EP2165069B1 - Control valve, particularly for a fuel injector of an internal combustion engine - Google Patents

Control valve, particularly for a fuel injector of an internal combustion engine Download PDF

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Publication number
EP2165069B1
EP2165069B1 EP08760982A EP08760982A EP2165069B1 EP 2165069 B1 EP2165069 B1 EP 2165069B1 EP 08760982 A EP08760982 A EP 08760982A EP 08760982 A EP08760982 A EP 08760982A EP 2165069 B1 EP2165069 B1 EP 2165069B1
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EP
European Patent Office
Prior art keywords
valve
valve piston
coupler
piston spring
spring
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP08760982A
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German (de)
French (fr)
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EP2165069A1 (en
Inventor
Holger Rapp
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP2165069A1 publication Critical patent/EP2165069A1/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
    • 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
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic

Definitions

  • the invention relates to a control valve, in particular for a fuel injector of an internal combustion engine according to the preamble of claim 1 such as in document WO 2004/104403 shown.
  • Control valves for fuel injectors which are used as servo-valves for indirectly driving a nozzle needle of a fuel injector are known, for example from DE 103 22 672 A1 .
  • These servo-valves comprise a piezo-actuator, which acts via a coupler module on a valve member which blocks a fluid flow from a valve chamber to a return channel in the closed position and connects the fluid flow from a rear control chamber of the nozzle needle with the return channel by opening a valve seat.
  • the coupler connected between the piezoactuator and the valve member comprises a coupler piston guided in a coupler housing and a valve piston, between which there is a coupler gap with a hydraulic cushion as a hydraulic coupler.
  • an actuator head is designed with a spherical bearing geometry, which dips into an arcuate, concave depression on an adjusting piece.
  • the valve piston must be preloaded by a valve piston spring with a preload of approximately 18N.
  • the valve piston spring presses the valve piston against a valve element of a valve member.
  • a sleeve is pressed onto the valve piston, on which the valve piston spring is supported on the valve piston side.
  • the counter bearing for the valve piston spring forms an annular surface on the coupler housing.
  • Object of the present invention is to make the control valve easier and cheaper.
  • the object of the invention is achieved with the characterizing features of claim 1. This eliminates the pressed-on the valve piston sleeve for supporting the valve piston spring.
  • a conically wound valve piston spring which is supported in a circumferential groove on the valve piston.
  • the conically wound valve piston spring engages with the small winding diameter in the groove, so that the recess forms the valve piston-side support for the valve piston spring. It is also particularly advantageous to upstream of the notch valve element side an insertion, so that the valve piston spring is pushed in the assembly with the large winding diameter of the conically coiled valve piston spring on the insertion beforehand and the small winding diameter of the conically coiled valve piston spring biased slides over the Ein 1500Cge and in the Notch or the groove engages.
  • the recess has an annular bearing surface, which extends slightly inclined in the radial direction in the direction of the central axis of the valve piston.
  • the Indian FIG. 1 and 2 illustrated fuel injector has an injector body 10, a nozzle body 11, a valve plate 12 and a throttle plate 13 which are clamped by means of a hydraulic nozzle nut 15 hydraulically tight.
  • a receiving space 16 and a high pressure bore 17 is formed in the injector body 11.
  • a piezoelectric actuator 25 with an actuator base 26 and a coupler module 30 is arranged in the receiving space 16.
  • a nozzle needle pressure chamber 18 is formed, in which a nozzle needle 19 is guided axially movable.
  • the nozzle needle 19 is exposed at the rear end of a control chamber 20 which is surrounded radially by a control chamber sleeve 21 which separates the control chamber 20 from the nozzle needle pressure chamber 18 hydraulically.
  • In the nozzle needle pressure chamber 18 performs a guided through the throttle plate 15 high-pressure bore 22 and guided through the valve plate 13 further high-pressure bore 23, which are hydraulically in communication with the high-pressure bore 17.
  • About these hydraulic connections stored in the common rail fuel reaches the prevailing system pressure in the nozzle needle pressure chamber 18 to which the nozzle needle 19 is exposed with a pressure shoulder, not shown.
  • the coupler module 30 comprises according to FIG. 1 and 2 a coupler housing 31, a spring sleeve 32, a coupler piston 33, a valve piston 34, a valve piston spring 35 and a shim 36.
  • the coupler housing 31 rests with a collar 37 on the valve plate 12. At the collar 37 also engages the spring sleeve 32, on which the shim 36 rests.
  • the coupler piston 33 is supported with a Kopplerkolbenbund 38.
  • the coupler piston 33 and the valve piston 34 are guided in guides formed on the coupler housing 31, respectively.
  • the pointing in the coupler housing 31 End faces of the coupler piston 33 and the valve piston 34 are spaced from each other, so that between the end faces of a coupler gap 39 is formed, which is filled in the guides of the coupler piston 31 and the valve piston 34 existing leakage gaps with the hydraulic medium.
  • the coupler module 30 with the coupler gap 39 acts as a hydraulic coupler to compensate for elongations of the piezoactuator 25.
  • the coupler housing 31 has at the valve member end a filling chamber 47 into which the valve piston 34 protrudes and in which the valve piston spring 35 is arranged.
  • an adjusting piece 28 is arranged, on which the actuator head 26 rests with a spherical bearing 29.
  • valve piston spring 35 is supported on the valve piston side.
  • the counter bearing for the valve piston spring 35 forms an annular surface 49 on the coupler housing 31st
  • valve plate 12 is according to FIG. 1 and 2 a valve member 40 is arranged with a valve element 41.
  • the valve element 41 is mounted in a valve chamber 42 and is held by a valve spring 43 against a valve seat 44.
  • a valve piston formed on the valve piston 34 acts 45, with which the valve element 41 can be pushed off the valve seat 44.
  • the valve piston 34 is biased by the valve piston spring 35 in the direction of the valve element 41.
  • the valve piston 34 has a notch 50 on a valve member-side end portion.
  • the indentation 50 forms on the valve piston 34 a support for the valve piston spring 35.
  • the support is executed by a circumferential recess 51 with a conical surface 52 and a support surface 53.
  • the valve piston spring 35 is according to the embodiment according to the invention FIG. 2 and 3 designed as a conically wound valve piston spring 54 with a small winding diameter d1 and a large winding diameter d2.
  • the indentation 50 or the recess 51 is preceded by a further conical section 55 on the valve element side on the valve piston 34.
  • the upstream conical section 55 serves as an insertion bevel for the conically wound valve piston spring 54 during assembly of the coupler module 40, as will be described in more detail later.
  • the bearing surface 53 forms an annular surface, which in the simplest embodiment is flat and orthogonal to the central axis of the valve piston 34.
  • the annular bearing surface 53 may also be slightly conical, in such a way that the bearing surface 53 is slightly tilted in the direction of the central axis of the valve piston 34 toward the valve end of the Ventilkobens 34 or open to the actuator end of the valve piston 34 back is.
  • the conically wound valve piston spring 54 engages better in the notch 50 or in the recess 51. It is furthermore advantageous if the axis of symmetry of the cone runs parallel to the center line of the valve piston 34, wherein the cone angle preferably has an angle of less than 180 ° and greater than 60 °.
  • the conically wound valve piston spring 54 When mounting the coupler module 30, the conically wound valve piston spring 54 is pushed with the large winding diameter d2 ahead of the other conical portion 55, so that the small winding diameter d1 of the conically wound valve piston spring 54 at the further conical portion 55 slightly widens and when crossing the other conical section 55 engages in the notch 50 and the groove 51 by the resulting pre-tension during insertion. As a result, the conically wound valve spring 54 with the small winding diameter d1 rests on the support 52 of the notch 50. The support 52 thus forms the valve piston-side abutment for the valve piston spring 54. The abutment for the large winding diameter d2, the valve piston spring 54 forms, as in the prior art according to FIG. 1 the annular surface 49 formed on the coupler housing 31.
  • the operation of the fuel injector of FIG. 1 and 2 is as follows: When actuating the piezo actuator 25, this lengthens. The resulting pressure is transmitted via the coupler piston 33, the coupler gap 39 and the valve piston 34, wherein the valve piston 34 with the valve stem 45, the valve element 41 from the valve seat 44 pushes away. As a result, the stroke of the piezoactuator 35 is transmitted to the valve element 41 and arises at the valve seat 44 a corresponding valve seat gap, so that an open state of the valve element 41 is generated.
  • drain hole is hydraulically connected to a drain channel, also not shown, the drain channel opens into the receiving space 16, which in turn is hydraulically connected to a low pressure / return system.
  • the control chamber 20 is relieved of pressure and acting in the opening direction of the pressure shoulder of the nozzle needle 19 opening forces exceed the forces acting in the control chamber 20 closing forces, so that the fuel from the nozzle needle pressure chamber 18 is injected with system pressure of the common rail.

Abstract

A control valve is proposed for controlling liquids, particularly for a fuel injector of an internal combustion engine, with an actuating unit (25) which acts via a coupler module (30) on a valve element (41. The coupler module (30), which is guided in a coupler housing (31), has a coupler piston (33) and a valve piston (34). The valve piston (34) has a notch (50) which forms a support on the valve piston side for a conically wound valve piston spring (54).

Description

Die Erfindung geht aus von einem Steuerventil, insbesondere für einen Kraftstoffinjektor einer Brennkraftmaschine gemäß dem Oberbegriff des Anspruchs 1 wie z.B. in Dokument WO 2004/104403 gezeigt.The invention relates to a control valve, in particular for a fuel injector of an internal combustion engine according to the preamble of claim 1 such as in document WO 2004/104403 shown.

Stand der TechnikState of the art

Steuerventile für Kraftstoffinjektoren, die als Servo-Ventile zum indirekten Ansteuern einer Düsennadel eines Kraftstoffinjektors verwendet werden, sind bekannt, beispielsweise aus DE 103 22 672 A1 . Diese Servo-Ventile umfassen einen Piezo-Aktor, der über ein Kopplermodul auf ein Ventilglied einwirkt, das in Schließstellung einen Fluidstrom von einem Ventilraum zu einem Rücklaufkanal sperrt und durch Öffnen eines Ventilsitzes den Fluidstrom aus einem rückwärtigen Steuerraum der Düsennadel mit dem Rücklaufkanal verbindet. Der zwischen Piezo-Aktor und Ventilglied geschaltete Koppler umfasst einen in einem Kopplergehäuse geführten Kopplerkolben und einen Ventilkolben, zwischen denen sich ein Kopplerspalt mit einem Hydraulikpolster als hydraulischer Koppler befindet. Am Piezo-Aktor ist ein Aktorkopf mit einer kugelförmigen Auflagegeometrie ausgeführt, die in eine bogenförmige, konkave Vertiefung an einem Einstellstück eintaucht. Um die Wiederbefüllung des Kopplerspaltes in den Einspritzpausen sicherzustellen, muss der Ventilkolben durch eine Ventilkolbenfeder mit einer Vorspannung von ca. 18 N vorgespannt sein. Die Ventilkolbenfeder drückt dabei den Ventilkolben gegen ein Ventilelement eines Ventilglieds. Dazu ist auf den Ventilkolben eine Hülse aufgepresst, an der sich die Ventilkolbenfeder ventilkolbenseitig stützt. Das Gegenlager für die Ventilkolbenfeder bildet eine Ringfläche am Kopplergehäuse.Control valves for fuel injectors, which are used as servo-valves for indirectly driving a nozzle needle of a fuel injector are known, for example from DE 103 22 672 A1 , These servo-valves comprise a piezo-actuator, which acts via a coupler module on a valve member which blocks a fluid flow from a valve chamber to a return channel in the closed position and connects the fluid flow from a rear control chamber of the nozzle needle with the return channel by opening a valve seat. The coupler connected between the piezoactuator and the valve member comprises a coupler piston guided in a coupler housing and a valve piston, between which there is a coupler gap with a hydraulic cushion as a hydraulic coupler. On the piezo actuator, an actuator head is designed with a spherical bearing geometry, which dips into an arcuate, concave depression on an adjusting piece. To ensure refilling of the coupler gap in the injection pauses, the valve piston must be preloaded by a valve piston spring with a preload of approximately 18N. The valve piston spring presses the valve piston against a valve element of a valve member. For this purpose, a sleeve is pressed onto the valve piston, on which the valve piston spring is supported on the valve piston side. The counter bearing for the valve piston spring forms an annular surface on the coupler housing.

Aufgabe der vorliegenden Erfindung ist es, das Steuerventil einfacher und kostengünstiger auszuführen.Object of the present invention is to make the control valve easier and cheaper.

Vorteile der ErfindungAdvantages of the invention

Die Aufgabe der Erfindung wird mit den kennzeichnenden Merkmalen des Anspruchs 1 gelöst. Dadurch entfällt die auf den Ventilkolben aufgepresste Hülse zur Abstützung der Ventilkolbenfeder.The object of the invention is achieved with the characterizing features of claim 1. This eliminates the pressed-on the valve piston sleeve for supporting the valve piston spring.

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

Besonders zweckmäßig ist die Verwendung einer konisch gewickelten Ventilkolbenfeder, die sich in einem umlaufenden Einstich am Ventilkolben abstützt. Dabei rastet die konisch gewickelte Ventilkolbenfeder mit dem kleinen Wickeldurchmesser im Einstich ein, so dass der Einstich die ventilkolbenseitige Auflage für die Ventilkolbenfeder ausbildet. Besonders vorteilhaft ist es weiterhin, der Einkerbung ventilelementseitig eine Einführschräge vorzuschalten, so dass die Ventilkolbenfeder bei der Montage mit dem großen Wickeldurchmesser der konisch gewickelten Ventilkolbenfeder voran über die Einführschräge geschoben wird und der kleine Wickeldurchmesser der konisch gewickelten Ventilkolbenfeder vorgespannt über die Einführschäge gleitet und in die Einkerbung bzw. den Einstich einrastet. Um ein sicheres Einrasten zu gewährleisten, weist der Einstich eine ringförmige Auflagefläche auf, die in radialer Richtung leicht geneigt in Richtung der Mittelachse des Ventilkolbens verläuft.Particularly useful is the use of a conically wound valve piston spring, which is supported in a circumferential groove on the valve piston. The conically wound valve piston spring engages with the small winding diameter in the groove, so that the recess forms the valve piston-side support for the valve piston spring. It is also particularly advantageous to upstream of the notch valve element side an insertion, so that the valve piston spring is pushed in the assembly with the large winding diameter of the conically coiled valve piston spring on the insertion beforehand and the small winding diameter of the conically coiled valve piston spring biased slides over the Einführschäge and in the Notch or the groove engages. In order to ensure a secure engagement, the recess has an annular bearing surface, which extends slightly inclined in the radial direction in the direction of the central axis of the valve piston.

Ausführungsbeispielembodiment

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

Es zeigen:

Figur 1
eine Schnittdarstellung durch einen Kraftstoffinjektor mit einem Kopplermodul nach dem Stand der Technik gemäß DE 103 22 672 A1 ,
Figur 2
eine Schnittdarstellung durch den Kraftstoffinjektor mit einem er- findungsgemäßen Kopplermodul und
Figur 3
eine vergrößerter Ausschnitt X des erfindungsgemäßen Kopp- lermoduls in Figur 2.
Show it:
FIG. 1
a sectional view through a fuel injector with a coupler module according to the prior art according to DE 103 22 672 A1 .
FIG. 2
a sectional view through the fuel injector with a coupler module according to the invention and
FIG. 3
an enlarged section X of the coupler module according to the invention in FIG. 2 ,

Der in der Figur 1 und 2 dargestellte Kraftstoffinjektor weist einen Injektorkörper 10, einen Düsenkörper 11, eine Ventilplatte 12 und eine Drosselplatte 13 auf, die mittels einer Düsenspannmutter 15 hydraulisch dicht verspannt sind. Im Injektorkörper 11 ist ein Aufnahmeraum 16 und eine Hochdruckbohrung 17 ausgebildet. Im Aufnahmeraum 16 ist ein Piezo-Aktor 25 mit einem Aktorfuß 26 und ein Kopplermodul 30 angeordnet.The Indian FIG. 1 and 2 illustrated fuel injector has an injector body 10, a nozzle body 11, a valve plate 12 and a throttle plate 13 which are clamped by means of a hydraulic nozzle nut 15 hydraulically tight. In the injector body 11, a receiving space 16 and a high pressure bore 17 is formed. In the receiving space 16, a piezoelectric actuator 25 with an actuator base 26 and a coupler module 30 is arranged.

Im Düsenkörper 11 ist ein Düsennadeldruckraum 18 ausgebildet, in dem eine Düsennadel 19 axial beweglich geführt ist. Die Düsennadel 19 ist am rückwärtigen Ende einem Steuerraum 20 ausgesetzt, der radial von einer Steuerraumhülse 21 umgeben ist, die den Steuerraum 20 vom Düsennadeldruckraum 18 hydraulisch trennt. In den Düsennadeldruckraum 18 führt eine durch die Drosselplatte 15 geführte Hochdruckbohrung 22 und eine durch die Ventilplatte 13 geführte weitere Hochdruckbohrung 23, die mit der Hochdruckbohrung 17 hydraulisch in Verbindung stehen. Über diese hydraulischen Verbindungen gelangt der im Common-Rail gespeicherte Kraftstoff mit dem dort herrschenden Systemdruck in den Düsennadeldruckraum 18, dem die Düsennadel 19 mit einer nicht dargestellten Druckschulter ausgesetzt ist.In the nozzle body 11, a nozzle needle pressure chamber 18 is formed, in which a nozzle needle 19 is guided axially movable. The nozzle needle 19 is exposed at the rear end of a control chamber 20 which is surrounded radially by a control chamber sleeve 21 which separates the control chamber 20 from the nozzle needle pressure chamber 18 hydraulically. In the nozzle needle pressure chamber 18 performs a guided through the throttle plate 15 high-pressure bore 22 and guided through the valve plate 13 further high-pressure bore 23, which are hydraulically in communication with the high-pressure bore 17. About these hydraulic connections stored in the common rail fuel reaches the prevailing system pressure in the nozzle needle pressure chamber 18 to which the nozzle needle 19 is exposed with a pressure shoulder, not shown.

Das Kopplermodul 30 umfasst gemäß Figur 1 und 2 ein Kopplergehäuse 31, eine Federhülse 32, einen Kopplerkolben 33, einen Ventilkolben 34, eine Ventilkolbenfeder 35 und eine Ausgleichsscheibe 36. Das Kopplergehäuse 31 liegt mit einem Bund 37 auf der Ventilplatte 12 auf. Am Bund 37 greift außerdem die Federhülse 32 an, auf der die Ausgleichsscheibe 36 aufliegt. Auf der Ausgleichsscheibe 36 stützt sich der Kopplerkolben 33 mit einem Kopplerkolbenbund 38 ab. Der Kopplerkolben 33 und der Ventilkolben 34 sind in am Kopplergehäuse 31 ausgebildeten Führungen jeweils geführt. Die in das Kopplergehäuse 31 weisenden Stirnflächen des Kopplerkolbens 33 und des Ventilkolbens 34 sind beabstandet zueinander angeordnet, so dass sich zwischen den Stirnflächen ein Kopplerspalt 39 ausbildet, der über in den Führungen des Kopplerkolbens 31 und des Ventilkolbens 34 vorhandenen Leckspalte mit dem hydraulischen Medium gefüllt ist. Dadurch wirkt das Kopplermodul 30 mit dem Kopplerspalt 39 als hydraulischer Koppler zum Ausgleich von Längendehnungen des Piezo-Aktors 25. Das Kopplergehäuse 31 weist an der ventilgliedseitigen Ende einen Befüllungsraum 47 in den der Ventilkolben 34 hineinragt und in dem die Ventilkolbenfeder 35 angeordnet ist.The coupler module 30 comprises according to FIG. 1 and 2 a coupler housing 31, a spring sleeve 32, a coupler piston 33, a valve piston 34, a valve piston spring 35 and a shim 36. The coupler housing 31 rests with a collar 37 on the valve plate 12. At the collar 37 also engages the spring sleeve 32, on which the shim 36 rests. On the shim 36, the coupler piston 33 is supported with a Kopplerkolbenbund 38. The coupler piston 33 and the valve piston 34 are guided in guides formed on the coupler housing 31, respectively. The pointing in the coupler housing 31 End faces of the coupler piston 33 and the valve piston 34 are spaced from each other, so that between the end faces of a coupler gap 39 is formed, which is filled in the guides of the coupler piston 31 and the valve piston 34 existing leakage gaps with the hydraulic medium. As a result, the coupler module 30 with the coupler gap 39 acts as a hydraulic coupler to compensate for elongations of the piezoactuator 25. The coupler housing 31 has at the valve member end a filling chamber 47 into which the valve piston 34 protrudes and in which the valve piston spring 35 is arranged.

Zwischen Kopplerkolben 33 und Aktorkopf 26 ist ein Einstellstück 28 angeordnet, auf dem der Aktorkopf 26 mit einer kugelförmigen Auflage 29 aufliegt.Between coupler piston 33 and actuator head 26, an adjusting piece 28 is arranged, on which the actuator head 26 rests with a spherical bearing 29.

Bei der Ausführungsform des Standes der Technik gemäß Figur 1 ist an dem in den Befüllungsraum 47 hineinragenden ventilgliedseitigen Endabschnitt des Ventilkolbens 34 eine Hülse 48 aufgepresst, an der sich die Ventilkolbenfeder 35 ventilkolbenseitig stützt. Das Gegenlager für die Ventilkolbenfeder 35 bildet eine Ringfläche 49 am Kopplergehäuse 31.In the embodiment of the prior art according to FIG. 1 is on the projecting into the filling chamber 47 valve member end portion of the valve piston 34, a sleeve 48 is pressed, at which the valve piston spring 35 is supported on the valve piston side. The counter bearing for the valve piston spring 35 forms an annular surface 49 on the coupler housing 31st

In der Ventilplatte 12 ist gemäß Figur 1 und 2 ein Ventilglied 40 mit einem Ventilelement 41 angeordnet. Das Ventilelement 41 ist in einer Ventilkammer 42 gelagert und wird mittels einer Ventilfeder 43 gegen einen Ventilsitz 44 gehalten. Auf das Ventilelement 41 wirkt ein am Ventilkolben 34 ausgebildeter Ventilstempel 45 ein, mit dem das Ventilelement 41 vom Ventilsitz 44 abgedrückt werden kann. Der Ventilkolben 34 ist mittels der Ventilkolbenfeder 35 in Richtung auf das Ventilelement 41 vorgespannt.In the valve plate 12 is according to FIG. 1 and 2 a valve member 40 is arranged with a valve element 41. The valve element 41 is mounted in a valve chamber 42 and is held by a valve spring 43 against a valve seat 44. On the valve element 41, a valve piston formed on the valve piston 34 acts 45, with which the valve element 41 can be pushed off the valve seat 44. The valve piston 34 is biased by the valve piston spring 35 in the direction of the valve element 41.

Bei dem in Figur 2 und 3 dargestellten erfindungsgemäßen Kopplermodul 40 weist der Ventilkolben 34 an einem ventilgliedseitigen Endabschnitt eine Einkerbung 50 auf. Dei Einkerbung 50 bildet am Ventilkolben 34 eine Auflage für die Ventilkolbenfeder 35 aus. Gemäß Figur 2 ist die Auflage durch einen umlaufenden Einstich 51 mit einer konischen Fläche 52 und einer Auflagefläche 53 ausgeführt. Die Ventilkolbenfeder 35 ist bei der erfindungsgemäßen Ausführungsform gemäß Figur 2 und 3 als eine konisch gewickelte Ventilkolbenfeder 54 mit einem kleinen Wickeldurchmesser d1 und einem großen Wickeldurchmesser d2 ausgeführt. Der Einkerbung 50 bzw. dem Einstich 51 ist ventilelementseitig am Ventilkolben 34 ein weiterer konischer Abschnitt 55 vorgelagert. Der vorgelagerte konischer Abschnitt 55 dient als Einführschräge für die konisch gewickelte Ventilkolbenfeder 54 bei der Montage des Kopplermoduls 40, wie später noch näher beschrieben wird. Die Auflagefläche 53 bildet eine Ringfläche, die in einfachster Ausführung eben und orthogonal zur Mittelachse des Ventilkolbens 34 verläuft. In vorteilhafter Weise kann die ringförmige Auflagefläche 53 aber auch leicht konisch ausgeführt sein, und zwar derart, dass die Auflagefläche 53 in Richtung der Mittelachse des Ventilkolbens 34 zum ventilseitigen Ende des Ventilkobens 34 hin leicht gekippt ist bzw. zum aktorseitigen Ende des Ventilkolbens 34 hin geöffnet ist. Dadurch rastet die konisch gewickelte Ventilkolbenfeder 54 besser im in der Einkerbung 50 bzw. im Einstich 51 ein. Vorteilhaft ist weiterhin, wenn die Symmetrieachse des Kegels parallel zur Mittellinie des Ventilkolbens 34 verläuft, wobei der Kegelwinkel vorzugsweise einen Winkel kleiner als 180° und größer als 60° aufweist.At the in FIG. 2 and 3 illustrated coupler module 40 according to the invention, the valve piston 34 has a notch 50 on a valve member-side end portion. The indentation 50 forms on the valve piston 34 a support for the valve piston spring 35. According to FIG. 2 the support is executed by a circumferential recess 51 with a conical surface 52 and a support surface 53. The valve piston spring 35 is according to the embodiment according to the invention FIG. 2 and 3 designed as a conically wound valve piston spring 54 with a small winding diameter d1 and a large winding diameter d2. The indentation 50 or the recess 51 is preceded by a further conical section 55 on the valve element side on the valve piston 34. The upstream conical section 55 serves as an insertion bevel for the conically wound valve piston spring 54 during assembly of the coupler module 40, as will be described in more detail later. The bearing surface 53 forms an annular surface, which in the simplest embodiment is flat and orthogonal to the central axis of the valve piston 34. In an advantageous manner, the annular bearing surface 53 may also be slightly conical, in such a way that the bearing surface 53 is slightly tilted in the direction of the central axis of the valve piston 34 toward the valve end of the Ventilkobens 34 or open to the actuator end of the valve piston 34 back is. As a result, the conically wound valve piston spring 54 engages better in the notch 50 or in the recess 51. It is furthermore advantageous if the axis of symmetry of the cone runs parallel to the center line of the valve piston 34, wherein the cone angle preferably has an angle of less than 180 ° and greater than 60 °.

Bei der Montage des Kopplermoduls 30 wird die konisch gewickelte Ventilkolbenfeder 54 mit dem großen Wickeldurchmesser d2 voran über den weiteren konischen Abschnitt 55 geschoben, so dass der kleine Wickeldurchmesser d1 der konisch gewickelten Ventilkolbenfeder 54 sich am weiteren konischen Abschnitt 55 geringfügig aufweitet und beim Überschreiten des weiteren konischen Abschnitts 55 durch die beim Aufschieben entstehenden Vorspannung in die Einkerbung 50 bzw. den Einstich 51 einrastet. Dadurch liegt die konisch gewickelte Ventilfeder 54 mit dem kleinen Wickeldurchmesser d1 auf der Auflage 52 der Einkerbung 50 auf. Die Auflage 52 bildet somit das ventilkolbenseitige Wiederlager für die Ventilkolbenfeder 54. Das Gegenlager für den großen Wickeldurchmesser d2 die Ventilkolbenfeder 54 bildet, wie beim Stand der Technik gemäß Figur 1 die am Kopplergehäuse 31 ausgebildete Ringfläche 49.When mounting the coupler module 30, the conically wound valve piston spring 54 is pushed with the large winding diameter d2 ahead of the other conical portion 55, so that the small winding diameter d1 of the conically wound valve piston spring 54 at the further conical portion 55 slightly widens and when crossing the other conical section 55 engages in the notch 50 and the groove 51 by the resulting pre-tension during insertion. As a result, the conically wound valve spring 54 with the small winding diameter d1 rests on the support 52 of the notch 50. The support 52 thus forms the valve piston-side abutment for the valve piston spring 54. The abutment for the large winding diameter d2, the valve piston spring 54 forms, as in the prior art according to FIG. 1 the annular surface 49 formed on the coupler housing 31.

Die Funktionsweise des Kraftstoffinjektors von Figur 1 und 2 ist folgendermaßen: Beim Betätigen des Piezo-Aktors 25 längt dieser aus. Der dadurch entstehende Druck wird über den Kopplerkolben 33, den Kopplerspalt 39 und den Ventilkolben 34 übertragen, wobei der Ventilkolben 34 mit dem Ventilstempel 45 das Ventilelement 41 vom Ventilsitz 44 wegdrückt. Dadurch wird der Hub des Piezo-Aktors 35 auf das Ventilelement 41 übertragen und es entsteht am Ventilsitz 44 ein entsprechender Ventilsitzspalt, so dass ein geöffneter Zustand des Ventilelements 41 erzeugt wird. In dieser Schaltstellung wird eine zwischen Ventilkammer 42 und Steuerraum 20 vorhandener, nicht dargestellte Ablaufbohrung mit einem ebenfalls nicht gezeigten Ablaufkanal hydraulisch verbunden, wobei der Ablaufkanal in den Aufnahmeraum 16 mündet, der wiederum mit einem Niederdruck/Rücklaufsystem hydraulisch verbunden ist. Dadurch wird der Steuerraum 20 druckentlastet und die in Öffnungsrichtung an der nicht dargestellten Druckschulter der Düsennadel 19 wirkenden Öffnungskräfte übersteigen die im Steuerraum 20 wirkenden Schließkräfte, so dass der Kraftstoff aus dem Düsennadeldruckraum 18 mit Systemdruck des Common-Rails eingespritzt wird.The operation of the fuel injector of FIG. 1 and 2 is as follows: When actuating the piezo actuator 25, this lengthens. The resulting pressure is transmitted via the coupler piston 33, the coupler gap 39 and the valve piston 34, wherein the valve piston 34 with the valve stem 45, the valve element 41 from the valve seat 44 pushes away. As a result, the stroke of the piezoactuator 35 is transmitted to the valve element 41 and arises at the valve seat 44 a corresponding valve seat gap, so that an open state of the valve element 41 is generated. In this switching position between a valve chamber 42 and the control chamber 20 existing, not shown drain hole is hydraulically connected to a drain channel, also not shown, the drain channel opens into the receiving space 16, which in turn is hydraulically connected to a low pressure / return system. As a result, the control chamber 20 is relieved of pressure and acting in the opening direction of the pressure shoulder of the nozzle needle 19 opening forces exceed the forces acting in the control chamber 20 closing forces, so that the fuel from the nozzle needle pressure chamber 18 is injected with system pressure of the common rail.

Claims (7)

  1. Control valve for controlling liquids, in particular for a fuel injector of an internal combustion engine, having an actuator unit (25) which acts via a coupler module (30) on a valve element (41) which interacts with a valve seat (44) and which, in the closed position, blocks a fluid flow from a valve chamber (42) to a return flow duct, the coupler module (30) being guided in a coupler housing (31) and having a coupler piston (33) and a valve piston (34), an actuator head (26) of the actuator unit (25) acting on the coupler piston (33) and a valve plunger (45) of the valve piston (34) acting on the valve element (41), the valve piston (34) being preloaded against the valve element (41) by means of a valve piston spring (35), and the valve piston spring (35) being supported at the actuator side on the coupler housing (31) and at the valve element side on the valve piston (34), characterized in that the valve piston (34) has a notch (50) which forms a support on the valve piston for the valve piston spring (35).
  2. Control valve according to Claim 1, characterized in that the valve piston spring (35) is designed as a conically wound valve piston spring (54) and in that the conically wound valve piston spring (54) is supported with the small winding diameter d1 in the notch (50).
  3. Control valve according to Claim 2, characterized in that the notch (50) is formed as an encircling recess (51) with a conical section (52) and with an annular support surface (53) for the conically wound valve piston spring (54).
  4. Control valve according to Claim 2 or 3, characterized in that the small winding diameter d1 of the conically wound valve piston spring (54) is dimensioned such that the conically wound valve piston spring (54) latches with the small winding diameter d1 in the notch (50) or in the recess (51).
  5. Control valve according to Claim 3, characterized in that the annular support surface (53) is planar and is aligned orthogonally with respect to the central axis of the valve piston (34).
  6. Control valve according to Claim 3, characterized in that the annular support surface (53) is of conical design, in such a way that the conical support surface opens in the direction of the actuator-side end of the valve piston (34).
  7. Control valve according to one of the preceding claims, characterized in that a further conical section (55) is positioned on the valve piston (34) in front of the notch (50) or the recess (51) at the valve element side, which further conical section (55) forms an insertion bevel for the conically wound valve piston spring (54) such that the valve piston spring (35) latches into the notch (50) or into the recess (51).
EP08760982A 2007-07-11 2008-06-13 Control valve, particularly for a fuel injector of an internal combustion engine Not-in-force EP2165069B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007032219A DE102007032219A1 (en) 2007-07-11 2007-07-11 Control valve, in particular for a fuel injector of an internal combustion engine
PCT/EP2008/057450 WO2009007195A1 (en) 2007-07-11 2008-06-13 Control valve, particularly for a fuel injector of an internal combustion engine

Publications (2)

Publication Number Publication Date
EP2165069A1 EP2165069A1 (en) 2010-03-24
EP2165069B1 true EP2165069B1 (en) 2011-04-20

Family

ID=39769060

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08760982A Not-in-force EP2165069B1 (en) 2007-07-11 2008-06-13 Control valve, particularly for a fuel injector of an internal combustion engine

Country Status (4)

Country Link
EP (1) EP2165069B1 (en)
AT (1) ATE506531T1 (en)
DE (2) DE102007032219A1 (en)
WO (1) WO2009007195A1 (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010029607A1 (en) 2010-06-02 2011-12-08 Robert Bosch Gmbh Fuel injector comprises hydraulic coupling module, which has coupling piston and valve piston, which is axially guided in common coupling body, where supply of supply line is interconnected with high pressure line

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB533709A (en) * 1938-08-13 1941-02-19 Daimler Benz Ag Improvements in liquid pumps
DE10203655A1 (en) * 2002-01-30 2004-01-22 Robert Bosch Gmbh Fuel injector
DE10322672A1 (en) 2003-05-20 2004-12-09 Robert Bosch Gmbh Valve for controlling liquids

Also Published As

Publication number Publication date
DE102007032219A1 (en) 2009-01-15
DE502008003288D1 (en) 2011-06-01
ATE506531T1 (en) 2011-05-15
WO2009007195A1 (en) 2009-01-15
EP2165069A1 (en) 2010-03-24

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