments

In Figur 1 ist ein Längsschnitt durch einen Common-Rail-Injektor 1 dargestellt, der über einen nur schematisch angedeuteten Hochdruckspeicherraum 2 mit unter hohem Druck stehenden Kraftstoff versorgt wird. Der Hochdruckspeicherraum 2 wird auch als Common-Rail oder als Kraftstoffhochdruckquelle bezeichnet. Vom Innenraum des Hochdruckspeicherraums 2 erstreckt sich eine Kraftstoffzuleitung 3 zu einem Druckübersetzer 5, der auch als Druckverstärker bezeichnet wird und in den Kraftstoffinjektor 1 integriert ist. Der Druckübersetzer 5 ist von einem Injektorgehäuse 6 umschlossen, das in den Figuren 1 und 2 nur schematisch angedeutet ist.In FIG. 1 is a longitudinal section through a common rail injector 1 shown, which is supplied via an only schematically indicated high-pressure accumulator chamber 2 with high pressure fuel. The high-pressure storage space 2 is also referred to as a common rail or as a high-pressure fuel source. From the interior of the high pressure accumulator 2, a fuel supply line 3 extends to a pressure booster 5, which is also referred to as a pressure booster and is integrated into the fuel injector 1. The pressure booster 5 is enclosed by an injector 6, which in the FIGS. 1 and 2 is indicated only schematically.

Das Injektorgehäuse 6 umfasst einen Injektorkörper 7, von dem in den Figuren 1 und 2 nur der Innenraum gezeigt ist, und einen Düsenkörper 8, der eine zentrale Führungsbohrung 9 aufweist. In der Führungsbohrung 9 ist ein Einspritzventilglied 10 hin und her bewegbar geführt, das auch als Düsennadel bezeichnet wird. Die Düsennadel 10 weist eine Spitze 11 auf, an der eine Dichtfläche ausgebildet ist, die mit einem Dichtsitz zusammenwirkt, der an dem in den Brennraum ragenden Ende des Düsenkörpers 8 ausgebildet ist. Wenn sich die Spitze 11 der Düsennadel 10 mit ihrer Dichtfläche in Anlage an dem Dichtsitz befindet, sind mindestens ein Spritzloch, insbesondere mehrere Spritzlöcher, in dem Düsenkörper 8 verschlossen.The injector housing 6 comprises an injector body 7, from which in the FIGS. 1 and only the interior is shown, and a nozzle body 8 having a central guide bore 9. In the guide bore 9, an injection valve member 10 is guided reciprocally movable, which is also referred to as a nozzle needle. The nozzle needle 10 has a tip 11, on which a sealing surface is formed, which cooperates with a sealing seat, which is formed at the projecting into the combustion chamber end of the nozzle body 8. When the tip 11 of the nozzle needle 10 with its sealing surface is in contact with the sealing seat, at least one spray hole, in particular a plurality of injection holes, is closed in the nozzle body 8.

Wenn die Düsennadelspitze 11 von ihrem Sitz abhebt, dann wird mit Hochdruck beaufschlagter Kraftstoff durch die Spritzlöcher in den Brennraum der Brennkraftmaschine eingespritzt. Die Öffnungsbewegung der Düsennadel 10 wird über eine Zumessventileinrichtung 12 gesteuert, die wiederum über ein Magnetventil angesteuert wird. Bei der Zumessventileinrichtung 12 handelt es sich um ein 3/2-Wegeventil, das in den Kraftstoffinjektor 1 integriert ist.When the nozzle needle tip 11 lifts from its seat, then high-pressure fuel is injected through the injection holes in the combustion chamber of the internal combustion engine. The opening movement of the nozzle needle 10 is controlled via a metering valve device 12, which in turn is controlled by a solenoid valve. The metering valve device 12 is a 3/2-way valve, which is integrated in the fuel injector 1.

An der Düsennadel 10 ist eine Druckschulter 14 ausgebildet, die in einem Druckraum 15, der auch als Einspritzventilglieddruckraum bezeichnet wird, in dem Düsenkörper 8 angeordnet ist. Die Düsennadel 10 ist durch eine Düsenfeder 16 mit ihrer Spitze 11 gegen den zugehörigen Düsennadelsitz vorgespannt. Die Düsenfeder 16 ist in einen Düsenfederraum 17 aufgenommen, der in dem Injektorkörper 7 ausgespart ist. Der Druckraum 15 steht über einen Verbindungskanal 18 mit einem Druckverstärkerdruckraum 22 in Verbindung.On the nozzle needle 10, a pressure shoulder 14 is formed, which is arranged in the nozzle body 8 in a pressure chamber 15, which is also referred to as Einspritzventilglieddruckraum. The nozzle needle 10 is biased by a nozzle spring 16 with its tip 11 against the associated nozzle needle seat. The nozzle spring 16 is received in a nozzle spring chamber 17 which is recessed in the injector body 7. The pressure chamber 15 is connected via a connecting channel 18 with a pressure booster pressure chamber 22 in connection.

Der Druckverstärkerdruckraum 22 wird von einem Abschnitt einer zentralen Bohrung in dem Injektorkörper 7 gebildet, die zum Brennraum hin als Sackbohrung ausgebildet ist. An ihrem brennraumfernen Ende erweitert sich die Bohrung, um einen Druckverstärkersteuerraum 23 auszubilden. In der Sackbohrung ist ein Ende 24 eines Druckverstärkerkolbens 25 hin und her bewegbar aufgenommen. Das Ende 24 des Druckverstärkerkolbens 25 hat die Gestalt eines Kreiszylinders, der einen kleineren Durchmesser aufweist als ein anschließender Bund 21 des Druckverstärkerkolbens 25. Von der brennraumfernen Stirnseite des Bundes 21 ragt ein Stempel 20, an dessen Ende ein Federteller 19 ausgebildet ist, in einen Druckverstärkerarbeitsraum 26, der über die Kraftstoffzuleitung 3 mit der Kraftstoffhochdruckquelle 2 in Verbindung steht.The pressure booster pressure chamber 22 is formed by a portion of a central bore in the injector body 7, which is formed as a blind bore toward the combustion chamber. At its combustion chamber remote end, the bore expands to form a pressure booster control chamber 23. In the blind bore, an end 24 of a pressure booster piston 25 is received reciprocally movable. The end 24 of the pressure booster piston 25 has the shape of a circular cylinder, which has a smaller diameter than a subsequent collar 21 of the pressure booster piston 25. From the combustion chamber distant end face of the collar 21 protrudes a punch 20, at the end of a spring plate 19 is formed in a pressure booster working space 26, which is connected via the fuel supply line 3 with the high-pressure fuel source 2 in conjunction.

Der Druckerstärkerdruckraum 22 wird durch das brennraumnahe Ende des Kreiszylinders 24 des Druckerverstärkerkolbens 25 begrenzt. Der Druckverstärkersteuerraum 23 hat die Gestalt eines Ringraums, der sich um den Kreiszylinder 24 in dem Injektorkörper 7 erstreckt und durch die brennraumnahe Stirnfläche des Bundes 21 des Druckverstärkerkolbens 25 begrenzt wird. Die brennraumferne Stirnfläche des Bundes 21 des Druckverstärkerkolbens 25 begrenzt den Druckverstärkerarbeitsraum 26. Zwischen dem Federteller 19 und einem injektorgehäusefesten Anschlag 33 ist eine Düsenfeder 27 eingespannt, durch die das brennraumferne Ende des Druckverstärkerkolbens 25 gegen das Injektorgehäuse vorgespannt ist.The pressure intensifier pressure chamber 22 is limited by the combustion chamber near the end of the circular cylinder 24 of the booster piston 25. The pressure intensifier control chamber 23 has the shape of an annular space which extends around the circular cylinder 24 in the injector body 7 and is limited by the combustion chamber near end face of the collar 21 of the pressure intensifier piston 25. The combustion chamber-remote end face of the collar 21 of the pressure booster piston 25 limits the pressure booster working space 26. Between the spring plate 19 and an injector housing fixed stop 33, a nozzle spring 27 is clamped by the combustion chamber distal end of the pressure booster piston 25 is biased against the injector.

Der Druckverstärkersteuerraum 23 steht über eine Steuerleitung 28, in der eine Drossel 29 vorgesehen ist, mit dem Düsenfederraum 17 in Verbindung. Außerdem steht der Druckverstärkersteuerraum 23 über eine Verbindungsleitung 30 und das Zumessventil 12 sowie die Zuleitung 3 mit dem Hochdruckspeicherraum 2 in Verbindung. In der in Figur 1 dargestellten Stellung des Zumessventils 12 ist der Druckverstärkerkolben 25 druckausgeglichen und der Injektor 1 befindet sich im Ruhezustand.The pressure booster control chamber 23 communicates with the nozzle spring chamber 17 via a control line 28, in which a throttle 29 is provided. In addition, the pressure booster control chamber 23 is connected via a connecting line 30 and the metering valve 12 and the supply line 3 to the high-pressure accumulator 2 in connection. In the in FIG. 1 illustrated position of the metering valve 12, the pressure booster piston 25 is pressure balanced and the injector 1 is in the idle state.

Wenn das Zumessventil 12 in seine zweite Stellung gebracht wird, dann wird die Verbindungsleitung 30 mit einer Rücklaufleitung 31 in Verbindung gebracht, die mit einem Niederdruckbereich in Verbindung steht. Von der Steuerleitung 28 geht eine Verbindungsleitung 32 aus, in der ein Rückschlagventil 34 angeordnet ist, und die in den Verbindungskanal 18 mündet, der mit dem Druckverstärkerdruckraum 22 in Verbindung steht. Über die Verbindungsleitung 32 und das Rückschlagventil 34 wird der Druckverstärkerdruckraum 22 mit Kraftstoff aus dem Hochdruckspeicherraum 2 befüllt. Das Rückschlagventil 34 verhindert ein Rückströmen von Kraftstoff aus dem Druckverstärkerdruckraum 22.When the metering valve 12 is brought to its second position, the connecting line 30 is brought into communication with a return line 31, which communicates with a low pressure area. From the control line 28 is a connecting line 32, in which a check valve 34 is disposed, and in the connecting channel 18 opens, which is in communication with the pressure booster pressure chamber 22. Via the connecting line 32 and the check valve 34, the pressure booster pressure chamber 22 is filled with fuel from the high-pressure reservoir 2. The check valve 34 prevents a backflow of fuel from the pressure booster pressure chamber 22nd

Von der Verbindungsleitung 32 führt eine Verbindungsleitung mit einer Drossel 36 in einen Einspritzventilgliedsteuerraum 38, der in dem Düsenkörper 8 durch das brennraumferne Ende 41 eines Dämpferkolbens 42 begrenzt wird. Das brennraumnahe Ende 43 des Dämpferkolbens 42 ist ballig ausgebildet und liegt an dem brennraumfernen Ende der Düsennadel 10 an. In dem dargestellten Zustand ist eine zentrale Durchgangsbohrung 45 mit einer Drossel in dem Dämpferkolben 42 verschlossen. Der Dämpferkolben 42 wird durch die Düsenfeder 16 mit seinem brennraumnahen Ende 43 gegen das brennraumferne Ende der Düsennadel 10 gedrückt.From the connecting line 32, a connecting line with a throttle 36 leads into an injection valve member control chamber 38 which is delimited in the nozzle body 8 by the combustion chamber distal end 41 of a damper piston 42. The combustion chamber near end 43 of the damper piston 42 is formed spherical and is located at the combustion chamber remote end of the nozzle needle 10 at. In the illustrated state, a central through-bore 45 with a throttle in the damper piston 42 is closed. The damper piston 42 is pressed by the nozzle spring 16 with its combustion chamber near end 43 against the combustion chamber distal end of the nozzle needle 10.

Bei dem in Figur 1 dargestellten Ausführungsbeispiel ist ein Dämpfungspfad, in dem die Drossel 36 angeordnet ist, mit 46 bezeichnet. Der Dämpfungspfad 46 mündet in die Verbindungsleitung 32, die zwischen dem Rückschlagventil 34 und der Steuerleitung 28 verläuft. Ein Füllpfad für den Druckverstärkerdruckraum 22 ist in Figur 1 mit 47 bezeichnet.At the in FIG. 1 illustrated embodiment, a damping path in which the throttle 36 is arranged, designated 46. The damping path 46 opens into the connecting line 32 which extends between the check valve 34 and the control line 28. A filling path for the pressure booster pressure chamber 22 is in FIG. 1 denoted by 47.

Der in Figur 1 dargestellte Kraftstoffinjektor 1 wird über das 3/2-Wegeventil 12 gesteuert. Im deaktivierten Ruhezustand des Injektors 1 ist der Druckverstärkersteuerraum 23 über die Verbindungsleitung 30 und das Zumessventil 12 mit demselben Systemdruck wie der Druckverstärkerarbeitsraum 26 beaufschlagt. Die Verbindung zum Rücklauf 31 ist geschlossen. Die Druckverstärkerkolbeneinheit 25 ist druckausgeglichen und es findet keine Druckverstärkung statt. Die Düsennadel 10 ist geschlossen.The in FIG. 1 shown fuel injector 1 is controlled via the 3/2-way valve 12. In the deactivated state of rest of the injector 1, the pressure booster control chamber 23 is acted upon via the connecting line 30 and the metering valve 12 with the same system pressure as the pressure booster working chamber 26. The connection to the return 31 is closed. The intensifier piston unit 25 is pressure compensated and there is no pressure boosting. The nozzle needle 10 is closed.

Zur Aktivierung des Injektors 1 wird der Druckverstärkersteuerraum 23 druckentlastet. Dazu wird der Druckverstärkersteuerraum 23 von der Druckquelle 2 abgekoppelt und über die Verbindungsleitung 30 in den Rücklauf 31 druckentlastet. Der Druck in dem Druckverstärkerdruckraum 22 wird dabei entsprechend dem Übersetzungsverhältnis des Druckverstärkers 25 erhöht und über die Verbindungsleitung 18 in den Druckraum 15 an der Düsennadel 10 weitergeleitet. Die Düsennadel 10 beginnt zu öffnen, wobei Kraftstoff aus dem Dämpfungsraum 38 über die Drossel 36 verdrängt werden muss. Dadurch wird die Nadelöffnungsgeschwindigkeit verringert. Der sich bei der Entspannung über die Drossel 36 in den Dämpfungspfad 46 erwärmende Kraftstoff wird in den Füllpfad 47 vor das Rückschlagventil 34 geführt.To activate the injector 1, the pressure booster control chamber 23 is depressurized. For this purpose, the pressure booster control chamber 23 is decoupled from the pressure source 2 and relieved of pressure via the connecting line 30 in the return 31. The pressure in the pressure booster pressure chamber 22 is thereby increased according to the transmission ratio of the pressure booster 25 and forwarded via the connecting line 18 into the pressure chamber 15 at the nozzle needle 10. The nozzle needle 10 begins to open, taking fuel must be displaced from the damping chamber 38 via the throttle 36. This reduces the needle opening speed. The fuel which is heated in the damping path 46 during the expansion via the throttle 36 is conducted into the filling path 47 in front of the check valve 34.

Solange der Druckverstärkersteuerraum 23, der auch als Rückraum des Druckverstärkerkolbens 25 bezeichnet wird, druckentlastet ist, bleibt der Druckverstärker 25 aktiviert und verdichtet den Kraftstoff in dem Druckverstärkerdruckraum 22. Der verdichtete Kraftstoff wird zur Düsennadel 10 weitergeleitet und eingespritzt.As long as the pressure booster control chamber 23, which is also referred to as the back space of the pressure booster piston 25, is depressurized, the pressure booster 25 remains activated and compresses the fuel in the pressure booster pressure chamber 22. The compressed fuel is forwarded to the nozzle needle 10 and injected.

Zum Beenden der Einspritzung wird durch das Steuerventil 12, das auch als Zumessventil bezeichnet wird, der Rückraum 23 vom Rücklauf 31 getrennt und mit dem Versorgungsdruck der Kraftstoffhochdruckquelle 2 beaufschlagt. Dadurch baut sich in der Verbindungsleitung 30 und dem Rückraum 23 Raildruck auf. Gleichzeitig fällt der Druck in dem Druckverstärkerdruckraum 22 und dem Druckraum 15 auf Raildruck ab. Die Düsennadel 10 schließt. Dabei trennt sich die Düsennadel 10 vom Dämpfungskolben 42 und führt eine schnelle Schließbewegung aus.To end the injection is separated by the control valve 12, which is also referred to as a metering valve, the rear space 23 from the return line 31 and acted upon by the supply pressure of the high-pressure fuel source 2. As a result, 23 rail pressure builds up in the connecting line 30 and the rear space. At the same time, the pressure in the pressure booster pressure chamber 22 and the pressure chamber 15 drops to rail pressure. The nozzle needle 10 closes. In this case, the nozzle needle 10 separates from the damping piston 42 and performs a fast closing movement.

Der Dämpfungskolben 42 wird anschließend durch die Düsenfeder 16 zurückgestellt. Dabei wird der Dämpfungsraum 38 über die zentrale Durchgangsbohrung 45, die auch als Dämpfungsraumfüllpfad bezeichnet wird, und den geöffneten Dichtsitz zwischen dem Dämpfungskolben 42 und der Düsennadel 10 befüllt. Der Dämpfungsraumfüllpfad 45 ist so an die Steuerleitung 28 angebunden, dass die Befüllung mit neuem, kaltem Kraftstoff erfolgt. Dadurch ergibt sich eine erzwungene Durchspülung des Dämpfungsraums 38.The damping piston 42 is then reset by the nozzle spring 16. In this case, the damping chamber 38 is filled via the central through-bore 45, which is also referred to as Dämpfungsraumfüllpfad, and the open sealing seat between the damping piston 42 and the nozzle needle 10. The Dämpfungsraumfüllpfad 45 is so to the control line 28 that it is filled with new, cold fuel. This results in a forced flushing of the damping chamber 38th

Nach dem Druckausgleich des Systems wird der Druckverstärkerkolben 25 durch die Druckverstärkerfeder 27 in seine Ausgangslage zurückgestellt, wobei der Druckverstärkerdruckraum 22 über den Füllpfad 47 mit dem Rückschlagventil 34 befüllt wird. Dieser Füllstrom ist so ausgebildet, dass dadurch die erwärmte Menge aus dem Dämpfungsraum 38 beziehungsweise dem Dämpfungspfad 46 in den Druckverstärkerdruckraum gefördert und in Folge eingespritzt wird.After pressure equalization of the system, the pressure booster piston 25 is returned by the pressure booster spring 27 in its initial position, wherein the pressure booster pressure chamber 22 is filled via the filling path 47 with the check valve 34. This filling flow is designed so that thereby the heated amount from the damping chamber 38 and the damping path 46 is conveyed into the pressure booster pressure chamber and injected in sequence.

Claims (3)

  1. Device for the injection of fuel into a combustion chamber of an internal combustion engine, having a fuel injector (1) which can be loaded with highly pressurized fuel via a high-pressure fuel source (2) and can be actuated via a metering-valve device (12), by which the pressure in a pressure-intensifier control space (23) can be controlled in such a way that the pressure in a pressure-intensifier pressure space (22) which is delimited by a pressure-intensifier piston (25), can be filled with fuel from the high-pressure fuel source (2) via a filling path (47), in which a non-return valve (34) is arranged, and is connected to an injection-valve element pressure space (15) is increased by the pressure-intensifier piston (25) in such a way that an injection-valve element (10) opens for the injection of fuel, the pressure-intensifier control space (23) being connected via a control line (28) which comprises a restrictor (29) and via the metering-valve device (12) to the high-pressure fuel source (2) and to a nozzle-spring space (17), a damping space (38) being provided, from which fuel is displaced via a damping path (46), in which a damping restrictor (36) is arranged, the damping path (46) opening into a filling path (47), and the damping path (46) being attached to the filling path (47), characterized in that the filling path (47) opens into a connecting line (32) which extends between the non-return valve (34) and the control line (28), with the result that the fuel which is displaced from the damping space (38) via the damping restrictor (36) during an injection operation passes via the damping path (46) into the filling path (47) of the pressure-intensifier pressure space (22).
  2. Fuel injection device according to Claim 1, characterized in that the damping space (38) is delimited by a damping piston (42) which has a damping-space filling path (45), via which the damping space (38) is filled.
  3. Fuel injection device according to Claim 1 or 2, characterized in that the metering-valve device (12) and/or the injection-valve element (10) and/or the pressure-intensifier piston (25) are/is integrated into the fuel injector (1).
EP05106765A 2004-11-04 2005-07-22 Fuel injection apparatus Expired - Fee Related EP1657428B1 (en)

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DE102004017305A1 (en) * 2004-04-08 2005-10-27 Robert Bosch Gmbh Fuel injection device for internal combustion engines with directly controllable nozzle needles
US7293547B2 (en) * 2005-10-03 2007-11-13 Caterpillar Inc. Fuel injection system including a flow control valve separate from a fuel injector
DE102006062491A1 (en) * 2006-12-28 2008-07-03 Robert Bosch Gmbh Fuel dosing device for exhaust gas system of internal combustion engine i.e. diesel engine, has damping device provided for damping pressure oscillation and connected with fuel inlet that is fed from low pressure system of injection system
DE102007027667A1 (en) 2007-06-15 2008-12-18 Robert Bosch Gmbh Fuel injector for combustion chamber of internal combustion engine, has pressure amplifier piston actuatable by three/two valve, where high pressure space is provided in injector body in minimum possible distance to valve
US20090057438A1 (en) * 2007-08-28 2009-03-05 Advanced Propulsion Technologies, Inc. Ultrasonically activated fuel injector needle
US7578283B1 (en) 2008-06-30 2009-08-25 Caterpillar Inc. System for selectively increasing fuel pressure in a fuel injection system
US20100096473A1 (en) * 2008-10-20 2010-04-22 Caterpillar Inc. Variable flow rate valve for mechnically actuated fuel injector
EP2478210A4 (en) * 2009-09-17 2013-06-05 Int Engine Intellectual Prop High-pressure unit fuel injector
CN106089522B (en) * 2016-07-29 2018-11-06 中国北方发动机研究所(天津) A kind of electric-controlled fuel injector

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DE10229415A1 (en) 2002-06-29 2004-01-29 Robert Bosch Gmbh Device for damping the needle stroke on pressure-controlled fuel injectors
DE10229412A1 (en) * 2002-06-29 2004-01-29 Robert Bosch Gmbh Fuel injector with pressure intensifier for multiple injection
DE10315015B4 (en) * 2003-04-02 2005-12-15 Robert Bosch Gmbh Fuel injector with pressure booster and servo valve with optimized control quantity
JP2006522254A (en) * 2003-04-02 2006-09-28 ローベルト　ボツシユ　ゲゼルシヤフト　ミツト　ベシユレンクテル　ハフツング Servo valve controlled fuel injector with intensifier
DE10335059A1 (en) * 2003-07-31 2005-02-17 Robert Bosch Gmbh Switching valve for a fuel injector with pressure booster
DE102004024527A1 (en) * 2004-05-18 2005-12-15 Robert Bosch Gmbh Fuel injection system

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US20060090734A1 (en) 2006-05-04
DE102004053274A1 (en) 2006-05-11
DE502005006051D1 (en) 2009-01-08
US7171951B2 (en) 2007-02-06

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