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EP2111505B1 - Fuel injector with an integrated pressure booster - Google Patents

Fuel injector with an integrated pressure booster Download PDF

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Publication number
EP2111505B1
EP2111505B1 EP08701208A EP08701208A EP2111505B1 EP 2111505 B1 EP2111505 B1 EP 2111505B1 EP 08701208 A EP08701208 A EP 08701208A EP 08701208 A EP08701208 A EP 08701208A EP 2111505 B1 EP2111505 B1 EP 2111505B1
Authority
EP
European Patent Office
Prior art keywords
pressure
fuel injector
chamber
control valve
return
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.)
Active
Application number
EP08701208A
Other languages
German (de)
French (fr)
Other versions
EP2111505A1 (en
Inventor
Juergen Frasch
Heinz-Bernd Haiser
Christoph Butscher
Hans-Christoph Magel
Stephan Wehr
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
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Filing date
Publication date
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Publication of EP2111505A1 publication Critical patent/EP2111505A1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • 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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/002—Arrangement of leakage or drain conduits in or from injectors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/14—Arrangements of injectors with respect to engines; Mounting of injectors

Definitions

  • the invention is based on a fuel injector according to the preamble of claim 1.
  • a fuel injector with an integrated pressure booster is for example out DE 103 35 340 A1 known.
  • the pressure intensifier has a pressure booster piston guided in a housing of the fuel injector, which acts on a compression space, a differential pressure space and a high-pressure space.
  • a first control valve With a first control valve, a rear control chamber of a nozzle needle is controlled and derived the control volume in a low pressure / return system.
  • a second control valve also connects the differential pressure chamber of the booster to the low pressure / return system.
  • the pressure booster piston presses into the compression space and compresses the fuel, which thereby receives an increase in pressure, which is transmitted to a pressure shoulder of the nozzle needle, so that acting on the pressure shoulder translated high pressure lifts the nozzle needle from the nozzle needle seat and the fuel with the injected via the system pressure increased fuel pressure in the combustion chamber of an internal combustion engine.
  • an injection valve which has two control valves and a leakage connection on the outside, over which the leakage amount is derived.
  • a fuel injection system which has an injector with laterally formed leakage port for the leakage amount.
  • the object of the invention is achieved with the characterizing features of claim 1.
  • the fuel injector according to the invention has the advantage that a mutual function influencing the control valves is prevented. This ensures a stable quantity map of the fuel injector, which is necessary in order to ensure an optimal course of injection as a function of the power requirement to the internal combustion engine.
  • the arrangement of the two return ports in different housing parts of the housing a simple separation and design of the two return ports is possible.
  • the first return connection for the control quantity or for the control volume of the control chamber of the nozzle needle by at least one bore, which is guided through a first housing part to the outside, wherein the housing part is the nozzle retaining nut, and the second return port for the To realize control amount or for the control volume of the pressure booster by at least one further bore, which is guided by a second housing part to the outside.
  • the second bore opens into a formed on the outer wall of the housing part annular recess, wherein the recess of a first Housing portion and a second housing portion is limited, and wherein in each case a sealing ring is arranged in the first housing portion and the second housing portion.
  • the first control valve has a first low-pressure space, which is connected via a hydraulic connecting line with a first space which lies between the nozzle retaining nut and a further housing part.
  • the second control valve has a second low-pressure space, which is hydraulically connected to at least one drain hole, which leads into a second space into which the further bore of the second return port opens.
  • the second control valve is associated with a leakage chamber, which is hydraulically connected via guided through the housing hydraulic connecting lines to the first low-pressure chamber of the first control valve.
  • the leakage space is hydraulically connected to the second low-pressure chamber of the second control valve by means of a bypass channel in which a throttle is integrated.
  • each of the two return ports When installed in the internal combustion engine, each of the two return ports is connected to one integrated in a cylinder head of the internal combustion engine return passage, each return passage is connected to a respective low pressure / return system of the internal combustion engine.
  • a stepped bore is expediently formed in the cylinder head into which the housing of the fuel injector at least partially protruding, wherein within the stepped bore two hydraulically separated sections are provided with respective annular spaces, and wherein in the one annular space of the first return port and in the other annulus of the second return section opens and the annular spaces, each with a return channel are hydraulically connected.
  • the in FIG. 1 dargish fuel injector includes, for example, a housing 10 having a first housing part 11, a second housing part 12, a third housing part 13, a fourth housing part 14 and a connecting part 15 and a nozzle body 16.
  • the nozzle body 16, the housing part 14 and the housing part 13 are clamped hydraulically tight by means of a nozzle lock nut 17.
  • the nozzle body 16 includes an injection valve member 20 having a nozzle needle 21 which is guided axially displaceably in the nozzle body 16.
  • the nozzle needle 21 cooperates with a nozzle needle seat not shown in more detail, which is formed on the nozzle body 16, which forms a sealing seat with the nozzle needle 21, which in turn separates a nozzle needle pressure chamber 22 from the injection openings 23 in the closed state of the nozzle needle 21.
  • a control chamber sleeve 24 is guided, which presses by means of a compression spring 25 against a sealing surface and thereby encloses a control chamber 26.
  • the control chamber 26 is exposed to the nozzle needle 21 with a control surface 27 acting in the closing direction.
  • a high-pressure bore 18 is arranged, which leads into the nozzle needle pressure chamber 22.
  • the housing 10 has, for example on the housing part 12, a high-pressure connection 19 with a high-pressure feed line 29, with which the fuel injector is connected to a common rail of a diesel injection device.
  • a designed as a stepped piston pressure booster piston 31 for pressure amplification of the system pressure of the common rail is exposed to a working space 32, a differential pressure chamber 33 and a compression space 34.
  • the working space 32 and the compression space 34 are connected via a connecting channel 35 with a check valve 36 in connection.
  • the high-pressure feed line 29 in the working space 32
  • the pressure booster piston 31 in the in FIG. 1 resets the initial position shown.
  • the piston portion 37 serves as a stop when returning the pressure booster piston 31 to the starting position.
  • From the compression space 34 branches off a further high-pressure bore 39, which is hydraulically connected to the high-pressure bore 18, so that the pressure of the compression space 34 is transmitted to the nozzle needle pressure chamber 22.
  • the fuel injector further comprises a first control valve 40 designed as a servo valve and a second control valve 50 likewise designed as a servo valve.
  • the first control valve 40 is a 2/2 way valve and comprises a first electromagnetic control element 41 with a magnet armature 42 is connected to a first valve piston 43.
  • the valve piston 43 acts on a sealing seat 44 which separates a control bore 45 connected to the control chamber 26 from a low-pressure chamber 46.
  • a guided out of the low pressure chamber 46 of the first control valve 40 first low-pressure connection 461 leads into a housing part 14 surrounding the first annular space 48 into which a guided through the nozzle retaining nut 17 bore 49 leads.
  • the bore 49 forms a first return port 71, which is hydraulically in communication with a first low pressure / return system.
  • the control amount of the control chamber 26 of the nozzle needle 21, which is switched by the first control valve 40, is discharged into the first low pressure / return system, wherein the control quantity flows into the low pressure / return system at a substantially constant pressure level of only approximately 1 bar.
  • the second control valve 50 includes a second electromagnetic actuator 52 having a second armature 53 connected to a second valve piston 54.
  • the valve piston 54 has, for example, a first sealing seat 55 designed as a slide seat and a second sealing seat 56 designed, for example, as a flat seat, so that the second control valve 50 functions as a 3/2-way valve.
  • the first sealing seat 55 separates a high pressure line 57 connected to the working space 32 from a valve space 58.
  • the valve space 58 is connected to the differential pressure chamber 33 via a hydraulic connection 59 and is connected by means of the second sealing seat 56 hydraulically separated from another low-pressure space 61.
  • two drainage holes 62 lead to a branching space 63, which is connected via further hydraulic connections 64 to a further annular space 65.
  • two bores 66 which are guided through the housing part 13 branch off from the annular space 65 and form a second return port 72.
  • the second return port 72 communicates with a second low pressure / return system.
  • Above the bore 66 is an upper annular housing portion 75 and below the bore 66, a lower annular housing portion 76, each with a sealing ring 77 is arranged. Between the housing sections 75, 76 thus forming a running around the housing 10 recess 78 into which open the two holes 66.
  • the control amount of the pressure boosting device 30 connected by the second control valve 50 is discharged into the second low pressure / return system.
  • the control amount of the pressure booster 30 is greater than the control amount of the control chamber 26 and has much higher pressure surges.
  • the low-pressure chamber 46 of the first control valve 40 is formed via the first low-pressure connection 461 formed in the housing part 14, a second low-pressure connection 462 guided through the housing part 13, a third low-pressure connection 463 guided through the housing part 12 and a fourth low-pressure connection 464 formed in the housing part 11 with a leakage space 51 the second control valve 50 is hydraulically connected.
  • the leakage chamber 51 expands in the second control element 52 to the second valve piston 53.
  • a bypass channel 67 is arranged with a throttle 68, so that the two hydraulic chambers are connected hydraulically throttled.
  • FIG. 2 shows the fuel injector in the installed state in a cylinder head 80 of an internal combustion engine.
  • the cylinder head 80 has a stepped bore 81 with a first section 82, a second section 83 and a third section 84 and with an annular bearing surface 85.
  • On the annular bearing surface 85 is a sealing ring 86, on which the fuel injector rests with the nozzle retaining nut 17.
  • the stepped bore 81 has a first annular space 87 into which the second return port 72 opens.
  • the first annular space 87 is hydraulically sealed upwards and downwards by means of the sealing rings 77.
  • a second annular space 88 is formed, which is hydraulically sealed upwardly by the sealing ring 77 of the second housing portion 76 and down through the sealing ring 86.
  • the first return port 71 opens.
  • the first return passage 91 is connected to the first low pressure / return system.
  • a second return passage 92 leads into the first annular space 87, so that by means of the second return passage 92 further unillustrated second return ports of further fuel injectors are hydraulically coupled.
  • the second return passage 92 is hydraulically connected to the second low pressure / return system.
  • the fuel injector is fixed by means of a clamping claw 95, which acts on a flange-shaped annular surface 96 on the housing 10 of the fuel injector by means of a clamping screw 97 on the cylinder head 80, such that by means of the clamping claw 95 and the sealing ring 86 on the support surface 85, a gas-tight support of the fuel injector arises towards the combustion chamber of the internal combustion engine.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

Proposed is a fuel injector for injecting fuel into a combustion chamber of an internal combustion engine. The fuel injector has a housing in which are arranged an injection valve element with a nozzle needle, a pressure boosting device, and a first control valve, and a second control valve. The first control valve controls a control space of the nozzle needle and the second control valve controls a differential pressure space of the pressure boosting device. A first return flow connection is provided for discharging the control quantity of the control space of the nozzle needle, and a second return flow connection is provided for discharging the control quantity of the pressure boosting device. The two return flow connections are arranged on different housing parts of the housing.

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einem Kraftstoffinjektor nach dem Oberbegriff des Anspruchs 1.The invention is based on a fuel injector according to the preamble of claim 1.

Ein Kraftstoffinjektor mit einem integrierten Druckverstärker ist beispielsweise aus DE 103 35 340 A1 bekannt. Der Druckverstärker weist einen in einem Gehäuse des Kraftstoffinjektors geführten Druckübersetzerkolben auf, der auf einen Kompressionsraum, einen Differenzdruckraum und einen Hochdruckraum einwirkt. Mit einem ersten Steuerventil wird ein rückwärtiger Steuerraum einer Düsennadel ansteuert und das Steuervolumen in ein Niederdruck/ Rücklaufsystem abgeleitet. Ein zweites Steuerventil verbindet den Differenzdruckraum des Druckverstärkers ebenfalls mit dem Niederdruck/Rücklaufsystem. Durch die Druckänderung im Differenzdruckraum drückt der Druckübersetzerkolben in den Kompressionsraum und komprimiert dort den Kraftstoff, der dadurch eine Druckerhöhung erfährt, die an eine Druckschulter der Düsennadel übertragen wird, so dass der an der Druckschulter wirkende übersetzte Hochdruck die Düsennadel vom Düsennadelsitz abhebt und der Kraftstoff mit dem über den Systemdruck erhöhten Kraftstoffdruck in den Brennraum einer Brennkraftmaschine einspritzt.A fuel injector with an integrated pressure booster is for example out DE 103 35 340 A1 known. The pressure intensifier has a pressure booster piston guided in a housing of the fuel injector, which acts on a compression space, a differential pressure space and a high-pressure space. With a first control valve, a rear control chamber of a nozzle needle is controlled and derived the control volume in a low pressure / return system. A second control valve also connects the differential pressure chamber of the booster to the low pressure / return system. Due to the pressure change in the differential pressure chamber, the pressure booster piston presses into the compression space and compresses the fuel, which thereby receives an increase in pressure, which is transmitted to a pressure shoulder of the nozzle needle, so that acting on the pressure shoulder translated high pressure lifts the nozzle needle from the nozzle needle seat and the fuel with the injected via the system pressure increased fuel pressure in the combustion chamber of an internal combustion engine.

Aus der EP 1584 813 A2 ist ein Einspritzventil bekannt, bei dem zwei Steuerventile vorgesehen sind, deren Leckagemenge über separate Leckageanschlüsse und jeweils eine Leckageleitung abgeführt wird.From the EP 1584 813 A2 an injection valve is known in which two control valves are provided, the leakage quantity is discharged via separate leakage ports and a respective leakage line.

Aus der DE 10 2004 053 421 A1 ist ebenfalls ein Einspritzventil bekannt, das zwei Steuerventile aufweist und einen Leckageanschluss an der Außenseite, über den die Leckagemenge abgeleitet wird.From the DE 10 2004 053 421 A1 Also, an injection valve is known which has two control valves and a leakage connection on the outside, over which the leakage amount is derived.

Aus der DE 10 2004 008 349 A1 ist ein Brennstoffeinspritzsystem bekannt, das einen Injektor mit seitlich ausgebildetem Leckageanschluss für die Leckagemenge aufweist.From the DE 10 2004 008 349 A1 For example, a fuel injection system is known which has an injector with laterally formed leakage port for the leakage amount.

In der deutschen Patentanmeldung DE 100 206 038 840.2 wird bereits gezeigt, für das die Düsennadel ansteuernde erste Steuerventil und das den Druckverstärker ansteuernde zweite Steuerventil jeweils einenIn the German patent application DE 100 206 038 840.2 is already shown, for the nozzle needle controlling first control valve and the pressure booster driving second control valve each one

Rücklaufanschluss zum Verbinden mit dem Niederdruck/Rücklaufsystem vorzusehen.To provide return connection for connection to the low pressure / return system.

Da die Rücklaufsysteme für das erste Steuerventil der Düsennadel und für das zweite Steuerventil des Druckverstärkers unterschiedlichen Druckniveaus ausgesetzt sind und darüber hinaus das Rücklaufsystem des Druckverstärkers mit starken Druckstößen beaufschlagt wird, ist eine technisch sinnvolle Entkopplung beider Rücklaufkreise innerhalb des Kraftstoffinjektors notwendig. Außerdem ist eine geeignete Anordnung der beiden Rücklaufanschlüsse am Injektorgehäuse notwendig.Since the return systems for the first control valve of the nozzle needle and the second control valve of the pressure intensifier are exposed to different pressure levels and beyond the return system of the pressure intensifier is subjected to strong pressure surges, a technically meaningful decoupling of both return circuits within the fuel injector is necessary. In addition, a suitable arrangement of the two return ports on the injector is necessary.

Offenbarung der ErfindungDisclosure of the invention

Die Aufgabe der Erfindung wird mit den kennzeichnenden Merkmalen des Anspruchs 1 gelöst. Der erfindungsgemäße Kraftstoffinjektor hat den Vorteil, dass eine gegenseitige Funktionsbeeinflussung der Steuerventile verhindert wird. Dadurch wird ein stabiles Mengenkennfeld des Kraftstoffinjektors gewährleistet, das notwendig ist, um einen optimalen Einspritzverlauf in Abhängigkeit von der Leistungsanforderung an die Brennkraftmaschine zu gewährleisten. Durch die Anordnung der beiden Rücklaufanschlüsse in unterschiedlichen Gehäuseteilen des Gehäuses ist eine einfache Trennung und Ausführung der beiden Rücklaufanschlüsse möglich.The object of the invention is achieved with the characterizing features of claim 1. The fuel injector according to the invention has the advantage that a mutual function influencing the control valves is prevented. This ensures a stable quantity map of the fuel injector, which is necessary in order to ensure an optimal course of injection as a function of the power requirement to the internal combustion engine. The arrangement of the two return ports in different housing parts of the housing a simple separation and design of the two return ports is possible.

Vorteilhafte Weiterbildungen der Erfindung sind durch die Maßnahmen der Unteransprüche möglich.Advantageous developments of the invention are possible by the measures of the subclaims.

Besonders vorteilhaft ist es, den ersten Rücklaufanschluss für die Steuermenge bzw. für das Steuervolumen des Steuerraums der Düsennadel durch mindestens eine Bohrung zu realisieren, die durch ein erstes Gehäuseteil nach außen geführt ist, wobei das Gehäuseteil die Düsenspannmutter ist, und den zweite Rücklaufanschluss für die Steuermenge bzw. für das Steuervolumen der Druckverstärkungseinrichtung durch mindestens eine weitere Bohrung zu realisieren, die durch ein zweites Gehäuseteil nach außen geführt ist. Dabei mündet die zweite Bohrung in eine an der Außenwand des Gehäuseteils ausgebildete ringförmige Vertiefung, wobei die Vertiefung von einem ersten Gehäuseabschnitt und einem zweiten Gehäuseabschnitt begrenzt ist, und wobei im ersten Gehäuseabschnitt und im zweiten Gehäuseabschnitt jeweils ein Dichtring angeordnet ist.It is particularly advantageous to realize the first return connection for the control quantity or for the control volume of the control chamber of the nozzle needle by at least one bore, which is guided through a first housing part to the outside, wherein the housing part is the nozzle retaining nut, and the second return port for the To realize control amount or for the control volume of the pressure booster by at least one further bore, which is guided by a second housing part to the outside. In this case, the second bore opens into a formed on the outer wall of the housing part annular recess, wherein the recess of a first Housing portion and a second housing portion is limited, and wherein in each case a sealing ring is arranged in the first housing portion and the second housing portion.

Das erste Steuerventil weist einen ersten Niederdruckraum auf, der über eine hydraulischen Verbindungsleitung mit einem ersten Raum verbunden ist, der zwischen der Düsenspannmutter und einem weiteren Gehäuseteil liegt. Das zweite Steuerventil weist einen zweiten Niederdruckraum auf, der mit mindestens einer Ablaufbohrung hydraulisch verbunden ist, die in einen zweiten Raum führt, in den die weitere Bohrung des zweiten Rücklaufanschluss mündet. Dem zweiten Steuerventil ist ein Leckageraum zugeordnet, der über durch das Gehäuse geführte hydraulische Verbindungsleitungen mit dem ersten Niederdruckraum des ersten Steuerventils hydraulisch verbunden ist. Der Leckageraum ist mittels eines Bypasskanals, in den eine Drossel integriert ist, mit dem zweiten Niederdruckraum des zweiten Steuerventils hydraulisch verbunden.The first control valve has a first low-pressure space, which is connected via a hydraulic connecting line with a first space which lies between the nozzle retaining nut and a further housing part. The second control valve has a second low-pressure space, which is hydraulically connected to at least one drain hole, which leads into a second space into which the further bore of the second return port opens. The second control valve is associated with a leakage chamber, which is hydraulically connected via guided through the housing hydraulic connecting lines to the first low-pressure chamber of the first control valve. The leakage space is hydraulically connected to the second low-pressure chamber of the second control valve by means of a bypass channel in which a throttle is integrated.

Im eingebauten Zustand in die Verbrennungskraftmaschine ist jeder der beiden Rücklaufanschlüsse mit jeweils einem in einem Zylinderkopf der Verbrennungskraftmaschine integrierten Rücklaufkanal verbunden, wobei jeder Rücklaufkanal an jeweils ein Niederdruck/Rücklaufsystem der Verbrennungskraftmaschine angeschlossen ist. Dazu ist zweckmäßigerweise im Zylinderkopf eine Stufenbohrung ausgebildet, in die das Gehäuse des Kraftstoffinjektors zumindest teilweise hineinragt, wobei innerhalb der Stufenbohrung zwei hydraulisch getrennte Abschnitte mit jeweiligen Ringräumen vorhanden sind, und wobei in den einen Ringraum der erste Rücklaufanschluss und in den anderen Ringraum der zweite Rücklaufabschnitt mündet und die Ringräume mit jeweils einem Rücklaufkanal hydraulisch verbunden sind.When installed in the internal combustion engine, each of the two return ports is connected to one integrated in a cylinder head of the internal combustion engine return passage, each return passage is connected to a respective low pressure / return system of the internal combustion engine. For this purpose, a stepped bore is expediently formed in the cylinder head into which the housing of the fuel injector at least partially protruding, wherein within the stepped bore two hydraulically separated sections are provided with respective annular spaces, and wherein in the one annular space of the first return port and in the other annulus of the second return section opens and the annular spaces, each with a return channel are hydraulically connected.

Ausführungsbeispielembodiment

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert.An embodiment of the invention is illustrated in the drawing and explained in more detail in the following description.

Es zeigen:

Figur 1
eine Schnittdarstellung durch einen erfindungsgemäßen Kraftstoffinjektor und
Figur 2
eine Schnittdarstellung durch den erfindungsgemäßen Kraftstoffinjektor im eingebauten Zustand in einen Zylinderkopf einer Brennkraftmaschine.
Show it:
FIG. 1
a sectional view through an inventive Fuel injector and
FIG. 2
a sectional view through the fuel injector according to the invention in the installed state in a cylinder head of an internal combustion engine.

Der in Figur 1 dargstellte Kraftstoffinjektor weist beispielweise ein Gehäuse 10 mit einem ersten Gehäuseteil 11, einem zweiten Gehäuseteil 12, einem dritten Gehäuseteil 13, einem vierten Gehäuseteil 14 und einem Anschlussteil 15 sowie mit einem Düsenkörper 16 auf. Der Düsenkörper 16, das Gehäuseteil 14 und das Gehäuseteil 13 sind mittels einer Düsenspannmutter 17 hydraulisch dicht verspannt. Der Düsenkörper 16 enthält ein Einspritzventilglied 20 mit einer Düsennadel 21, die im Düsenkörper 16 axial verschiebbar geführt ist. Die Düsennadel 21 wirkt mit einem nicht näher dargestellten, am Düsenkörper 16 ausgebildeten Düsennadelsitz zusammen, der mit der Düsennadel 21 einen Dichtsitz bildet, der wiederum einen Düsennadeldruckraum 22 im geschlossenen Zustand der Düsennadel 21 von Einspritzöffnungen 23 trennt. An der Düsennadel 21 ist eine Steuerraumhülse 24 geführt, die mittels einer Druckfeder 25 gegen eine Dichtfläche drückt und dadurch einen Steuerraum 26 umschließt. Dem Steuerraum 26 ist die Düsennadel 21 mit einer in Schließrichtung wirkenden Steuerfläche 27 ausgesetzt. Im Gehäuseteil 14 ist eine Hochdruckbohrung 18 angeordnet, die in den Düsennadeldruckraum 22 führt. Das Gehäuse 10 weist beispielsweise am Gehäuseteil 12 einen Hochdruckanschluss 19 mit einer Hochdruckzuleitung 29 auf, mit dem der Kraftstoffinjektor an ein Common-Rail einer Dieseleinspritzeinrichtung angeschlossen ist.The in FIG. 1 dargstellte fuel injector includes, for example, a housing 10 having a first housing part 11, a second housing part 12, a third housing part 13, a fourth housing part 14 and a connecting part 15 and a nozzle body 16. The nozzle body 16, the housing part 14 and the housing part 13 are clamped hydraulically tight by means of a nozzle lock nut 17. The nozzle body 16 includes an injection valve member 20 having a nozzle needle 21 which is guided axially displaceably in the nozzle body 16. The nozzle needle 21 cooperates with a nozzle needle seat not shown in more detail, which is formed on the nozzle body 16, which forms a sealing seat with the nozzle needle 21, which in turn separates a nozzle needle pressure chamber 22 from the injection openings 23 in the closed state of the nozzle needle 21. At the nozzle needle 21, a control chamber sleeve 24 is guided, which presses by means of a compression spring 25 against a sealing surface and thereby encloses a control chamber 26. The control chamber 26 is exposed to the nozzle needle 21 with a control surface 27 acting in the closing direction. In the housing part 14, a high-pressure bore 18 is arranged, which leads into the nozzle needle pressure chamber 22. The housing 10 has, for example on the housing part 12, a high-pressure connection 19 with a high-pressure feed line 29, with which the fuel injector is connected to a common rail of a diesel injection device.

Im Gehäuse 10 des Kraftstoffinjektors ist weiterhin zur Druckverstärkung des Systemdrucks des Common-Rails eine Druckverstärkungseinrichtung 30 mit einem als Stufenkolben ausgeführten Druckübersetzerkolben 31 angeordnet. Der Druckübersetzerkolben 31 ist einem Arbeitsraum 32, einem Differenzdruckraum 33 und einem Kompressionsraum 34 ausgesetzt. Der Arbeitsraum 32 und der Kompressionsraum 34 stehen über einen Verbindungskanal 35 mit einem Rückschlagventil 36 in Verbindung. In den Arbeitsraum 32 führt die Hochdruckzuleitung 29, so dass im Arbeitsraum permanent Systemdruck des Common-Rails anliegt. In den Arbeitsraum 32 ragt ferner eine oberer Kolbenabschnitt 37 des Druckübersetzerkolbens 31, der von einer Rückstellfeder 38 umgeben ist, die den Druckübersetzerkolben 31 in die in Figur 1 dargestellte Ausgangsposition zurückstellt. Der Kolbenabschnitt 37 dient als Anschlag beim Zurückstellen des Druckübersetzerkolbens 31 in die Ausgangsposition. Aus dem Kompressionsraum 34 zweigt eine weitere Hochdruckbohrung 39 ab, die mit der Hochdruckbohrung 18 hydraulisch verbunden ist, so dass der Druck des Kompressionsraums 34 in den Düsennadeldruckraum 22 übertragen wird.In the housing 10 of the fuel injector pressure amplification device 30 is further arranged with a designed as a stepped piston pressure booster piston 31 for pressure amplification of the system pressure of the common rail. The pressure booster piston 31 is exposed to a working space 32, a differential pressure chamber 33 and a compression space 34. The working space 32 and the compression space 34 are connected via a connecting channel 35 with a check valve 36 in connection. In the working space 32, the high-pressure feed line 29, so that in the working space permanently applied system pressure of the common rail. In the working space 32 further protrudes an upper piston portion 37 of the pressure booster piston 31, of a return spring 38 is surrounded, the pressure booster piston 31 in the in FIG. 1 resets the initial position shown. The piston portion 37 serves as a stop when returning the pressure booster piston 31 to the starting position. From the compression space 34 branches off a further high-pressure bore 39, which is hydraulically connected to the high-pressure bore 18, so that the pressure of the compression space 34 is transmitted to the nozzle needle pressure chamber 22.

Der Kraftstoffinjektor umfasst weiterhin ein als Servo-Ventil ausgebildetes erstes Steuerventil 40 und ein ebenfalls als Servo-Ventil ausgebildetes zweites Steuerventil 50. Das erste Steuerventil 40 ist ein 2/2 Wege-Ventil und umfasst ein erstes elektromagnetisches Stellelement 41 mit einem Magnetanker 42, der mit einem ersten Ventilkolben 43 verbunden ist. Der Ventilkolben 43 wirkt auf einen Dichtsitz 44, der eine mit dem Steuerraum 26 verbundene Steuerbohrung 45 von einem Niederdruckraum 46 trennt. Eine aus dem Niederdruckraum 46 des ersten Steuerventils 40 herausgeführte erste Niederdruckverbindung 461 führt in einen das Gehäuseteil 14 umgebenden ersten Ringraum 48, in den eine durch die Düsenspannmutter 17 geführte Bohrung 49 führt. Die Bohrung 49 bildet einen ersten Rücklaufanschluss 71, der hydraulisch mit einem ersten Niederdruck/Rücklaufsystem in Verbindung steht.The fuel injector further comprises a first control valve 40 designed as a servo valve and a second control valve 50 likewise designed as a servo valve. The first control valve 40 is a 2/2 way valve and comprises a first electromagnetic control element 41 with a magnet armature 42 is connected to a first valve piston 43. The valve piston 43 acts on a sealing seat 44 which separates a control bore 45 connected to the control chamber 26 from a low-pressure chamber 46. A guided out of the low pressure chamber 46 of the first control valve 40 first low-pressure connection 461 leads into a housing part 14 surrounding the first annular space 48 into which a guided through the nozzle retaining nut 17 bore 49 leads. The bore 49 forms a first return port 71, which is hydraulically in communication with a first low pressure / return system.

Über den ersten Rücklaufanschluss 71 wird die vom ersten Steuerventil 40 geschaltete Steuermenge des Steuerraums 26 der Düsennadel 21 in das erste Niederdruck/Rücklaufsystem abgeführt, wobei die Steuermenge mit einem im Wesentlichen konstanten Druckniveau von lediglich ca. 1 bar in das Niederdruck/Rücklaufsystem abfließt.Via the first return port 71, the control amount of the control chamber 26 of the nozzle needle 21, which is switched by the first control valve 40, is discharged into the first low pressure / return system, wherein the control quantity flows into the low pressure / return system at a substantially constant pressure level of only approximately 1 bar.

Das zweite Steuerventil 50 umfasst ein zweites elektromagnetisches Stellelement 52 mit einem zweiten Magnetanker 53, der mit einem zweiten Ventilkolben 54 verbunden ist. Der Ventilkolben 54 weist beispielsweise einen als Schiebersitz ausgebildeten ersten Dichtsitz 55 und einen beispielsweise als Flachsitz ausgeführten zweiten Dichtsitz 56 auf, so dass das zweite Steuerventil 50 als 3/2-Wege-Ventil arbeitet. Der erste Dichtsitz 55 trennt eine mit dem Arbeitsraum 32 verbundene Hochdruckleitung 57 von einem Ventilraum 58. Der Ventilraum 58 ist über eine hydraulische Verbindung 59 mit dem Differenzdruckraum 33 verbunden und wird mittels des zweiten Dichtsitzes 56 von einem weiteren Niederdruckraum 61 hydraulisch getrennt. Vom Niederdruckraum 61 führen beispielsweise zwei Ablaufbohrungen 62 zu einem Verzweigungsraum 63, der über weitere hydraulischen Verbindungen 64 mit einem weiteren Ringraum 65 in Verbindung steht. Vom Ringraum 65 zweigen beispielsweise zwei durch das Gehäuseteil 13 geführten Bohrungen 66 ab, die einen zweiten Rücklaufanschluss 72 bilden. Der zweite Rücklaufanschluss 72 steht mit einem zweiten Niederdruck/Rücklaufsystem in Verbindung. Oberhalb der Bohrung 66 ist ein oberer ringförmiger Gehäuseabschnitt 75 und unterhalb der Bohrung 66 ein unterer ringförmiger Gehäuseabschnitt 76 mit je einem Dichtring 77 angeordnet. Zwischen den Gehäuseabschnitten 75, 76 bildet sich somit eine um das Gehäuse 10 verlaufende Vertiefung 78 aus, in die die beiden Bohrungen 66 münden. Auf die Funktion der Gehäuseabschnitte 75, 76 und der Dichtringe 77 wird im Zusammenhang mit Figur 2 eingegangen. Über den zweiten Rücklaufanschluss 72 wird die vom zweiten Steuerventil 50 geschaltete Steuermenge der Druckverstärkungseinrichtung 30 in das zweite Niederdruck/Rücklaufsystem abgeführt. Die Steuermenge der Druckverstärkungseinrichtung 30 ist größer als die Steuermenge des Steuerraums 26 und weist wesentlich höhere Druckstöße auf.The second control valve 50 includes a second electromagnetic actuator 52 having a second armature 53 connected to a second valve piston 54. The valve piston 54 has, for example, a first sealing seat 55 designed as a slide seat and a second sealing seat 56 designed, for example, as a flat seat, so that the second control valve 50 functions as a 3/2-way valve. The first sealing seat 55 separates a high pressure line 57 connected to the working space 32 from a valve space 58. The valve space 58 is connected to the differential pressure chamber 33 via a hydraulic connection 59 and is connected by means of the second sealing seat 56 hydraulically separated from another low-pressure space 61. From the low-pressure space 61, for example, two drainage holes 62 lead to a branching space 63, which is connected via further hydraulic connections 64 to a further annular space 65. For example, two bores 66 which are guided through the housing part 13 branch off from the annular space 65 and form a second return port 72. The second return port 72 communicates with a second low pressure / return system. Above the bore 66 is an upper annular housing portion 75 and below the bore 66, a lower annular housing portion 76, each with a sealing ring 77 is arranged. Between the housing sections 75, 76 thus forming a running around the housing 10 recess 78 into which open the two holes 66. On the function of the housing sections 75, 76 and the sealing rings 77 is in connection with FIG. 2 received. Via the second return port 72, the control amount of the pressure boosting device 30 connected by the second control valve 50 is discharged into the second low pressure / return system. The control amount of the pressure booster 30 is greater than the control amount of the control chamber 26 and has much higher pressure surges.

Der Niederdruckraum 46 des ersten Steuerventils 40 ist über die im Gehäuseteil 14 ausgebildete erste Niederdruckverbindung 461, eine durch das Gehäuseteil 13 geführte zweite Niederdruckverbindung 462, eine durch das Gehäuseteil 12 geführte dritte Niederdruckverbindung 463 und einer im Gehäuseteil 11 ausgebildeten vierten Niederdruckverbindung 464 mit einem Leckageraum 51 des zweiten Steuerventils 50 hydraulisch verbunden. Der Leckageraum 51 dehnt sich dabei im zweiten Stellelement 52 bis zum zweiten Ventilkolben 53 aus. Zwischen dem Leckageraum 51 und dem weiteren Niederdruckraum 61 ist ein Bypasskanal 67 mit einer Drossel 68 angeordnet, so dass die beiden hydraulischen Räume hydraulisch gedrosselt verbunden sind.The low-pressure chamber 46 of the first control valve 40 is formed via the first low-pressure connection 461 formed in the housing part 14, a second low-pressure connection 462 guided through the housing part 13, a third low-pressure connection 463 guided through the housing part 12 and a fourth low-pressure connection 464 formed in the housing part 11 with a leakage space 51 the second control valve 50 is hydraulically connected. The leakage chamber 51 expands in the second control element 52 to the second valve piston 53. Between the leakage chamber 51 and the further low-pressure chamber 61, a bypass channel 67 is arranged with a throttle 68, so that the two hydraulic chambers are connected hydraulically throttled.

Durch das Vorliegen von zwei getrennten Rücklaufanschlüssen 71, 72 für den Rücklauf des Steuervolumens der Druckverstärkungseinrichtung 30 und des Steuervolumens des Steuerraums 26 der Düsennadel 21 wird gewährleistet, dass das mit großen Druckstößen belastete Steuervolumen der Druckverstärkungseinrichtung 30 nicht das erste Steuerventil 40 zur Ansteuerung der Düsenadel 21 beeinflusst.The presence of two separate return ports 71, 72 for the return of the control volume of the pressure booster 30 and the control volume of the control chamber 26 of the nozzle needle 21 ensures that the loaded with large pressure surges control volume of Pressure booster 30 does not affect the first control valve 40 for controlling the nozzle needle 21.

Figur 2 zeigt den Kraftstoffinjektor im eingebauten Zustand in einem Zylinderkopf 80 einer Brennkraftmaschine. Dabei weist der Zylinderkopf 80 eine Stufenbohrung 81 mit einem ersten Abschnitt 82, einem zweiten Abschnitt 83 und einem dritten Abschnitt 84 sowie mit einer ringförmigen Auflagefläche 85 auf. Auf der ringförmigen Auflagefläche 85 liegt ein Dichtring 86 auf, auf den der Kraftstoffinjektor mit der Düsenspannmutter 17 aufliegt. Im ersten Abschnitt 82 weist die Stufenbohrung 81 einen ersten Ringraum 87 auf, in den der zweite Rücklaufanschluss 72 mündet. Der erste Ringraum 87 ist nach oben und unten jeweils mittels der Dichtringe 77 hydraulisch abgedichtet. Im zweiten Abschnitt 83 ist ein zweiter Ringraum 88 ausgebildet, der nach oben durch den Dichtring 77 des zweiten Gehäuseabschnitts 76 und nach unten durch den Dichtring 86 hydraulisch abgedichtet ist. In den zweiten Ringraum 88 mündet der erste Rücklaufanschluss 71. Aus dem zweiten Ringraum 88 führt ein erster Rücklaufkanal 91 heraus, der nicht dargestellte ersten Rücklaufanschlüsse weiterer Kraftstoffinjektoren miteinander hydraulisch verbindet. Der erste Rücklaufkanal 91 ist an das erste Niederdruck/Rücklaufsystem angeschlossen. Ein zweiter Rücklaufkanal 92 führt in den ersten Ringraum 87, so dass mittels des zweiten Rücklaufkanals 92 weitere nicht dargestellt zweite Rücklaufanschlüsse weiterer Kraftstoffinjektoren hydraulisch gekoppelt sind. Der zweite Rücklaufkanal 92 ist mit dem zweiten Niederdruck/Rücklaufsystem hydraulisch verbunden. FIG. 2 shows the fuel injector in the installed state in a cylinder head 80 of an internal combustion engine. In this case, the cylinder head 80 has a stepped bore 81 with a first section 82, a second section 83 and a third section 84 and with an annular bearing surface 85. On the annular bearing surface 85 is a sealing ring 86, on which the fuel injector rests with the nozzle retaining nut 17. In the first section 82, the stepped bore 81 has a first annular space 87 into which the second return port 72 opens. The first annular space 87 is hydraulically sealed upwards and downwards by means of the sealing rings 77. In the second section 83, a second annular space 88 is formed, which is hydraulically sealed upwardly by the sealing ring 77 of the second housing portion 76 and down through the sealing ring 86. In the second annular space 88, the first return port 71 opens. From the second annulus 88 performs a first return passage 91, the first return ports not shown further fuel injectors connects to each other hydraulically. The first return passage 91 is connected to the first low pressure / return system. A second return passage 92 leads into the first annular space 87, so that by means of the second return passage 92 further unillustrated second return ports of further fuel injectors are hydraulically coupled. The second return passage 92 is hydraulically connected to the second low pressure / return system.

Der Kraftstoffinjektor wird mittels einer Spannpratze 95, die an einer flanschförmigen Ringfläche 96 am Gehäuse 10 des Kraftstoffinjektors angreift, mittels einer Spannschraube 97 am Zylinderkopf 80 befestigt, derart, dass mittels der Spannpratze 95 und des Dichtrings 86 an der Auflagefläche 85 eine gasdichte Auflage des Kraftstoffinjektors zum Brennraum der Brennkraftmaschine hin entsteht.The fuel injector is fixed by means of a clamping claw 95, which acts on a flange-shaped annular surface 96 on the housing 10 of the fuel injector by means of a clamping screw 97 on the cylinder head 80, such that by means of the clamping claw 95 and the sealing ring 86 on the support surface 85, a gas-tight support of the fuel injector arises towards the combustion chamber of the internal combustion engine.

Claims (10)

  1. Fuel injector for injecting fuel into a combustion chamber of an internal combustion engine, having a housing (10) in which are arranged an injection valve member (20) with a nozzle needle (21) for opening and closing at least one injection opening (23), a pressure boosting device (30) by means of which fuel at system pressure is compressed to injection pressure, and a first control valve (40) and a second control valve (50), wherein the first control valve (40) controls a control chamber (26) of the nozzle needle (21) and the second control valve (50) controls a differential pressure chamber (33) of the pressure boosting device (30), wherein a high-pressure port (19) is provided for the supply of the fuel, and wherein a first return port (71) is provided for discharging a control quantity of a control chamber (26) from the nozzle needle (21) and a second return port (72) is provided for discharging a control quantity from the pressure boosting device (30), and the two return ports (71, 72) are arranged on different housing parts of the housing (10), characterized in that the second control valve (50) is assigned a leakage chamber (51) which is hydraulically connected to the first low-pressure chamber (46) of the control valve (40) via hydraulic connecting lines (461, 462, 463, 464) guided through the housing (10).
  2. Fuel injector according to Claim 1, characterized in that the first return port (71) for the control quantity from the nozzle needle (21) is realized by at least one bore (49) which is guided to the outside through a housing part arranged close to the nozzle needle (21).
  3. Fuel injector according to Claim 2, characterized in that the housing part arranged close to the nozzle needle is a nozzle clamping nut (17).
  4. Fuel injector according to Claim 1, characterized in that the second return port (72) for the control quantity from the pressure boosting device (30) is realized by at least one further bore (66) which is guided to the outside through a second housing part (13).
  5. Fuel injector according to Claim 4, characterized in that the further bore (66) opens into an annular depression (78) formed on the outer wall of the housing part (13), in that the depression (78) is delimited by a first housing portion (75) and a second housing portion (76), and in that in each case one sealing ring (77) is arranged in the first housing portion (75) and in the second housing portion (76).
  6. Fuel injector according to Claim 1, characterized in that the first control valve (40) has a first low-pressure chamber (46) which is connected via a hydraulic connecting line (461) to a first chamber (48), and in that the bore (49) of the first return port (71) opens into the first chamber (48).
  7. Fuel injector according to Claim 1, characterized in that the second control valve (50) has a second low-pressure chamber (61) which is hydraulically connected to at least one outflow bore (62) which leads into a second chamber (65) into which the further bore (66) of the second return port (72) opens.
  8. Fuel injector according to Claim 1, characterized in that the leakage chamber (51) is hydraulically connected to the second low-pressure chamber (61) of the second control valve (50) by means of a bypass duct (67) into which a throttle (68) is integrated.
  9. Fuel injector according to one of the preceding claims, characterized in that each of the two return ports (71, 72) is connected in each case to a return duct (91, 92) integrated into a cylinder head (80) of the internal combustion engine, and in that each return duct (91, 92) is connected to in each case one low-pressure/return system of the internal combustion engine.
  10. Fuel injector according to Claim 9, characterized in that, in the cylinder head (80), there is formed a stepped bore (81) into which the housing (10) at least partially projects, in that at least two hydraulically separate portions (82, 83) are formed within the stepped bore (81), in that the first return port (71) opens into one portion (83) and the second return port (72) opens into the other portion (82), and in that the portions (82, 83) are connected to in each case one of the return ducts (91, 92).
EP08701208A 2007-01-18 2008-01-03 Fuel injector with an integrated pressure booster Active EP2111505B1 (en)

Applications Claiming Priority (2)

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DE102007002760A DE102007002760A1 (en) 2007-01-18 2007-01-18 Fuel injector with integrated pressure booster
PCT/EP2008/050022 WO2008087052A1 (en) 2007-01-18 2008-01-03 Fuel injector with an integrated pressure booster

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EP2111505A1 EP2111505A1 (en) 2009-10-28
EP2111505B1 true EP2111505B1 (en) 2012-03-14

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US (1) US8348176B2 (en)
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JP (1) JP5108897B2 (en)
CN (1) CN101583791B (en)
AT (1) ATE549506T1 (en)
DE (1) DE102007002760A1 (en)
ES (1) ES2379841T3 (en)
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JP2010516933A (en) 2010-05-20
ES2379841T3 (en) 2012-05-04
US20100019068A1 (en) 2010-01-28
EP2111505A1 (en) 2009-10-28
JP5108897B2 (en) 2012-12-26
WO2008087052A1 (en) 2008-07-24
CN101583791A (en) 2009-11-18
ATE549506T1 (en) 2012-03-15
CN101583791B (en) 2013-11-06
DE102007002760A1 (en) 2008-07-24
US8348176B2 (en) 2013-01-08

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