EP2082127B1 - Injector for injecting fuel into combustion chambers of internal combustion engines - Google Patents

Injector for injecting fuel into combustion chambers of internal combustion engines Download PDF

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Publication number
EP2082127B1
EP2082127B1 EP07820155A EP07820155A EP2082127B1 EP 2082127 B1 EP2082127 B1 EP 2082127B1 EP 07820155 A EP07820155 A EP 07820155A EP 07820155 A EP07820155 A EP 07820155A EP 2082127 B1 EP2082127 B1 EP 2082127B1
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EP
European Patent Office
Prior art keywords
valve
pressure
valve sleeve
valve seat
fuel
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.)
Not-in-force
Application number
EP07820155A
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German (de)
French (fr)
Other versions
EP2082127A1 (en
Inventor
Andreas Rettich
Friedrich Boecking
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
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Robert Bosch GmbH
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Publication of EP2082127A1 publication Critical patent/EP2082127A1/en
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Publication of EP2082127B1 publication Critical patent/EP2082127B1/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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member
    • F02M63/008—Hollow valve members, e.g. members internally guided
    • 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
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/003—Valve inserts containing control chamber and valve piston

Definitions

  • the invention relates to an injector according to the preamble of claim 1.
  • the EP 1 612 403 A1 describes a common rail injector with a pressure compensated in the axial direction control valve for locking and opening a Kraftstoffablaufweges from a control chamber.
  • the fuel pressure can be influenced within the control chamber.
  • the control chamber is supplied via a pressure channel with fuel from a hydraulically connected to a high-pressure fuel pressure chamber.
  • a nozzle needle is moved between an open position and a closed position, wherein the nozzle needle in its open position releases the fuel flow into the combustion chamber of an internal combustion engine.
  • the control valve has an adjustable in the axial direction by means of an electromagnetic actuator valve sleeve, which cooperates sealingly with a stationary, conical valve seat surface.
  • the invention is therefore based on the object to propose an injector with a control valve, the opening characteristic remains at least substantially constant over its lifetime.
  • the invention is based on the idea, instead of a raised, for example conical valve seat provided as a flat seat valve seat with a flat valve seat surface, wherein the flat valve seat surface sealingly cooperates with a frontal peripheral edge of the valve sleeve of the control valve.
  • the peripheral edge extends from the valve sleeve in the axial direction.
  • the peripheral edge so the bearing edge, with which the valve sleeve rests on the flat valve seat surface, must be formed by the inner circumference of the valve sleeve.
  • the diameter of the peripheral edge is equal to the inner diameter of the valve sleeve in its guide portion on the axial pressure forces receiving guide pin in a pressure compensated in the axial direction control valve.
  • angles between the valve seat surface and the annular surface are suitable in a range between approximately 0.5 ° and 20 °.
  • the angle is approximately between 1 ° and 10 °; optimum results are achieved at an angle of about 5 °.
  • a defined pressure application surface can be provided in development of the invention at the expense of the axial pressure balance, which ensures that when a maximum fuel pressure within the valve sleeve is exceeded, it lifts from the flat valve seat and thus the fuel under an impermissible overpressure into a low-pressure space can drain away.
  • the pressure application surface is dimensioned such that the valve sleeve lifts at fuel pressures from 2100 bar, in particular from 2200 bar against the force of a valve spring from the valve seat.
  • the pressure application surface is designed as a circumferential pressure level. Such a pressure application surface is easy to produce with high accuracy.
  • the peripheral edge with which the valve sleeve rests on the flat valve seat surface, arranged at a radial distance from the guided on the guide pin inner surface of the valve sleeve.
  • this inner surface and the peripheral edge is preferably formed as a circumferential pressure step pressure application surface.
  • the guide pin extends from an area radially inside the flat valve seat surface in the axial direction into the valve sleeve.
  • valve sleeve is formed in an embodiment of the invention in one piece with an anchor plate of the actuator designed as an actuator.
  • the Kraftstoffablaufweg runs through the valve seat having the component in the axial direction in the guide pin and from there in the radial direction from this into an annular space within the valve sleeve. From there, the fuel can flow in the radial direction in a low-pressure chamber with valve sleeve lifted from the valve seat.
  • Fig. 1 are shown schematically the essential parts for the control of a common rail injector 1.
  • a common rail injector 1 Within a nozzle body 2, an elongated nozzle needle 3 is movably guided in the axial direction.
  • the nozzle needle 3 has at its needle tip, not shown, a closing surface with which it can be brought into tight contact with a needle body within the nozzle body 3, also not shown.
  • the fuel outlet When the nozzle needle 3 rests against the needle seat, the fuel outlet is blocked from a nozzle hole arrangement, not shown. If, on the other hand, it is raised from the needle seat, fuel can flow from a pressure chamber 4 in the axial direction along the nozzle needle 3 through the nozzle hole arrangement and be sprayed into a combustion chamber substantially under high pressure (rail pressure).
  • the basic structure of an injector 1 is known. In this regard is on the DE 100 24 703 A1 directed.
  • the injector 1 has a throttle plate 5, which extends sleeve-shaped in the plane of the drawing down into the nozzle body 2 inside.
  • a control chamber 7 is limited.
  • the control chamber 7 is connected via a pressure channel 8 with inlet throttle 9 to the pressure chamber 4, which in turn is connected via a supply line, not shown, with a high-pressure fuel storage. High-pressure fuel can thus flow into the control chamber 7 via the pressure channel 8.
  • From the control chamber 7 leads out in the axial direction of a fuel drain 10 with outlet throttle 11. About the fuel drain 10, fuel from the control chamber 7 with open control valve 12 can flow into a low-pressure chamber 13.
  • the flow cross-sections of the inlet throttle 9 and the outlet throttle 11 are coordinated so that the inflow through the pressure channel 8 is weaker than the outflow through the fuel drain 10 and thus with open control valve 12, a net outflow of fuel from the control chamber 7 results.
  • the resulting pressure drop in the control chamber 7 causes the amount of closing force falls below the amount of the opening force and lifts the nozzle needle 3 from its needle seat.
  • the fuel drainage path 10 leads through the throttle plate 5 with outlet throttle 11 in a plane arranged in the drawing plane component 14.
  • the component 14 has a valve seat 22 (flat seat) with a flat valve seat surface 15 of the control valve 12, wherein a valve sleeve 16 of the control valve 12 in the closed Control valve sealingly rests on the valve seat surface 15.
  • the valve sleeve 16 is spring-loaded by a valve spring 17 in the axial direction on the valve seat surface 15.
  • the valve spring 17 is supported in the plane of the drawing on top of an injector body 18 and at the opposite end on a spring guide part 19, which in turn rests on the valve sleeve 16.
  • the valve sleeve 15 is penetrated in the axial direction by a guide pin 25, on whose outer surface it is guided.
  • the guide pin 25 is formed integrally with a cylindrical portion of the component 14.
  • the valve spring 17 is disposed within an electromagnet 20.
  • an armature plate 21 formed integrally with the valve sleeve 16 is moved axially in the direction of the electromagnet 20, whereby the valve sleeve 16 lifts against the spring force of the valve spring 17 of the valve seat surface 15, which in turn the fuel flow from the control chamber 7 is made possible via the Kraftstoffablaufweg 10 in the low-pressure chamber 13. From there, the fuel can flow via a return line, not shown, to a reservoir.
  • the pressure within the low-pressure chamber is approximately between 0 and 10 bar, whereas the fuel pressure within the pressure chamber is approximately between 1800 and 2000 bar.
  • valve seat surface 15 of the valve seat 22 is formed flat, wherein the valve seat surface 15 extends transversely to the longitudinal central axis 23 of the valve sleeve 16.
  • the valve sleeve 16 rests against the valve seat surface 15 with a frontal peripheral edge 24 extending in the axial direction when the control valve 12 is closed.
  • the peripheral edge 24 is formed on the inner diameter d1 of the valve sleeve 16.
  • the diameter d2 of the valve sleeve 16 at the peripheral edge 24 corresponds to the diameter d1 of the valve sleeve 16 in the guide section on the guide pin 25. Because the diameter d2 corresponds to the diameter d1, the control valve 12 is according to FIG Fig. 2 pressure balanced in the axial direction. This means that act on the valve sleeve 16 in the axial direction no or minimal pressure forces.
  • At the peripheral edge 24 includes in the radial direction outwardly a conical annular surface 27 at. This includes with the flat valve seat surface 15 in the embodiment shown an angle ⁇ of about 5 °.
  • the injector 1 according to Fig. 1 can also be like in Fig. 3 be formed represented. Also in this embodiment, a flat valve seat surface 15 is provided.
  • a flat valve seat surface 15 is provided.
  • the diameter d2 is slightly larger than the diameter d1, thereby forming a pressure step, annular pressure application surface 28 at the Valve sleeve 16 is formed.
  • This pressure application surface 28 prevents damage or destruction of the injector when exceeding a maximum allowable fuel pressure within the control valve 12.
  • the pressure application surface 28 is dimensioned such that the valve sleeve 16 lifts on reaching an impermissible pressure level, for example, about 2200 bar from the valve seat 22 and thus fuel can flow into the low pressure chamber 13.

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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

The injector i.e. common rail injector (1), has a control valve (12) with a valve casing (16) enclosing a guide bolt (25). A fuel discharge channel (10) from a control chamber (7) is blocked and released by the control valve. The pressure in the chamber is controllable in such a manner that a nozzle needle (3) connected with the chamber is adjustable between an opening position and a closed position. A valve seat (22) is designed as flat seat with an even valve seat surface, and the casing rests on the even seat surface with a front-sided circulating edge when the control valve is closed.

Description

Stand der TechnikState of the art

Die Erfindung betrifft einen Injektor nach dem Oberbegriff des Anspruches 1.The invention relates to an injector according to the preamble of claim 1.

Die EP 1 612 403 A1 beschreibt einen Common-Rail-Injektor mit einem in axialer Richtung druckausgeglichenen Steuerventil zum Sperren und Öffnen eines Kraftstoffablaufweges aus einer Steuerkammer. Mittels des Steuerventils kann der Kraftstoffdruck innerhalb der Steuerkammer beeinflusst werden. Die Steuerkammer wird dabei über einen Druckkanal mit Kraftstoff aus einem mit einem Kraftstoffhochdruckspeicher hydraulisch verbundenen Druckraum versorgt. Durch Variation des Kraftstoffdruckes innerhalb der Steuerkammer wird eine Düsennadel zwischen einer Öffnungsstellung und einer Schließstellung verstellt, wobei die Düsennadel in ihrer Öffnungsstellung den Kraftstofffluss in den Brennraum einer Brennkraftmaschine freigibt. Das Steuerventil weist eine in axialer Richtung mittels eines Elektromagnetantriebes verstellbare Ventilhülse auf, die mit einer ortsfesten, konischen Ventilsitzfläche dichtend zusammenwirkt. Beim Langzeiteinsatz des bekannten Injektors sind Verschleißerscheinungen im Bereich des Ventilsitzes zu beobachten. Durch den Sitzverschleiß bildet sich eine Kreisringfläche am Ventilsitz sowie an der Ventilhülse aus, was dazu führt, dass das Steuerventil nicht mehr druckausgeglichen ist und die Öffnungscharakteristik des Steuerventils über die Lebensdauer des Injektors starken Änderungen unterliegt. Das Öffnungsverhalten des Steuerventils wird im Laufe der Zeit stark druckabhängig, was zu deutlichen Änderungen der Einspritzmengen führt.The EP 1 612 403 A1 describes a common rail injector with a pressure compensated in the axial direction control valve for locking and opening a Kraftstoffablaufweges from a control chamber. By means of the control valve, the fuel pressure can be influenced within the control chamber. The control chamber is supplied via a pressure channel with fuel from a hydraulically connected to a high-pressure fuel pressure chamber. By varying the fuel pressure within the control chamber, a nozzle needle is moved between an open position and a closed position, wherein the nozzle needle in its open position releases the fuel flow into the combustion chamber of an internal combustion engine. The control valve has an adjustable in the axial direction by means of an electromagnetic actuator valve sleeve, which cooperates sealingly with a stationary, conical valve seat surface. In the long-term use of the known injector signs of wear in the region of the valve seat can be observed. Due to the seat wear, an annular surface forms on the valve seat and on the valve sleeve, which results in that the control valve is no longer pressure balanced and the opening characteristic of the control valve is subject to significant changes over the life of the injector. The opening behavior of the control valve is Over time strongly dependent on pressure, which leads to significant changes in injection quantities.

Offenbarung der ErfindungDisclosure of the invention Technische AufgabeTechnical task

Der Erfindung liegt daher die Aufgabe zugrunde, einen Injektor mit einem Steuerventil vorzuschlagen, dessen Öffnungscharakteristik über seine Lebensdauer zumindest im Wesentlichen konstant bleibt.The invention is therefore based on the object to propose an injector with a control valve, the opening characteristic remains at least substantially constant over its lifetime.

Technische LösungTechnical solution

Diese Aufgabe wird mit den Merkmalen des Anspruches 1 gelöst. Vorteilhafte Weiterbildungen der Erfindung sind in den Unteransprüchen angegeben. Zudem fallen in den Rahmen der Erfindung alle Kombinationen aus zumindest zwei der in der Beschreibung, der Zeichnung und/oder den Ansprüchen offenbarten Merkmale.This object is achieved with the features of claim 1. Advantageous developments of the invention are specified in the subclaims. In addition, all combinations of at least two of the features disclosed in the description, the drawings and / or the claims fall within the scope of the invention.

Der Erfindung liegt der Gedanke zugrunde, anstatt eines erhabenen, beispielsweise konischen Ventilsitzes einen als Flachsitz ausgebildeten Ventilsitz mit einer ebenen Ventilsitzfläche vorzusehen, wobei die ebene Ventilsitzfläche dichtend mit einer stirnseitigen Umlaufkante der Ventilhülse des Steuerventils zusammenwirkt. Dabei erstreckt sich die Umlaufkante von der Ventilhülse in axialer Richtung. Bei geschlossenem Steuerventil wird die Ventilhülse mit ihrer stirnseitigen Umlaufkante gegen die ebene Ventilsitzfläche gepresst. Aufgrund der Kombination aus einer ebenen Ventilsitzfläche und der in radialer Richtung schmalen Auflagefläche (Umlaufkante) der Ventilhülse wird trotz eines nicht zu verhindernden Verschleißes sichergestellt, dass an der Ventilhülse keine Druckangriffsfläche für den Kraftstoffdruck in axialer Richtung entsteht, so dass die Öffnungscharakteristik über die Lebensdauer des Steuerventils im Wesentlichen erhalten bleibt. Um ein in axialer Richtung druckausgeglichenes Steuerventil zu erhalten, muss die Umlaufkante, also die Auflagekante, mit der die Ventilhülse auf der ebenen Ventilsitzfläche aufliegt, vom Innenumfang der Ventilhülse gebildet werden. Anders ausgedrückt ist der Durchmesser der Umlaufkante bei einem in axialer Richtung druckausgeglichenem Steuerventil gleich dem Innendurchmesser der Ventilhülse in ihrem Führungsabschnitt am die axialen Druckkräfte aufnehmenden Führungsbolzen.The invention is based on the idea, instead of a raised, for example conical valve seat provided as a flat seat valve seat with a flat valve seat surface, wherein the flat valve seat surface sealingly cooperates with a frontal peripheral edge of the valve sleeve of the control valve. In this case, the peripheral edge extends from the valve sleeve in the axial direction. When the control valve is closed, the valve sleeve is pressed with its frontal peripheral edge against the flat valve seat surface. Due to the combination of a flat valve seat and the narrow in the radial direction bearing surface (peripheral edge) of the valve sleeve is ensured despite an unavoidable wear that no pressure application surface for the fuel pressure in the axial direction of the valve sleeve, so that the opening characteristic over the life of Control valve is essentially maintained. To a pressure-balanced in the axial direction To receive control valve, the peripheral edge, so the bearing edge, with which the valve sleeve rests on the flat valve seat surface, must be formed by the inner circumference of the valve sleeve. In other words, the diameter of the peripheral edge is equal to the inner diameter of the valve sleeve in its guide portion on the axial pressure forces receiving guide pin in a pressure compensated in the axial direction control valve.

Die Auswirkungen des Verschleißes auf die Öffnungscharakteristik des Steuerventils sind minimal, wenn eine sich von der Umlaufkante nach radial außen erstreckende Ringfläche mit der Ventilsitzfläche einen Winkel einschließt.The effects of wear on the opening characteristic of the control valve are minimal when an annular surface extending radially outwardly from the peripheral edge forms an angle with the valve seat surface.

Dieser Winkel muss so bemessen werden, dass erstens der Verschleiß der Ventilhülse und des Ventilsitzes minimal ist und zweitens Strömungskräfte auf die Ventilhülse, die von dem bei geöffnetem Steuerventil in einen die Ventilhülse umgebenden Niederdruckraum strömenden Kraftstoff verursacht werden, minimiert werden. Es hat sich herausgestellt, dass je nachdem, für welche Einspritzdrücke der Injektor ausgelegt wird, Winkel zwischen der Ventilsitzfläche und der Ringfläche in einem Bereich zwischen etwa 0,5° und 20° geeignet sind. Bevorzugt beträgt der Winkel etwa zwischen 1° und 10°; optimale Ergebnisse werden bei einem Winkel von etwa 5° erzielt.This angle must be such that firstly the wear of the valve sleeve and the valve seat is minimal and secondly, flow forces on the valve sleeve, which are caused by the fuel when the control valve is open in a low pressure chamber surrounding the valve sleeve fuel is minimized. It has been found that, depending on the injection pressures for which the injector is designed, angles between the valve seat surface and the annular surface are suitable in a range between approximately 0.5 ° and 20 °. Preferably, the angle is approximately between 1 ° and 10 °; optimum results are achieved at an angle of about 5 °.

Zur Realisierung eines Sicherheitskonzeptes kann in Weiterbildung der Erfindung zu Lasten der axialen Druckausgeglichenheit eine definierte Druckangriffsfläche vorgesehen werden, die sicherstellt, dass bei Überschreiten eines maximalen Kraftstoffdruckes innerhalb der Ventilhülse diese von dem ebenen Ventilsitz abhebt und somit der unter einem unzulässigen Überdruck stehende Kraftstoff in einen Niederdruckraum abfließen kann. Insbesondere ist die Druckangriffsfläche derart bemessen, dass die Ventilhülse bei Kraftstoffdrücken ab 2100 bar, insbesondere ab 2200 bar entgegen der Kraft einer Ventilfeder vom Ventilsitz abhebt.To realize a safety concept, a defined pressure application surface can be provided in development of the invention at the expense of the axial pressure balance, which ensures that when a maximum fuel pressure within the valve sleeve is exceeded, it lifts from the flat valve seat and thus the fuel under an impermissible overpressure into a low-pressure space can drain away. In particular, the pressure application surface is dimensioned such that the valve sleeve lifts at fuel pressures from 2100 bar, in particular from 2200 bar against the force of a valve spring from the valve seat.

In Weiterbildung der Erfindung ist mit Vorteil vorgesehen, dass die Druckangriffsfläche als umlaufende Druckstufe ausgebildet ist. Eine derartige Druckangriffsfläche ist auf einfache Weise mit hoher Genauigkeit herzustellen.In a further development of the invention is advantageously provided that the pressure application surface is designed as a circumferential pressure level. Such a pressure application surface is easy to produce with high accuracy.

Bevorzugt ist die Umlaufkante, mit der die Ventilhülse auf der ebenen Ventilsitzfläche aufliegt, mit radialem Abstand zu der an dem Führungsbolzen geführten Innenfläche der Ventilhülse angeordnet. In einem Bereich zwischen dieser Innenfläche und der Umlaufkante befindet sich die bevorzugt als umlaufende Druckstufe ausgebildete Druckangriffsfläche.Preferably, the peripheral edge, with which the valve sleeve rests on the flat valve seat surface, arranged at a radial distance from the guided on the guide pin inner surface of the valve sleeve. In a region between this inner surface and the peripheral edge is preferably formed as a circumferential pressure step pressure application surface.

Winkelfehler zwischen Ventilhülse und ebenem Ventilsitz werden minimiert, wenn der Führungsbolzen einstückig mit einem den Ventilsitz bildenden bzw. aufweisenden Bauteil ausgebildet ist. Dabei erstreckt sich der Führungsbolzen von einem Bereich radial innerhalb der ebenen Ventilsitzfläche in axialer Richtung in die Ventilhülse hinein.Angular errors between the valve sleeve and flat valve seat are minimized when the guide pin is formed integrally with a valve seat forming or having component. In this case, the guide pin extends from an area radially inside the flat valve seat surface in the axial direction into the valve sleeve.

Winkelfehler zwischen Ventilhülse und Ventilsitzfläche können weiterhin dadurch verringert werden, dass die Ventilhülse in Ausgestaltung der Erfindung einstückig mit einer Ankerplatte des als Elektromagnetantriebs ausgebildeten Aktuators ausgebildet ist.Angular error between the valve sleeve and valve seat surface can be further reduced by the fact that the valve sleeve is formed in an embodiment of the invention in one piece with an anchor plate of the actuator designed as an actuator.

Mit Vorteil verläuft der Kraftstoffablaufweg durch das den Ventilsitz aufweisende Bauteil in axialer Richtung in den Führungsbolzen hinein und von dort in radialer Richtung aus diesem in einen Ringraum innerhalb der Ventilhülse. Von dort aus kann der Kraftstoff bei vom Ventilsitz abgehobener Ventilhülse in radialer Richtung in einen Niederdruckraum strömen.Advantageously, the Kraftstoffablaufweg runs through the valve seat having the component in the axial direction in the guide pin and from there in the radial direction from this into an annular space within the valve sleeve. From there, the fuel can flow in the radial direction in a low-pressure chamber with valve sleeve lifted from the valve seat.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Weitere Vorteile, Merkmale und Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung bevorzugter Ausführungsbeispiele sowie anhand der Zeichnung. Diese zeigt in:

Fig. 1:
eine schematische Schnittdarstellung eines Injektors,
Fig. 2:
eine mögliche Ausgestaltung eines Details aus Fig. 1 und
Fig. 3:
eine alternative Ausgestaltung des Details aus Fig. 1.
Further advantages, features and details of the invention will become apparent from the following description of preferred embodiments and from the drawing. This shows in:
Fig. 1:
a schematic sectional view of an injector,
Fig. 2:
a possible embodiment of a detail Fig. 1 and
3:
an alternative embodiment of the details Fig. 1 ,

Ausführungsformen der ErfindungEmbodiments of the invention

In den Figuren sind gleiche Bauteile und Bauteile mit gleichen Funktionen mit den gleichen Bezugszeichen gekennzeichnet.In the figures, the same components and components with the same functions with the same reference numerals.

In Fig. 1 sind schematisch die für die Steuerung wesentlichen Teile eines Common-Rail-Injektors 1 dargestellt. Innerhalb eines Düsenkörpers 2 ist eine längliche Düsennadel 3 in axialer Richtung beweglich geführt. Die Düsennadel 3 weist an ihrer nicht gezeigten Nadelspitze eine Schließfläche auf, mit welcher sie in dichte Anlage an einem innerhalb des Düsenkörpers 3, ebenfalls nicht gezeigten, Nadelsitz bringbar ist. Wenn die Düsennadel 3 am Nadelsitz anliegt, ist der Kraftstoffaustritt aus einer nicht dargestellten Düsenlochanordnung gesperrt. Ist sie dagegen vom Nadelsitz angehoben, kann Kraftstoff aus einem Druckraum 4 in axialer Richtung entlang der Düsennadel 3 durch die Düsenlochanordnung strömen und dort im Wesentlichen unter dem Hochdruck (Rail-Druck) stehend in einen Brennraum gespritzt werden. Der grundsätzliche Aufbau eines Injektors 1 ist bekannt. Diesbezüglich wird auf die DE 100 24 703 A1 verwiesen.In Fig. 1 are shown schematically the essential parts for the control of a common rail injector 1. Within a nozzle body 2, an elongated nozzle needle 3 is movably guided in the axial direction. The nozzle needle 3 has at its needle tip, not shown, a closing surface with which it can be brought into tight contact with a needle body within the nozzle body 3, also not shown. When the nozzle needle 3 rests against the needle seat, the fuel outlet is blocked from a nozzle hole arrangement, not shown. If, on the other hand, it is raised from the needle seat, fuel can flow from a pressure chamber 4 in the axial direction along the nozzle needle 3 through the nozzle hole arrangement and be sprayed into a combustion chamber substantially under high pressure (rail pressure). The basic structure of an injector 1 is known. In this regard is on the DE 100 24 703 A1 directed.

Der Injektor 1 weist eine Drosselplatte 5 auf, die sich hülsenförmig in der Zeichnungsebene nach unten in den Düsenkörper 2 hinein erstreckt. Von dem hülsenförmigen Abschnitt der Drosselplatte 5 und von der Stirnseite 6 der Düsennadel 3 wird eine Steuerkammer 7 begrenzt. Die Steuerkammer 7 ist über einen Druckkanal 8 mit Zulaufdrossel 9 mit dem Druckraum 4 verbunden, welcher wiederum über eine nicht dargestellte Versorgungsleitung mit einem Kraftstoff-Hochdruckspeicher verbunden ist. Über den Druckkanal 8 kann somit unter Hochdruck stehender Kraftstoff in die Steuerkammer 7 fließen. Aus der Steuerkammer 7 heraus führt in axialer Richtung ein Kraftstoffablaufweg 10 mit Ablaufdrossel 11. Über den Kraftstoffablaufweg 10 kann Kraftstoff aus der Steuerkammer 7 bei geöffnetem Steuerventil 12 in einen Niederdruckraum 13 strömen. Die Durchflussquerschnitte der Zulaufdrossel 9 und der Ablaufdrossel 11 sind dabei so aufeinander abgestimmt, dass der Zufluss durch den Druckkanal 8 schwächer als der Abfluss durch den Kraftstoffablaufweg 10 ist und demnach bei geöffnetem Steuerventil 12 ein Nettoabfluss von Kraftstoff aus der Steuerkammer 7 resultiert. Der daraus resultierende Druckabfall in der Steuerkammer 7 bewirkt, dass der Betrag der Schließkraft unter den Betrag der Öffnungskraft sinkt und die Düsennadel 3 von ihrem Nadelsitz abhebt.The injector 1 has a throttle plate 5, which extends sleeve-shaped in the plane of the drawing down into the nozzle body 2 inside. Of the sleeve-shaped portion of the throttle plate 5 and the end face 6 of the nozzle needle 3, a control chamber 7 is limited. The control chamber 7 is connected via a pressure channel 8 with inlet throttle 9 to the pressure chamber 4, which in turn is connected via a supply line, not shown, with a high-pressure fuel storage. High-pressure fuel can thus flow into the control chamber 7 via the pressure channel 8. From the control chamber 7 leads out in the axial direction of a fuel drain 10 with outlet throttle 11. About the fuel drain 10, fuel from the control chamber 7 with open control valve 12 can flow into a low-pressure chamber 13. The flow cross-sections of the inlet throttle 9 and the outlet throttle 11 are coordinated so that the inflow through the pressure channel 8 is weaker than the outflow through the fuel drain 10 and thus with open control valve 12, a net outflow of fuel from the control chamber 7 results. The resulting pressure drop in the control chamber 7 causes the amount of closing force falls below the amount of the opening force and lifts the nozzle needle 3 from its needle seat.

Der Kraftstoffablaufweg 10 führt durch die Drosselplatte 5 mit Ablaufdrossel 11 in ein in der Zeichnungsebene darüber angeordnetes Bauteil 14. Das Bauteil 14 weist einen Ventilsitz 22 (Flachsitz) mit einer ebenen Ventilsitzfläche 15 des Steuerventils 12 auf, wobei eine Ventilhülse 16 des Steuerventils 12 bei geschlossenem Steuerventil dichtend auf der Ventilsitzfläche 15 aufliegt. Hierzu ist die Ventilhülse 16 von einer Ventilfeder 17 in axialer Richtung auf die Ventilsitzfläche 15 federkraftbeaufschlagt. Die Ventilfeder 17 stützt sich in der Zeichnungsebene oben an einem Injektorkörper 18 und am entgegengesetzten Ende an einem Federführungsteil 19 ab, welches wiederum auf der Ventilhülse 16 aufliegt. Die Ventilhülse 15 ist in axialer Richtung von einem Führungsbolzen 25 durchsetzt, an dessen Außenfläche sie geführt ist. Der Führungsbolzen 25 ist dabei einstückig mit einem zylinderförmigen Abschnitt des Bauteils 14 ausgebildet.The fuel drainage path 10 leads through the throttle plate 5 with outlet throttle 11 in a plane arranged in the drawing plane component 14. The component 14 has a valve seat 22 (flat seat) with a flat valve seat surface 15 of the control valve 12, wherein a valve sleeve 16 of the control valve 12 in the closed Control valve sealingly rests on the valve seat surface 15. For this purpose, the valve sleeve 16 is spring-loaded by a valve spring 17 in the axial direction on the valve seat surface 15. The valve spring 17 is supported in the plane of the drawing on top of an injector body 18 and at the opposite end on a spring guide part 19, which in turn rests on the valve sleeve 16. The valve sleeve 15 is penetrated in the axial direction by a guide pin 25, on whose outer surface it is guided. The guide pin 25 is formed integrally with a cylindrical portion of the component 14.

Die Ventilfeder 17 ist innerhalb eines Elektromagneten 20 angeordnet. Bei Bestromung des Elektromagneten 20 wird eine einstückig mit der Ventilhülse 16 ausgebildete Ankerplatte 21 axial in Richtung Elektromagnet 20 bewegt, wodurch die Ventilhülse 16 entgegen der Federkraft der Ventilfeder 17 von der Ventilsitzfläche 15 abhebt, wodurch wiederum der Kraftstofffluss aus der Steuerkammer 7 über den Kraftstoffablaufweg 10 in den Niederdruckraum 13 ermöglicht wird. Von dort aus kann der Kraftstoff über eine nicht gezeigte Rücklaufleitung zu einem Vorratsbehälter abfließen. Der Druck innerhalb des Niederdruckraumes beträgt je nach Betriebszustand etwa zwischen 0 und 10 bar, wohingegen der Kraftstoffdruck innerhalb des Druckraumes etwa zwischen 1800 und 2000 bar beträgt.The valve spring 17 is disposed within an electromagnet 20. When current is supplied to the electromagnet 20, an armature plate 21 formed integrally with the valve sleeve 16 is moved axially in the direction of the electromagnet 20, whereby the valve sleeve 16 lifts against the spring force of the valve spring 17 of the valve seat surface 15, which in turn the fuel flow from the control chamber 7 is made possible via the Kraftstoffablaufweg 10 in the low-pressure chamber 13. From there, the fuel can flow via a return line, not shown, to a reservoir. Depending on the operating state, the pressure within the low-pressure chamber is approximately between 0 and 10 bar, whereas the fuel pressure within the pressure chamber is approximately between 1800 and 2000 bar.

Wie aus Fig. 2 ersichtlich ist die Ventilsitzfläche 15 des Ventilsitzes 22 eben ausgeformt, wobei sich die Ventilsitzfläche 15 quer zur Längsmittelachse 23 der Ventilhülse 16 erstreckt. Die Ventilhülse 16 liegt mit einer sich in axialer Richtung erstreckenden, stirnseitigen Umlaufkante 24 bei geschlossenem Steuerventil 12 an der Ventilsitzfläche 15 an. Die Umlaufkante 24 ist dabei am Innendurchmesser d1 der Ventilhülse 16 ausgebildet. Anders ausgedrückt, entspricht der Durchmesser d2 der Ventilhülse 16 an der Umlaufkante 24 dem Durchmesser d1 der Ventilhülse 16 im Führungsabschnitt am Führungsbolzen 25. Dadurch, dass der Durchmesser d2 dem Durchmesser d1 entspricht, ist das Steuerventil 12 gemäß Fig. 2 in axialer Richtung druckausgeglichen. Dies bedeutet, dass auf die Ventilhülse 16 in axialer Richtung keine oder nur minimale Druckkräfte wirken.How out Fig. 2 it can be seen that the valve seat surface 15 of the valve seat 22 is formed flat, wherein the valve seat surface 15 extends transversely to the longitudinal central axis 23 of the valve sleeve 16. The valve sleeve 16 rests against the valve seat surface 15 with a frontal peripheral edge 24 extending in the axial direction when the control valve 12 is closed. The peripheral edge 24 is formed on the inner diameter d1 of the valve sleeve 16. In other words, the diameter d2 of the valve sleeve 16 at the peripheral edge 24 corresponds to the diameter d1 of the valve sleeve 16 in the guide section on the guide pin 25. Because the diameter d2 corresponds to the diameter d1, the control valve 12 is according to FIG Fig. 2 pressure balanced in the axial direction. This means that act on the valve sleeve 16 in the axial direction no or minimal pressure forces.

An die Umlaufkante 24 schließt in radialer Richtung nach außen eine konische Ringfläche 27 an. Diese schließt mit der ebenen ventilsitzfläche 15 im gezeigten Ausführungsbeispiel einen Winkel α von etwa 5° ein.At the peripheral edge 24 includes in the radial direction outwardly a conical annular surface 27 at. This includes with the flat valve seat surface 15 in the embodiment shown an angle α of about 5 °.

Ferner ist aus Fig. 2 zu erkennen, dass der Kraftstoffablaufweg von einem axialen Abschnitt in einen radialen Abschnitt übergeht, welcher in einem Ringraum 26 mündet, der einerseits von dem Führungsbolzen 25 und andererseits von der Ventilhülse 16 begrenzt wird.Furthermore, it is off Fig. 2 to recognize that the Kraftstoffablaufweg merges from an axial portion in a radial portion which opens into an annular space 26 which is bounded on the one hand by the guide pin 25 and the other part of the valve sleeve 16.

Der Injektor 1 gemäß Fig. 1 kann auch wie in Fig. 3 dargestellt ausgebildet werden. Auch bei dieser Ausführungsvariante ist eine ebene Ventilsitzfläche 15 vorgesehen. Im Unterschied zu dem Ausführungsbeispiel gemäß Fig. 2 entspricht der Durchmesser d2 der Ventilhülse 16 im Bereich der Umlaufkante 24 nicht dem Durchmesser d1 der Ventilhülse 16 im Führungsbereich unmittelbar radial außerhalb des Führungsbolzens 25. Der Durchmesser d2 ist geringfügig größer als der Durchmesser d1, wodurch eine als Druckstufe ausgebildete, ringförmige Druckangriffsfläche 28 an der Ventilhülse 16 gebildet ist. Diese Druckangriffsfläche 28 verhindert eine Beschädigung oder Zerstörung des Injektors bei einer Überschreitung eines maximal zulässigen Kraftstoffdruckes innerhalb des Steuerventils 12. Die Druckangriffsfläche 28 ist derart bemessen, dass die Ventilhülse 16 bei Erreichen eines unzulässigen Druckniveaus von beispielsweise etwa 2200 bar vom Ventilsitz 22 abhebt und damit Kraftstoff in den Niederdruckraum 13 abströmen kann.The injector 1 according to Fig. 1 can also be like in Fig. 3 be formed represented. Also in this embodiment, a flat valve seat surface 15 is provided. In contrast to the embodiment according to Fig. 2 corresponds to the diameter d2 of the valve sleeve 16 in the region of the peripheral edge 24 is not the diameter d1 of the valve sleeve 16 in the guide area immediately radially outside of the guide pin 25. The diameter d2 is slightly larger than the diameter d1, thereby forming a pressure step, annular pressure application surface 28 at the Valve sleeve 16 is formed. This pressure application surface 28 prevents damage or destruction of the injector when exceeding a maximum allowable fuel pressure within the control valve 12. The pressure application surface 28 is dimensioned such that the valve sleeve 16 lifts on reaching an impermissible pressure level, for example, about 2200 bar from the valve seat 22 and thus fuel can flow into the low pressure chamber 13.

In gleicher Weise wie bei dem Ausführungsbeispiel gemäß Fig. 2 schließt auch bei dem Ausführungsbeispiel gemäß Fig. 3 eine radial äußere Ringfläche 27 an die Umlaufkante 24 an, die mit der ebenen Ventilsitzfläche 15 bzw. ihrer gedachten Verlängerung einen Winkel α von etwa 5° einschließt.In the same manner as in the embodiment according to Fig. 2 also includes in the embodiment according to Fig. 3 a radially outer annular surface 27 to the peripheral edge 24, which forms an angle α of about 5 ° with the flat valve seat surface 15 and its imaginary extension.

Claims (10)

  1. Injector for injecting fuel into combustion chambers of internal combustion engines, in particular common rail injector, having a valve sleeve (16), which surrounds a guide pin (25), of a control valve (12), which valve sleeve (16) is arranged so as to be axially movable relative to a valve seat (22), with it being possible by means of the control valve (12) for a fuel outflow path (10) out of a control chamber (7) which is hydraulically connected to a pressure duct (8) which serves for supplying fuel to be shut off and opened up, whereby the pressure in the control chamber (7) can be controlled such that a nozzle needle (3) which is operatively connected to the control chamber (7) can be adjusted between an open position, in which the flow of fuel is enabled, and a closed position, characterized in that the valve seat (22) is designed as a flat seat with a planar valve seat surface (15), and in that the valve sleeve (16) rests with an end-side encircling edge (24) on the planar valve seat surface (15) when the control valve (12) is closed.
  2. Injector according to Claim 1, characterized in that an annular surface (27) which extends radially outwards from the encircling edge (24) encloses an angle (α) with the valve seat surface (22).
  3. Injector according to Claim 2, characterized in that the angle (α) is approximately between 0.5° and 20°, preferably approximately between 1° and 10°, preferably approximately 5°.
  4. Injector according to one of the preceding claims, characterized in that the valve sleeve (16) has provided on it a pressure engagement surface (28) for fuel pressure in the opening direction of the valve sleeve (16).
  5. Injector according to Claim 4, characterized in that the pressure engagement surface (28) is formed as an encircling pressure stage which extends in the radial direction.
  6. Injector according to one of Claims 4 or 5, characterized in that the pressure engagement surface (28) is dimensioned such that the valve sleeve (16) lifts from the valve seat (22) at fuel pressures above 2100 bar, in particular above 2200 bar.
  7. Injector according to one of Claims 2 to 5, characterized in that the encircling edge (24) is arranged with a radial spacing to the inner surface, which is guided on the guide pin, of the valve sleeve (16).
  8. Injector according to one of Claims 1 to 7, characterized in that the guide pin (25) is formed in one piece with a component (14) which has the valve seat (22), and said guide pin (25) extends in the axial direction from a region radially within the valve seat surface (15).
  9. Injector according to one of Claims 1 to 8, characterized in that the valve sleeve (16) is formed in one piece with an armature plate (21) of an actuator which is designed as an electromagnetic drive and which moves the valve sleeve (16).
  10. Injector according to one of Claims 1 to 9, characterized in that the fuel outflow path (10) runs axially into the guide pin (25) and in the radial direction out of the latter into an annular space (26) which is delimited by the valve sleeve (16) when the control valve (12) is closed.
EP07820155A 2006-10-23 2007-09-12 Injector for injecting fuel into combustion chambers of internal combustion engines Not-in-force EP2082127B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006049885A DE102006049885A1 (en) 2006-10-23 2006-10-23 Fuel injector i.e. common rail injector, for internal-combustion engine, has valve seat designed as flat seat with even valve seat surface, and casing resting on seat surface with front-sided circulating edge when control valve is closed
PCT/EP2007/059593 WO2008049691A1 (en) 2006-10-23 2007-09-12 Injector for injecting fuel into combustion chambers of internal combustion engines

Publications (2)

Publication Number Publication Date
EP2082127A1 EP2082127A1 (en) 2009-07-29
EP2082127B1 true EP2082127B1 (en) 2010-11-24

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP07820155A Not-in-force EP2082127B1 (en) 2006-10-23 2007-09-12 Injector for injecting fuel into combustion chambers of internal combustion engines

Country Status (6)

Country Link
US (1) US8573186B2 (en)
EP (1) EP2082127B1 (en)
CN (1) CN101529080B (en)
AT (1) ATE489550T1 (en)
DE (2) DE102006049885A1 (en)
WO (1) WO2008049691A1 (en)

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US9464613B2 (en) 2008-06-27 2016-10-11 C.R.F. Societa Consortile Per Azioni Fuel injector equipped with a metering servovalve for an internal combustion engine
EP2138708B1 (en) * 2008-06-27 2010-11-03 C.R.F. Società Consortile per Azioni Fuel injector equipped with a metering servovalve for an internal combustion engine
EP2674608B1 (en) * 2012-06-13 2015-08-12 Delphi International Operations Luxembourg S.à r.l. Fuel injector
CN104314722A (en) * 2014-10-17 2015-01-28 中国重汽集团重庆燃油喷射系统有限公司 Pressure balance electrically-controlled injector
DE102014225323A1 (en) * 2014-12-09 2016-06-09 Robert Bosch Gmbh Shift or pressure control valve for a fuel injection system
US10077748B2 (en) 2014-12-23 2018-09-18 Cummins Inc. Fuel injector for common rail
DE102015203515A1 (en) * 2015-02-27 2016-09-01 Robert Bosch Gmbh Partial pressure compensated pressure control valve for a high-pressure accumulator

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WO1999034111A1 (en) * 1997-12-23 1999-07-08 Siemens Aktiengesellschaft Injection valve with control valve
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ATE353118T1 (en) * 2000-07-18 2007-02-15 Delphi Tech Inc FUEL INJECTION VALVE
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ES2277230T3 (en) * 2004-06-30 2007-07-01 C.R.F. Societa Consortile Per Azioni FUEL INJECTOR FOR INTERNAL COMBUSTION ENGINE.
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Also Published As

Publication number Publication date
US20100294240A1 (en) 2010-11-25
US8573186B2 (en) 2013-11-05
ATE489550T1 (en) 2010-12-15
EP2082127A1 (en) 2009-07-29
DE502007005792D1 (en) 2011-01-05
WO2008049691A1 (en) 2008-05-02
DE102006049885A1 (en) 2008-04-24
CN101529080B (en) 2011-08-03
CN101529080A (en) 2009-09-09

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