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EP2171258A1 - Control valve for a fuel injection valve - Google Patents

Control valve for a fuel injection valve

Info

Publication number
EP2171258A1
EP2171258A1 EP08760855A EP08760855A EP2171258A1 EP 2171258 A1 EP2171258 A1 EP 2171258A1 EP 08760855 A EP08760855 A EP 08760855A EP 08760855 A EP08760855 A EP 08760855A EP 2171258 A1 EP2171258 A1 EP 2171258A1
Authority
EP
European Patent Office
Prior art keywords
control
valve
valve body
recess
pressure
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.)
Granted
Application number
EP08760855A
Other languages
German (de)
French (fr)
Other versions
EP2171258B1 (en
Inventor
Nadja Eisenmenger
Hans-Christoph Magel
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2171258A1 publication Critical patent/EP2171258A1/en
Application granted granted Critical
Publication of EP2171258B1 publication Critical patent/EP2171258B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • 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
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • 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
    • F02M63/0077—Valve seat details
    • 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

Definitions

  • the invention relates to a control valve for a fuel injector, which can be used for the injection of fuel under high pressure in the combustion chamber of an internal combustion engine.
  • a fuel injector is known from the prior art, for example, as it can be used for the injection of fuel into the combustion chamber, preferably by high-speed, self-igniting internal combustion engines.
  • the fuel injector is supplied with fuel under high pressure by means of a high-pressure pump and has a valve needle which alternately releases or closes one or more injection openings as a result of its longitudinal movement.
  • the fuel can be injected into the combustion chamber at a precisely determined time of the power stroke of the internal combustion engine, which takes place at very high pressure in order to achieve good atomization of the fuel.
  • the movement of the valve needle is achieved on the one hand by the hydraulic pressure of the fuel, which acts on the valve needle in the opening direction.
  • the opposite is a closing force, which is generated by the fuel pressure in a control room.
  • the fuel pressure in the control chamber is adjusted via a control valve.
  • the control valve known from DE 10 2006 021 741 A1 has a control sleeve, which is connected to a magnet armature and by the energizing or Non-energizing the electromagnet is moved in its longitudinal direction.
  • the control sleeve is seated on a valve seat which limits a pressure chamber connected to the control chamber radially outward, wherein when the control sleeve lifts from the valve seat, the pressure chamber and thus the control chamber is connected to a leakage oil chamber, while sitting on the control sleeve on the Valve seat of the pressure chamber and thus the control room is separated from the leakage oil space.
  • the control sleeve has on its end facing the valve seat on a sealing surface, which is formed substantially annularly circular. It can also be provided that a slightly conical shape of the sealing surface is provided in order to obtain a line contact. This increases the sealing effect, so that even with a relatively small spring force with which the valve sleeve is pressed onto the valve seat, a good seal is achieved.
  • the injection pressure with which the fuel is introduced into the injector by the high-pressure pump is up to 1800 bar in modern high-pressure injection systems, such as those used for self-igniting high-speed internal combustion engines, and will continue to increase in the future.
  • This high fuel pressure is also in the control chamber and thus in the pressure chamber and there leads to the control sleeve is radially expanded. Since the pressure drops when the control valve is open and rises again when the control valve is closed, this occurs
  • the control valve according to the invention for a fuel injector has the advantage that the wear in the region of the valve seat is markedly reduced compared to the known valve, so that a reliable function over the entire service life of the control valve is ensured.
  • a recess is formed on the side of the valve body, on which the valve seat is located, which is in hydraulic communication with the pressure chamber. Varying pressure in the pressure chamber, so on the one hand, the control sleeve, but also the recess in the valve body is radially expanded, wherein the recess is such that the relative movement of the valve seat and the sealing surface is at least approximately equal, which significantly reduces wear in this area ,
  • the control sleeve is guided on a guide pin, which protrudes from the side facing away from the valve body side of the guide sleeve into the guide sleeve.
  • the guide sleeve is guided independently of the valve body, so that an accurate alignment of the valve sleeve on the valve seat is possible.
  • the guide pin has an extension which projects into the recess of the valve body. As a result, the volume of the pressure chamber can be reduced, which increases the dynamics of the control valve, since the pressure changes in the pressure chamber and thus in the control room can be made faster. In this case, the function of the recess in the valve body is maintained.
  • valve seat is conical, thus has the shape of a truncated cone, wherein the valve seat is formed around the recess around.
  • the inner diameter of the guide sleeve and the diameter of the recess have the same diameter on.
  • control valve in a fuel injector for internal combustion engines, in which the fuel pressure is adjusted in a control chamber by the control valve. Due to the changing pressure in the control chamber, a valve needle can be moved in its longitudinal direction, which controls the fuel injection of the fuel injector into a combustion chamber of the internal combustion engine.
  • FIG. 2 is an enlarged view of the control valve in the region of the valve seat or the sealing surface
  • FIG. 3 shows another embodiment of the control valve, wherein the same
  • FIG. 5 shows a fourth exemplary embodiment in which the guide pin projects far into the valve body.
  • Description of the embodiments 1 shows a longitudinal section through a fuel injector, in which a control valve according to the invention is used.
  • the fuel injector has a housing 1, in which a control valve 3 is formed, which controls the movement of a valve needle 10.
  • the valve needle 10 is in this case in the form of a piston and, with its end facing away from the control valve 3, controls an injection opening through which fuel can be injected into a combustion chamber of an internal combustion engine.
  • the valve needle 10 is guided in this case in a valve body 5, which is arranged in the housing 1 and which has a bore 12 in which the valve needle 10 is guided.
  • a control chamber 7 is limited, the fuel pressure acts on the control valve side facing the valve needle 10 and so generates a closing force on the valve needle 10.
  • the control chamber 7 is always supplied with fuel under high pressure. This is done via an annular space 14 which surrounds the valve body 5 and which is connected via a bore, not shown in the drawing, to a fuel port, via which fuel compressed by a high-pressure pump is supplied.
  • the annular space 14 is connected through a throttle bore 15 with the control chamber 7, so that with a certain time delay always the same fuel pressure, both in the control chamber 7, as well as in the annular space 14 prevails.
  • the annular space 14 is sealed off via a seal 17 with respect to the low-pressure region of the fuel injector.
  • the pressure in the control chamber 7 is regulated by the control valve 3.
  • the valve body 5 has a flow channel 20, which runs centrally and coaxially with the valve needle 10.
  • a throttle 22 is formed, so that the amount of the outflowing fuel can flow only throttled through the drain passage 20.
  • the outlet channel 20 opens into a recess 24, which is part of a pressure chamber 26, wherein the pressure chamber 26 is limited by a control sleeve 25, a guide pin 30 and through the recess 24 of the valve body 5.
  • the control sleeve 25 is slidably guided on the guide pin 30 and connected to a magnet armature 34, which can be moved by an electromagnet 35.
  • a closing spring 32 is supported between the control sleeve 25 and an annular disc 29, which is firmly connected to the guide pin.
  • the electromagnet 35 is energized and the control sleeve 35 pulled by the armature 34 upwards, d. H. away from the valve seat 28.
  • the pressure chamber 26 is connected to the leakage oil chamber 38, which is depressurized, since it is connected via a drain 40 with a low pressure system.
  • the pressure in the pressure chamber 26 and in the control chamber 7 decreases then and the closing force on the valve needle 10 decreases so far that the valve needle 10 moves in the direction of the control chamber 7 and thereby releases injection ports through which fuel is now injected, for example, into a combustion chamber.
  • a sealing surface 27 is formed, which is formed substantially annularly circular and which rests on a valve body 5 formed on the flat valve seat 28.
  • the control sleeve 25 is pressed with sufficient surface pressure against the valve seat 28, so that the pressure chamber 26 is sealed against the pressureless leakage oil chamber 38.
  • the valve body 5 has in the region of the valve seat 28 through the recess 24 has a substantially hollow cylindrical shape.
  • the recess 24 is dimensioned such that due to the pressure in the pressure chamber 26, a widening of the valve body 5 in the region of the recess 24 takes place radially outward, just as the control sleeve 25 is radially widened by the pressure in the pressure chamber 26.
  • FIG. 3 shows a further exemplary embodiment of the control valve 3 according to the invention.
  • the valve seat 28 ' is conical here, and accordingly, the sealing surface 27' also has a conical shape.
  • the sleeve is always centered relative to the valve seat 28' so that the outflow of the fuel from the pressure chamber 26 occurs symmetrically during the opening movement of the control sleeve 25.
  • Figure 4 shows another embodiment, in which case an extension 31 is formed here on the guide pin 30 ', which projects into the recess 24.
  • the volume of the pressure chamber 26 can be decisively reduced, which considerably shortens the response time of the control valve 3. The lower the volume in the
  • valve seat 28 ' is also conical in this case, however, the conical angle compared to the embodiment of FIG. 3 is significantly increased. By this cone angle ⁇ , the wear between the sealing surface 27 'and the valve seat 28' can be further reduced: In the embodiment of FIG. 3, the sealing surface 27 'slides easily when placed on the conical valve seat 28' to the outside. At the same time, the valve seat 28 'is pressed inwards by the control sleeve 25, so that it turns into a valve for each closing movement of the control sleeve 25
  • valve seat 28 'and sealing surface 27' Relative movement between valve seat 28 'and sealing surface 27' comes. If the valve seat 28 ', however, formed as a cone with a large opening angle, this sliding can be prevented when placing the control sleeve, at the same time the relative movement of the valve seat 28' and sealing surface 27 'is suppressed by the fluctuating pressure in the pressure chamber 26.
  • cone angle ⁇ for the valve seat 28 ' so as the opening angle of the corresponding cone, a value of 155 ° to 175 ° has proven to be particularly advantageous, in particular an angle of about 160 °.
  • the sealing surface (27 ') has at least approximately the same cone angle as the valve seat 28'.
  • FIG. 5 shows a further exemplary embodiment of the control valve.
  • a bore is provided here, which extends through the entire valve body 5 and extends into the control chamber 7, the diameter of the bore 12 'corresponding to the inner diameter of the control sleeve 25.
  • the guide pin is provided here, which extends through the entire valve body 5 and extends into the control chamber 7, the diameter of the bore 12 'corresponding to the inner diameter of the control sleeve 25.
  • valve body 5 is designed such that on the one hand it guides the control sleeve 25 and on the other hand projects far into the valve body 5.
  • 5 bevels 33 are formed in the region of the valve body so that a hydraulic connection of the pressure chamber 26 'to the control chamber 7 is ensured is. Since the valve body 5 "in the region of the valve seat 28" exactly the same shape, namely a hollow cylindrical shape as the control sleeve 25, resulting in identical elastic properties, so that a relative movement between the valve seat 28 and sealing surface 27 "by the changing pressure in the pressure chamber 26th 'is excluded.

Landscapes

  • 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 invention relates to a control for a fuel injector having a control sleeve (25) delimiting a pressure chamber (26; 26') and movably supported in the longitudinal direction thereof. The control sleeve (25) has a sealing surface (27; 27'; 27'') on the front side thereof, said surface working together with a valve seat (28; 28'; 28'') configured on a valve body (5). In the valve body (5), a recess (24; 24') is designed in the side of the valve body (5) facing the pressure chamber (26; 26'), the control sleeve (25) and the recess (24; 24') in the valve body (5) being configured such that the deformation of the control sleeve (25) and valve body (5) as a result of the pressure in the pressure chamber (26; 26') causes no or only very little movement between the valve seat (28; 28'; 28'') and the sealing surface (27; 27'; 27'') of the control sleeve (25).

Description

Beschreibung description
Titeltitle
Steuerventil für ein KraftstoffeinspritzventilControl valve for a fuel injection valve
Die Erfindung betrifft ein Steuerventil für einen Kraftstoffinjektor, der zur Einspritzung von Kraftstoff unter hohem Druck in den Brennraum einer Brennkraftmaschine verwendet werden kann.The invention relates to a control valve for a fuel injector, which can be used for the injection of fuel under high pressure in the combustion chamber of an internal combustion engine.
Stand der TechnikState of the art
Aus dem Stand der Technik ist beispielsweise aus der DE 10 2006 021 741 Al ein Kraftstoffinjektor bekannt, wie er zur Einspritzung von Kraftstoff in den Brennraum vorzugsweise von schnelllaufenden, selbstzündenden Brennkraftmaschinen verwendet werden kann. Der Kraftstoffinjektor wird mit Kraftstoff unter ho- hem Druck mittels einer Hochdruckpumpe versorgt und weist eine Ventilnadel auf, die durch ihre Längsbewegung eine oder mehrere Einspritzöffnungen abwechselnd freigibt oder verschließt. Hierdurch kann der Kraftstoff zu einem genau bestimmten Zeitpunkt des Arbeitstaktes der Brennkraftmaschine in den Brennraum eingespritzt werden, was mit sehr hohem Druck geschieht, um eine gute Zerstäubung des Kraftstoffs zu erreichen. Die Bewegung der Ventilnadel wird einerseits durch den hydraulischen Druck des Kraftstoffs erreicht, der die Ventilnadel in Öffnungsrichtung beaufschlagt. Dem entgegengerichtet ist eine Schließkraft, die durch den Kraftstoffdruck in einem Steuerraum erzeugt wird. Durch wechselnden Kraftstoffdruck im Steuerraum lässt sich die Richtung der re- sultierenden Kraft auf die Ventilnadel ändern, so dass die Ventilnadel entweder in ihre Öffnungs- oder in ihre Schließstellung fährt.From DE 10 2006 021 741 A1, a fuel injector is known from the prior art, for example, as it can be used for the injection of fuel into the combustion chamber, preferably by high-speed, self-igniting internal combustion engines. The fuel injector is supplied with fuel under high pressure by means of a high-pressure pump and has a valve needle which alternately releases or closes one or more injection openings as a result of its longitudinal movement. As a result, the fuel can be injected into the combustion chamber at a precisely determined time of the power stroke of the internal combustion engine, which takes place at very high pressure in order to achieve good atomization of the fuel. The movement of the valve needle is achieved on the one hand by the hydraulic pressure of the fuel, which acts on the valve needle in the opening direction. The opposite is a closing force, which is generated by the fuel pressure in a control room. By changing the fuel pressure in the control chamber, the direction of the resulting force on the valve needle can be changed, so that the valve needle moves either in its opening or in its closed position.
Der Kraftstoffdruck im Steuerraum wird über ein Steuerventil eingestellt. Das aus der DE 10 2006 021 741 Al bekannte Steuerventil weist hierzu eine Steuerhülse auf, die mit einem Magnetanker verbunden ist und durch das Bestromen oder Nicht-Bestromen des Elektromagneten in ihrer Längsrichtung bewegt wird. Hierbei sitzt die Steuerhülse auf einem Ventilsitz auf, der einen mit dem Steuerraum verbundenen Druckraum radial nach außen begrenzt, wobei dann, wenn die Steuerhülse vom Ventilsitz abhebt, der Druckraum und damit der Steuerraum mit einem Leckölraum verbunden wird, während beim Aufsitzen der Steuerhülse auf dem Ventilsitz der Druckraum und damit auch der Steuerraum vom Leckölraum getrennt wird. Durch eine Verbindung des Steuerraums mit dem Kraftstoffhochdruck, mit dem der Injektor versorgt wird, kann so durch Betätigen des Steuerventils der Kraftstoffdruck im Steuerraum angehoben oder abgesenkt werden, was die die Ventilnadel bewegende Kraft erzeugt.The fuel pressure in the control chamber is adjusted via a control valve. For this purpose, the control valve known from DE 10 2006 021 741 A1 has a control sleeve, which is connected to a magnet armature and by the energizing or Non-energizing the electromagnet is moved in its longitudinal direction. In this case, the control sleeve is seated on a valve seat which limits a pressure chamber connected to the control chamber radially outward, wherein when the control sleeve lifts from the valve seat, the pressure chamber and thus the control chamber is connected to a leakage oil chamber, while sitting on the control sleeve on the Valve seat of the pressure chamber and thus the control room is separated from the leakage oil space. By connecting the control chamber with the high-pressure fuel, with which the injector is supplied, so can be raised or lowered by operating the control valve, the fuel pressure in the control chamber, which generates the valve needle moving force.
Die Steuerhülse weist an ihrer dem Ventilsitz zugewandten Stirnseite eine Dichtfläche auf, die im Wesentlichen ringkreisförmig ausgebildet ist. Es kann auch vorgesehen sein, dass eine leicht konische Form der Dichtfläche vorgesehen ist, um eine Linienberührung zu erhalten. Dies erhöht die Dichtwirkung, so dass auch mit einer relativ geringen Federkraft, mit der die Ventilhülse auf den Ventilsitz gedrückt wird, eine gute Abdichtung erreicht wird.The control sleeve has on its end facing the valve seat on a sealing surface, which is formed substantially annularly circular. It can also be provided that a slightly conical shape of the sealing surface is provided in order to obtain a line contact. This increases the sealing effect, so that even with a relatively small spring force with which the valve sleeve is pressed onto the valve seat, a good seal is achieved.
Der Einspritzdruck, mit dem der Kraftstoff durch die Hochdruckpumpe in den In- jektor eingeleitet wird, beträgt bei modernen Hochdruckeinspritzsystemen, wie sie für selbstzündende, schnelllaufende Brennkraftmaschinen verwendet werden, bis zu 1800 bar und wird in Zukunft weiter steigen. Dieser hohe Kraftstoffdruck liegt auch im Steuerraum und damit im Druckraum an und führt dort dazu, dass die Steuerhülse radial aufgeweitet wird. Da der Druck bei geöffnetem Steuerven- til absinkt und bei geschlossenem Steuerventil erneut ansteigt, kommt es zuThe injection pressure with which the fuel is introduced into the injector by the high-pressure pump is up to 1800 bar in modern high-pressure injection systems, such as those used for self-igniting high-speed internal combustion engines, and will continue to increase in the future. This high fuel pressure is also in the control chamber and thus in the pressure chamber and there leads to the control sleeve is radially expanded. Since the pressure drops when the control valve is open and rises again when the control valve is closed, this occurs
Druckschwankungen im Druckraum und damit zu einer Relativbewegung der Dichtfläche auf den Ventilsitz. Dies führt an dieser Stelle zu Verschleiß, insbesondere wenn eine linienförmige Auflagefläche an der Dichtfläche auf dem Ventilsitz vorgesehen ist, so dass die Dichtfläche, die effektiv auf dem Ventilsitz auf- liegt, immer größer wird. Überschreitet diese Dichtfläche einen gewissen Wert, reicht die Flächenpressung nicht mehr aus, um das Steuerventil abzudichten, und es kommt zu Leckverlusten aus dem Druckraum und damit auch zu einem kontinuierlichen Abfluss von Kraftstoff aus dem Steuerraum. Dies beeinflusst die Funktion des Steuerventils und damit auch des Kraftstoffinjektors, der durch ein solches Steuerventil gesteuert wird. Offenbarung der ErfindungPressure fluctuations in the pressure chamber and thus to a relative movement of the sealing surface on the valve seat. This leads to wear at this point, in particular if a line-shaped bearing surface is provided on the sealing surface on the valve seat, so that the sealing surface, which rests effectively on the valve seat, becomes ever larger. Exceeds this sealing surface a certain value, the surface pressure is no longer sufficient to seal the control valve, and there are leakage losses from the pressure chamber and thus also to a continuous outflow of fuel from the control room. This affects the function of the control valve and thus also the fuel injector, which is controlled by such a control valve. Disclosure of the invention
Das erfindungsgemäße Steuerventil für einen Kraftstoffinjektor weist demgegen- über den Vorteil auf, dass der Verschleiß im Bereich des Ventilsitzes gegenüber dem bekannten Ventil deutlich verringert ist, so dass eine zuverlässige Funktion über die gesamte Lebensdauer des Steuerventils gewährleistet ist. Hierzu ist an der Seite des Ventilkörpers, an der sich der Ventilsitz befindet, eine Ausnehmung ausgebildet, die mit dem Druckraum in hydraulischer Verbindung steht. Schwankt der Druck im Druckraum, so wird einerseits die Steuerhülse, andererseits aber auch die Ausnehmung im Ventilkörper radial aufgeweitet, wobei die Ausnehmung so beschaffen ist, dass die Relativbewegung des Ventilsitzes und der Dichtfläche zumindest annähernd gleich ist, was den Verschleiß in diesem Bereich deutlich reduziert.In contrast, the control valve according to the invention for a fuel injector has the advantage that the wear in the region of the valve seat is markedly reduced compared to the known valve, so that a reliable function over the entire service life of the control valve is ensured. For this purpose, a recess is formed on the side of the valve body, on which the valve seat is located, which is in hydraulic communication with the pressure chamber. Varying pressure in the pressure chamber, so on the one hand, the control sleeve, but also the recess in the valve body is radially expanded, wherein the recess is such that the relative movement of the valve seat and the sealing surface is at least approximately equal, which significantly reduces wear in this area ,
In einer ersten vorteilhaften Ausgestaltung ist die Steuerhülse auf einem Führungsstift geführt, der von der dem Ventilkörper abgewandt Seite der Führungshülse aus in die Führungshülse hineinragt. Hierdurch wird die Führungshülse unabhängig vom Ventilkörper geführt, so dass ein genaues Ausrichten der Ventil- hülse auf dem Ventilsitz möglicht ist. Besonders vorteilhaft ist es hierbei, wenn der Führungsstift einen Fortsatz aufweist, der in die Ausnehmung des Ventilkörpers hineinragt. Hierdurch lässt sich das Volumen des Druckraums vermindern, was die Dynamik des Steuerventils erhöht, da die Druckänderungen im Druckraum und damit im Steuerraum schneller vorgenommen werden können. Hierbei bleibt die Funktion der Ausnehmung im Ventilkörper erhalten.In a first advantageous embodiment, the control sleeve is guided on a guide pin, which protrudes from the side facing away from the valve body side of the guide sleeve into the guide sleeve. As a result, the guide sleeve is guided independently of the valve body, so that an accurate alignment of the valve sleeve on the valve seat is possible. It is particularly advantageous here if the guide pin has an extension which projects into the recess of the valve body. As a result, the volume of the pressure chamber can be reduced, which increases the dynamics of the control valve, since the pressure changes in the pressure chamber and thus in the control room can be made faster. In this case, the function of the recess in the valve body is maintained.
In einer weiteren vorteilhaften Ausgestaltung ist der Ventilsitz konisch ausgebildet, weist also die Form eines Kegelstumpfs auf, wobei der Ventilsitz um die Ausnehmung herum ausgebildet ist. Durch eine geeignete Wahl des Öffnungs- winkeis des Kegelstumpfs lässt sich sowohl der Verschleiß durch die Druckaufweitung als auch der Verschleiß durch das Aufsetzen der Steuerhülse minimieren.In a further advantageous embodiment of the valve seat is conical, thus has the shape of a truncated cone, wherein the valve seat is formed around the recess around. By a suitable choice of the opening angle of the truncated cone, both the wear due to the pressure expansion and the wear due to the fitting of the control sleeve can be minimized.
In einer weiteren vorteilhaften Ausgestaltung weist der Innendurchmesser der Führungshülse und der Durchmesser der Ausnehmung denselben Durchmesser auf. Durch diese Formgebung des Ventilkörpers lassen sich die gleichen elastischen Eigenschaften sowohl in der Steuerhülse als auch im Ventilkörper im Bereich der Ausnehmung erreichen, so dass eine identische Verformung beider Teile durch den Innendruck im Druckraum gewährleistet ist.In a further advantageous embodiment, the inner diameter of the guide sleeve and the diameter of the recess have the same diameter on. By this shape of the valve body, the same elastic properties can be achieved both in the control sleeve and in the valve body in the region of the recess, so that an identical deformation of both parts is ensured by the internal pressure in the pressure chamber.
Besonders vorteilhaft ist der Einsatz des Steuerventils in einem Kraftstoffinjektor für Brennkraftmaschinen, bei dem der Kraftstoffdruck in einem Steuerraum durch das Steuerventil eingestellt wird. Durch den wechselnden Druck im Steuerraum lässt sich eine Ventilnadel in ihrer Längsrichtung bewegen, die die Kraftstoffein- spritzung des Kraftstoffinjektors in einen Brennraum der Brennkraftmaschine steuert.Particularly advantageous is the use of the control valve in a fuel injector for internal combustion engines, in which the fuel pressure is adjusted in a control chamber by the control valve. Due to the changing pressure in the control chamber, a valve needle can be moved in its longitudinal direction, which controls the fuel injection of the fuel injector into a combustion chamber of the internal combustion engine.
Zeichnungdrawing
In der Zeichnung sind verschiedene Ausführungsbeispiele des erfindungsgemäßen Steuerventils dargestellt. Es zeigt:In the drawing, various embodiments of the control valve according to the invention are shown. It shows:
Figur 1 einen Kraftstoffinjektor, wobei nur der wesentliche Teil des Injektors gezeigt ist und die entsprechende Anwendung des erfindungsgemä- ßen Steuerventils,1 shows a fuel injector, wherein only the essential part of the injector is shown and the corresponding application of the inventive control valve,
Figur 2 eine vergrößerte Darstellung des Steuerventils im Bereich des Ventilsitzes bzw. der Dichtfläche,FIG. 2 is an enlarged view of the control valve in the region of the valve seat or the sealing surface;
Figur 3 ein weiteres Ausführungsbeispiel des Steuerventils, wobei derselbeFigure 3 shows another embodiment of the control valve, wherein the same
Ausschnitt wie in Figur 2 gezeigt ist,Section as shown in Figure 2,
Figur 4 ein weiteres Ausführungsbeispiel undFigure 4 shows another embodiment and
Figur 5 zeigt ein viertes Ausführungsbeispiel, bei dem der Führungsstift weit in den Ventilkörper hineinragt.FIG. 5 shows a fourth exemplary embodiment in which the guide pin projects far into the valve body.
Beschreibung der Ausführungsbeispiele In Figur 1 ist ein Längsschnitt durch einen Kraftstoffinjektor dargestellt, in den ein erfindungsgemäßes Steuerventil eingesetzt ist. Der Kraftstoffinjektor weist ein Gehäuse 1 auf, in welchem ein Steuerventil 3 ausgebildet ist, das die Bewegung einer Ventilnadel 10 steuert. Die Ventilnadel 10 ist hierbei kolbenförmig ausgebil- det und steuert mit ihrem dem Steuerventil 3 abgewandten Ende eine Einspritzöffnung, durch die Kraftstoff in einen Brennraum einer Brennkraftmaschine einspritzbar ist. Die Ventilnadel 10 ist hierbei in einem Ventilkörper 5 geführt, der im Gehäuse 1 angeordnet ist und der eine Bohrung 12 aufweist, in der die Ventilnadel 10 geführt ist. Durch die Bohrung 12 des Ventilkörpers 5 und die Ventilnadel 10 wird ein Steuerraum 7 begrenzt, dessen Kraftstoff druck auf die dem Steuerventil zugewandte Seite der Ventilnadel 10 wirkt und so eine Schließkraft auf die Ventilnadel 10 erzeugt. Der Steuerraum 7 wird stets mit Kraftstoff unter hohem Druck versorgt. Dies geschieht über einen Ringraum 14, der den Ventilkörper 5 umgibt und der über eine in der Zeichnung nicht dargestellte Bohrung mit einem Kraftstoffanschluss verbunden ist, über den von einer Hochdruckpumpe verdichteter Kraftstoff zugeführt wird. Der Ringraum 14 ist durch eine Drosselbohrung 15 mit dem Steuerraum 7 verbunden, so dass mit einer gewissen zeitlichen Verzögerung stets der gleiche Kraftstoffdruck, sowohl im Steuerraum 7, als auch im Ringraum 14 herrscht. Der Ringraum 14 ist dabei über eine Dichtung 17 gegen- über dem Niederdruckbereich des Kraftstoffinjektors abgedichtet.Description of the embodiments 1 shows a longitudinal section through a fuel injector, in which a control valve according to the invention is used. The fuel injector has a housing 1, in which a control valve 3 is formed, which controls the movement of a valve needle 10. The valve needle 10 is in this case in the form of a piston and, with its end facing away from the control valve 3, controls an injection opening through which fuel can be injected into a combustion chamber of an internal combustion engine. The valve needle 10 is guided in this case in a valve body 5, which is arranged in the housing 1 and which has a bore 12 in which the valve needle 10 is guided. Through the bore 12 of the valve body 5 and the valve needle 10, a control chamber 7 is limited, the fuel pressure acts on the control valve side facing the valve needle 10 and so generates a closing force on the valve needle 10. The control chamber 7 is always supplied with fuel under high pressure. This is done via an annular space 14 which surrounds the valve body 5 and which is connected via a bore, not shown in the drawing, to a fuel port, via which fuel compressed by a high-pressure pump is supplied. The annular space 14 is connected through a throttle bore 15 with the control chamber 7, so that with a certain time delay always the same fuel pressure, both in the control chamber 7, as well as in the annular space 14 prevails. The annular space 14 is sealed off via a seal 17 with respect to the low-pressure region of the fuel injector.
Der Druck im Steuerraum 7 wird durch das Steuerventil 3 geregelt. Hierzu weist der Ventilkörper 5 einen Ablaufkanal 20 auf, der mittig und koaxial zur Ventilnadel 10 verläuft. Im Ablaufkanal 20 ist eine Drossel 22 ausgebildet, so dass die Menge des abfließenden Kraftstoffs nur gedrosselt durch den Ablaufkanal 20 abfließen kann. Der Ablaufkanal 20 mündet in eine Ausnehmung 24, die Teil eines Druckraums 26 ist, wobei der Druckraum 26 durch eine Steuerhülse 25, einen Führungsstift 30 und durch die Ausnehmung 24 des Ventilkörper 5 begrenzt wird. Die Steuerhülse 25 ist verschiebbar auf dem Führungsstift 30 geführt und mit ei- nem Magnetanker 34 verbunden, der durch einen Elektromagneten 35 bewegt werden kann. Gleichzeitig stützt sich eine Schließfeder 32 zwischen der Steuerhülse 25 und einer Ringscheibe 29 ab, die mit dem Führungsstift fest verbunden ist. Durch die Kraft der Schließfeder 32, die unter Druckvorspannung im Gehäuse 1 angeordnet ist, wird die Steuerhülse 25 gegen den Ventilkörper 5 gedrückt und andererseits der Führungsstift 30 über die Ringscheibe 29 gegen das Gehäuse 1, so dass der Führungsstift 30 ortsfest im Gehäuse 1 verbleibt.The pressure in the control chamber 7 is regulated by the control valve 3. For this purpose, the valve body 5 has a flow channel 20, which runs centrally and coaxially with the valve needle 10. In the drain passage 20, a throttle 22 is formed, so that the amount of the outflowing fuel can flow only throttled through the drain passage 20. The outlet channel 20 opens into a recess 24, which is part of a pressure chamber 26, wherein the pressure chamber 26 is limited by a control sleeve 25, a guide pin 30 and through the recess 24 of the valve body 5. The control sleeve 25 is slidably guided on the guide pin 30 and connected to a magnet armature 34, which can be moved by an electromagnet 35. At the same time, a closing spring 32 is supported between the control sleeve 25 and an annular disc 29, which is firmly connected to the guide pin. By the force of the closing spring 32, which is arranged under pressure bias in the housing 1, the control sleeve 25 is pressed against the valve body 5 and on the other hand, the guide pin 30 via the annular disc 29 against the housing 1, so that the guide pin 30 remains stationary in the housing 1.
Soll eine Einspritzung erfolgen, so wird der Elektromagnet 35 bestromt und die Steuerhülse 35 durch den Magnetanker 34 nach oben gezogen, d. h. vom Ventilsitz 28 weg. Hierdurch wird der Druckraum 26 mit dem Leckölraum 38 verbunden, der drucklos ist, da er über einen Ablauf 40 mit einem Niederdrucksystem verbunden ist. Der Druck im Druckraum 26 und im Steuerraum 7 sinkt daraufhin ab und die Schließkraft auf die Ventilnadel 10 vermindert sich soweit, dass sich die Ventilnadel 10 in Richtung des Steuerraums 7 bewegt und dadurch Einspritzöffnungen freigibt, durch die jetzt Kraftstoff beispielsweise in einen Brennraum eingespritzt wird. Zur Beendigung der Einspritzung wird der Elektromagnet 35 stromlos geschaltet, so dass die Steuerhülse 25 durch die Schließfeder 32 erneut gegen den Ventilsitz 28 gedrückt wird, was den Druckraum 26 gegen den Lecköl- räum 38 verschließt. Der aus dem Ringraum 14 durch die Drosselbohrung 15 nachfließende Kraftstoff erhöht erneut den Kraftstoff druck im Steuerraum 7 und damit auch im Druckraum 26, was die Ventilnadel 10 in ihre Schließstellung drückt, womit die Kraftstoffeinspritzung beendet ist.If an injection takes place, then the electromagnet 35 is energized and the control sleeve 35 pulled by the armature 34 upwards, d. H. away from the valve seat 28. As a result, the pressure chamber 26 is connected to the leakage oil chamber 38, which is depressurized, since it is connected via a drain 40 with a low pressure system. The pressure in the pressure chamber 26 and in the control chamber 7 decreases then and the closing force on the valve needle 10 decreases so far that the valve needle 10 moves in the direction of the control chamber 7 and thereby releases injection ports through which fuel is now injected, for example, into a combustion chamber. To end the injection of the electromagnet 35 is de-energized, so that the control sleeve 25 is pressed by the closing spring 32 again against the valve seat 28, which closes the pressure chamber 26 against the Lecköl- space 38. The nachfließende from the annular space 14 through the throttle bore 15 fuel again increases the fuel pressure in the control chamber 7 and thus also in the pressure chamber 26, which pushes the valve needle 10 in its closed position, whereby the fuel injection is terminated.
In Figur 2 ist der Bereich des Druckraums 26 nochmals vergrößert dargestellt.In Figure 2, the area of the pressure chamber 26 is shown enlarged again.
An der Führungshülse 25 ist eine Dichtfläche 27 ausgebildet, die im Wesentlichen ringkreisförmig ausgebildet ist und die auf einem am Ventilkörper 5 ausgebildeten, ebenen Ventilsitz 28 aufliegt. Durch die Kraft der Schließfeder 32 wird die Steuerhülse 25 mit ausreichender Flächenpressung gegen den Ventilsitz 28 gedrückt, so dass der Druckraum 26 gegen den drucklosen Leckölraum 38 abgedichtet ist. Der Ventilkörper 5 weist im Bereich des Ventilssitzes 28 durch die Ausnehmung 24 eine im Wesentlichen hohlzylindrische Form auf. Die Ausnehmung 24 ist dabei so bemessen, dass durch den Druck im Druckraum 26 eine Aufweitung des Ventilkörpers 5 im Bereich der Ausnehmung 24 radial nach au- ßen erfolgt, ebenso wie durch den Druck im Druckraum 26 die Steuerhülse 25 radial aufgeweitet wird. Durch eine geeignete Auslegung der Ausnehmung 24 und die Formgebung der Steuerhülse 25 lässt sich erreichen, dass es bei geschlossenem Steuerventil 3 keine oder nur eine sehr geringe Relativbewegung zwischen der Dichtfläche 27 und dem Ventilsitz 28 auftritt. Dadurch wird der Ver- schleiß zwischen der Ventildichtfläche und dem Ventilsitz 28 entscheidend ge- mindert, was die Lebensdauer des Steuerventils 3 und damit des gesamten Kraftstoffinjektors erheblich erhöht.On the guide sleeve 25, a sealing surface 27 is formed, which is formed substantially annularly circular and which rests on a valve body 5 formed on the flat valve seat 28. By the force of the closing spring 32, the control sleeve 25 is pressed with sufficient surface pressure against the valve seat 28, so that the pressure chamber 26 is sealed against the pressureless leakage oil chamber 38. The valve body 5 has in the region of the valve seat 28 through the recess 24 has a substantially hollow cylindrical shape. The recess 24 is dimensioned such that due to the pressure in the pressure chamber 26, a widening of the valve body 5 in the region of the recess 24 takes place radially outward, just as the control sleeve 25 is radially widened by the pressure in the pressure chamber 26. By a suitable design of the recess 24 and the shape of the control sleeve 25 can be achieved that there is no or only a very small relative movement between the sealing surface 27 and the valve seat 28 when the control valve 3 is closed. As a result, the wear between the valve sealing surface and the valve seat 28 becomes crucial. reduces, which significantly increases the life of the control valve 3 and thus the entire fuel injector.
In Figur 3 ist ein weiteres Ausführungsbeispiel des erfindungsgemäßen Steuer- ventils 3 dargestellt. Der Ventilsitz 28' ist hier konisch ausgebildet, und entsprechend weist die Dichtfläche 27' ebenfalls eine konische Form auf. Durch diese Formgebung der Steuerhülse 25 und des Ventilsitzes 28' wird die Hülse stets zum Ventilsitz 28' zentriert, so dass das Abströmen des Kraftstoffs aus dem Druckraum 26 bei der Öffnungsbewegung der Steuerhülse 25 symmetrisch ge- schieht.FIG. 3 shows a further exemplary embodiment of the control valve 3 according to the invention. The valve seat 28 'is conical here, and accordingly, the sealing surface 27' also has a conical shape. As a result of this shaping of the control sleeve 25 and of the valve seat 28 ', the sleeve is always centered relative to the valve seat 28' so that the outflow of the fuel from the pressure chamber 26 occurs symmetrically during the opening movement of the control sleeve 25.
Figur 4 zeigt ein weiteres Ausführungsbeispiel, wobei hier am Führungsstift 30' ein Fortsatz 31 ausgebildet ist, der in die Ausnehmung 24 hineinragt. Dadurch kann das Volumen des Druckraum 26 entscheidend verringert werden, was die Ansprechzeit des Steuerventils 3 erheblich verkürzt. Je geringer das Volumen imFigure 4 shows another embodiment, in which case an extension 31 is formed here on the guide pin 30 ', which projects into the recess 24. As a result, the volume of the pressure chamber 26 can be decisively reduced, which considerably shortens the response time of the control valve 3. The lower the volume in the
Bereich des Druckraums 26 und auch im Bereich des Steuerraums 7, desto schneller kann der Druck im Druckraum 26 und damit auch im Steuerraum 7 erhöht oder erniedrigt werden. Durch die Formumgebung des Fortsatzes 31 lässt sich auch erreichen, dass die Strömungsverhältnisse beim Ausströmen des Kraftstoffs in den Leckölraum 38 optimiert werden und nur geringe Verluste durchArea of the pressure chamber 26 and also in the area of the control chamber 7, the faster the pressure in the pressure chamber 26 and thus also in the control chamber 7 can be increased or decreased. Due to the shape environment of the extension 31 can also be achieved that the flow conditions are optimized when flowing out of the fuel in the leakage oil chamber 38 and only small losses
Verwirbelung des Kraftstoffstroms entstehen bei gleichzeitig minimalem Volumen des Druckraums 26.Turbulence of the fuel flow occur at the same time minimal volume of the pressure chamber 26th
Der Ventilsitz 28' ist hier ebenfalls konisch ausgebildet, jedoch ist der Konuswin- kel gegenüber dem Ausführungsbeispiel nach Fig. 3 deutlich vergrößert. Durch diesen Konuswinkel α kann der Verschleiß zwischen Dichtfläche 27' und Ventilsitz 28' weiter verringert werden: Bei dem Ausführungsbeispiel nach Fig. 3 gleitet die Dichtfläche 27' beim Aufsetzen auf dem konischen Ventilsitz 28' leicht nach außen ab. Gleichzeitig wird der Ventilsitz 28' durch die Steuerhülse 25 nach in- nen gedrückt, so dass es bei jeder Schließbewegung der Steuerhülse 25 zu einerThe valve seat 28 'is also conical in this case, however, the conical angle compared to the embodiment of FIG. 3 is significantly increased. By this cone angle α, the wear between the sealing surface 27 'and the valve seat 28' can be further reduced: In the embodiment of FIG. 3, the sealing surface 27 'slides easily when placed on the conical valve seat 28' to the outside. At the same time, the valve seat 28 'is pressed inwards by the control sleeve 25, so that it turns into a valve for each closing movement of the control sleeve 25
Relativbewegung zwischen Ventilsitz 28' und Dichtfläche 27' kommt. Wird der Ventilsitz 28' hingegen als Konus mit großem Öffnungswinkel gebildet, so kann dieses Abgleiten beim Aufsetzen der Steuerhülse verhindert werden, wobei gleichzeitig die Relativbewegung von Ventilsitz 28' und Dichtfläche 27' durch den schwankenden Druck im Druckraum 26 unterdrückt ist. Als Konuswinkel α für den Ventilsitz 28', also als Öffnungswinkel des entsprechenden Kegels, hat sich ein Wert von 155° bis 175° als besondert vorteilhaft erwiesen, insbesondere ein Winkel von etwa 160°. Die Dichtfläche (27') weist dabei zumindest näherungsweise den gleichen Konuswinkel wie der Ventilsitz 28' auf.Relative movement between valve seat 28 'and sealing surface 27' comes. If the valve seat 28 ', however, formed as a cone with a large opening angle, this sliding can be prevented when placing the control sleeve, at the same time the relative movement of the valve seat 28' and sealing surface 27 'is suppressed by the fluctuating pressure in the pressure chamber 26. As cone angle α for the valve seat 28 ', so as the opening angle of the corresponding cone, a value of 155 ° to 175 ° has proven to be particularly advantageous, in particular an angle of about 160 °. The sealing surface (27 ') has at least approximately the same cone angle as the valve seat 28'.
In Figur 5 ist ein weiteres Ausführungsbeispiel des Steuerventils dargestellt. Statt einer Ausnehmung 24, die im Wesentlichen die Form einer Sackbohrung aufweist, ist hier eine Bohrung vorgesehen, die den gesamten Ventilkörper 5 durchzieht und bis in den Steuerraum 7 reicht, wobei der Durchmesser der Boh- rung 12' dem Innendurchmesser der Steuerhülse 25 entspricht. Der FührungsstiftFIG. 5 shows a further exemplary embodiment of the control valve. Instead of a recess 24, which essentially has the shape of a blind bore, a bore is provided here, which extends through the entire valve body 5 and extends into the control chamber 7, the diameter of the bore 12 'corresponding to the inner diameter of the control sleeve 25. The guide pin
30" ist so ausgebildet, dass er einerseits die Steuerhülse 25 führt und andererseits weit in den Ventilkörper 5 hineinragt. Am Führungsstift 30" sind im Bereich des Ventilkörpers 5 Anschliffe 33 ausgebildet, so dass eine hydraulische Verbindung des Druckraums 26' mit dem Steuerraum 7 gewährleistet ist. Da der Ventil- körper 5 im Bereich des Ventilsitzes 28" genau dieselbe Form aufweist, nämlich eine Hohlzylinderform wie die Steuerhülse 25, ergeben sich auf identische elastische Eigenschaften, so dass eine Relativbewegung zwischen Ventilsitz 28 und Dichtfläche 27" durch den wechselnden Druck im Druckraum 26' ausgeschlossen ist. 30 "is designed such that on the one hand it guides the control sleeve 25 and on the other hand projects far into the valve body 5. On the guide pin 30", 5 bevels 33 are formed in the region of the valve body so that a hydraulic connection of the pressure chamber 26 'to the control chamber 7 is ensured is. Since the valve body 5 "in the region of the valve seat 28" exactly the same shape, namely a hollow cylindrical shape as the control sleeve 25, resulting in identical elastic properties, so that a relative movement between the valve seat 28 and sealing surface 27 "by the changing pressure in the pressure chamber 26th 'is excluded.

Claims

Ansprüche claims
1. Steuerventil für einen Kraftstoffinjektor mit einer Steuerhülse (25), die einen Druckraum (26; 26') begrenzt und die in ihrer Längsrichtung beweglich gelagert ist, wobei die Steuerhülse (25) an einer Stirnseite eine Dichtfläche (27; 27'; 27") aufweist, mit der sie mit einem Ventilsitz (28; 28'; 28") zusammenwirkt, der an einem Ventilkörper (5) ausgebildet ist, dadurch gekennzeichnet, dass im Ventilkörper (5) eine Ausnehmung (24; 24') in der dem Druckraum (26; 26') zugewandten Seite des Ventilkörpers (5) ausgebildet ist, wobei die Steuerhülse (25) und die Ausnehmung (24; 24') im Ventilkörper (5) so ausgebildet sind, dass die Verformung von Steuerhülse (25) und Ventilkörper1. Control valve for a fuel injector with a control sleeve (25) which delimits a pressure chamber (26, 26 ') and which is movably mounted in its longitudinal direction, wherein the control sleeve (25) at one end face a sealing surface (27; 27'; 27 "), with which it cooperates with a valve seat (28; 28 '; 28") formed on a valve body (5), characterized in that in the valve body (5) has a recess (24; 24') in the The control sleeve (25) and the recess (24, 24 ') in the valve body (5) are formed such that the deformation of the control sleeve (25) is formed in the pressure chamber (26, 26') facing the valve body (5). and valve body
(5) durch den Druck im Druckraum (26; 26') zu keiner oder nur zu sehr geringer Bewegung zwischen dem Ventilsitz (28; 28'; 28") und der Dichtfläche (27; 27'; 27") der Steuerhülse (25) führt.(5) due to the pressure in the pressure chamber (26; 26 ') no or only very little movement between the valve seat (28; 28'; 28 ") and the sealing surface (27; 27 '; 27") of the control sleeve (25 ) leads.
2. Steuerventil nach Anspruch 1, dadurch gekennzeichnet, dass die Steuerhül- se (25) auf einem Führungsstift (30; 30'; 30") geführt ist, der von der dem2. Control valve according to claim 1, characterized in that the Steuerhül- se (25) on a guide pin (30; 30 ', 30 ") is guided, of the
Ventilkörper (5) abgewandten Seite der Steuerhülse (25) in die Steuerhülse (25) hineinragt, so dass der Druckraum (26; 26') durch die Steuerhülse (25), den Führungsstift (30; 30'; 30") und den Ventilkörper (5) begrenzt wird.Valve body (5) facing away from the control sleeve (25) projects into the control sleeve (25), so that the pressure chamber (26; 26 ') through the control sleeve (25), the guide pin (30; 30'; 30 ") and the valve body (5) is limited.
3. Steuerventil nach Anspruch 2, dadurch gekennzeichnet, dass der Führungs- stift (30; 30'; 30") einen im Verhältnis zum Innendurchmesser der Steuerhülse (25) im Durchmesser reduzierten Fortsatz (31) aufweist, der in die Ausnehmung (24) des Ventilkörpers (5) hineinragt.3. Control valve according to claim 2, characterized in that the guide pin (30; 30 '; 30 ") has a reduced in diameter relative to the inner diameter of the control sleeve (25) extension (31) which in the recess (24) of the valve body (5) protrudes.
4. Steuerventil nach Anspruch 1, dadurch gekennzeichnet, dass die Ausnehmung (24) im Ventilkörper (5) als Sackbohrung ausgeführt ist. 4. Control valve according to claim 1, characterized in that the recess (24) in the valve body (5) is designed as a blind bore.
5. Steuerventil nach Anspruch 4, dadurch gekennzeichnet, dass die Ausneh- mung (24) in Form einer Sackbohrung an ihrem offenen Ende einen geringeren Durchmesser aufweist als der Innendurchmesser der Steuerhülse (25).5. Control valve according to claim 4, characterized in that the recess (24) in the form of a blind bore at its open end has a smaller diameter than the inner diameter of the control sleeve (25).
6. Steuerventil nach Anspruch 1, dadurch gekennzeichnet, dass der Ventilsitz (28; 28'; 28") eine ebene Ringkreisfläche ist, die um die Ausnehmung (24) herum ausgebildet ist.6. Control valve according to claim 1, characterized in that the valve seat (28, 28 ', 28 ") is a flat annular circular surface which is formed around the recess (24) around.
7. Steuerventil nach Anspruch 1, dadurch gekennzeichnet, dass der Ventilsitz (28; 28'; 28") konisch ausgebildet ist, also die Form eines Kegelstumpfs aufweist, wobei der Ventilsitz (28; 28'; 28") um die Ausnehmung (24) herum ausgebildet ist.7. Control valve according to claim 1, characterized in that the valve seat (28, 28 ', 28 ") is conical, ie has the shape of a truncated cone, wherein the valve seat (28, 28', 28") around the recess (24 ) is formed around.
8. Steuerventil nach Anspruch 7, dadurch gekennzeichnet, dass der Konuswinkel (α) des konischen Ventilsitzes (28; 28'; 28") 155° bis 175° beträgt, vorzugsweise etwa 160°.8. Control valve according to claim 7, characterized in that the cone angle (α) of the conical valve seat (28, 28 ', 28 ") is 155 ° to 175 °, preferably about 160 °.
9. Steuerventil nach Anspruch 8, dadurch gekennzeichnet, dass die Dichtfläche (27; 27') ebenfalls konisch ausgebildet ist.9. Control valve according to claim 8, characterized in that the sealing surface (27, 27 ') is also conical.
10. Steuerventil nach Anspruch 9, dadurch gekennzeichnet, dass der Konuswinkel der Dichtfläche (27; 27') und der Konuswinkel (α) des Ventilsitzes (28; 28'; 28") gleich groß sind.10. Control valve according to claim 9, characterized in that the cone angle of the sealing surface (27, 27 ') and the cone angle (α) of the valve seat (28, 28', 28 ") are the same size.
11. Steuerventil nach Anspruch 1, dadurch gekennzeichnet, dass die Ausneh- mung (24) als Bohrung (12') im Ventilkörper (5) ausgebildet ist, die denselben Durchmesser aufweist wie der Innendurchmesser der Steuerhülse (25).11. Control valve according to claim 1, characterized in that the recess (24) as a bore (12 ') in the valve body (5) is formed, which has the same diameter as the inner diameter of the control sleeve (25).
12. Steuerventil nach Anspruch 11, dadurch gekennzeichnet, dass sowohl die Dichtfläche (27; 27'; 27") der Steuerhülse (25) als auch der Ventilsitz (28; 28'; 28") am Ventilkörper (5) als Ringkreisfläche ausgebildet sind.12. Control valve according to claim 11, characterized in that both the sealing surface (27, 27 ', 27 ") of the control sleeve (25) and the valve seat (28, 28', 28") on the valve body (5) are designed as an annular circular surface ,
13. Kraftstoffinjektor für Brennkraftmaschinen mit einem Steuerventil (3) nach einem der Ansprüche 1 bis 12, welches den Kraftstoffdruck in einem Steuerraum (7) einstellt, mit einer kolbenförmigen Ventilnadel (10), die mit einem Körpersitz im Gehäuse (1) zusammenwirkt und so eine Einspritzöffnung öffnet und schließt, so dass je nach Stellung der Ventilnadel (10) Kraftstoff aus den Einspritzöffnungen ausgespritzt wird, wobei durch den Druck im Steuerraum (7) eine Schließkraft auf die Ventilnadel (10) in Richtung des Ventilsitzes zumindest mittelbar ausgeübt wird und der Steuerraum (7) mit dem Druckraum (26; 26') hydraulisch verbunden ist. 13. Fuel injector for internal combustion engines with a control valve (3) according to one of claims 1 to 12, which adjusts the fuel pressure in a control chamber (7), with a piston-shaped valve needle (10), with a Body seat in the housing (1) cooperates and thus opens an injection port and closes, so that depending on the position of the valve needle (10) fuel is ejected from the injection openings, wherein by the pressure in the control chamber (7) a closing force on the valve needle (10) in Direction of the valve seat is at least indirectly exerted and the control chamber (7) to the pressure chamber (26, 26 ') is hydraulically connected.
EP08760855.0A 2007-06-21 2008-06-11 Control valve for a fuel injection valve Active EP2171258B1 (en)

Applications Claiming Priority (3)

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DE102007028485 2007-06-21
DE102007044357A DE102007044357A1 (en) 2007-06-21 2007-09-17 Control valve for a fuel injection valve
PCT/EP2008/057304 WO2008155275A1 (en) 2007-06-21 2008-06-11 Control valve for a fuel injection valve

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EP2171258A1 true EP2171258A1 (en) 2010-04-07
EP2171258B1 EP2171258B1 (en) 2014-12-17

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EP08760855.0A Active EP2171258B1 (en) 2007-06-21 2008-06-11 Control valve for a fuel injection valve

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JP (1) JP5345612B2 (en)
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DE (2) DE102007044357A1 (en)
RU (2) RU2468244C2 (en)
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WO2008155275A1 (en) 2008-12-24
CN101688508B (en) 2012-03-21
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WO2008155260A1 (en) 2008-12-24
DE102007044357A1 (en) 2008-12-24
CN101688508A (en) 2010-03-31
RU2010101642A (en) 2011-07-27
RU2468244C2 (en) 2012-11-27
CN101680413A (en) 2010-03-24
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EP2171257B1 (en) 2012-08-15
JP5345612B2 (en) 2013-11-20
EP2171258B1 (en) 2014-12-17
JP2010530492A (en) 2010-09-09
RU2480616C2 (en) 2013-04-27
RU2010101640A (en) 2011-07-27
DE102007044355A1 (en) 2008-12-24

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