EP1718862B1 - Fuel injection valve for internal combustion engines - Google Patents

Fuel injection valve for internal combustion engines Download PDF

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Publication number
EP1718862B1
EP1718862B1 EP05706519A EP05706519A EP1718862B1 EP 1718862 B1 EP1718862 B1 EP 1718862B1 EP 05706519 A EP05706519 A EP 05706519A EP 05706519 A EP05706519 A EP 05706519A EP 1718862 B1 EP1718862 B1 EP 1718862B1
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EP
European Patent Office
Prior art keywords
control
injection valve
fuel injection
housing
valve according
Prior art date
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Application number
EP05706519A
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German (de)
French (fr)
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EP1718862A1 (en
Inventor
Marco Ganser
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Ganser Hydromag AG
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Ganser Hydromag AG
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Publication of EP1718862A1 publication Critical patent/EP1718862A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/168—Assembling; Disassembling; Manufacturing; Adjusting
    • 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
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
    • 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
    • F02M2200/16—Sealing of fuel injection apparatus not otherwise provided for
    • 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing

Definitions

  • the present invention relates to a fuel injection valve for intermittent fuel injection into the combustion chamber of an internal combustion engine according to the preamble of claim 1 such as in US 5 685 483 A disclosed.
  • An injector for fuel injection in which an annular gap is formed between an injector body and a throttle module inserted therein and designed as a separate component.
  • plastically deformable cutting edges are provided on the throttle module, which are pressed during the assembly of the throttle module to stages in the injector.
  • a control chamber is limited on the one hand by a spring plate, which is loose, that is not sealing, arranged in a bore of a nozzle body.
  • This spring plate is pressed by the pressure prevailing in the high pressure chamber of the valve and the force of a spring against a counter body.
  • the present invention is based on the object to provide a fuel injection valve of the type mentioned, in which the manufacture and installation of the control body in the housing in comparison to the known fuel injection valves is simpler and therefore less expensive.
  • control body is no longer pressed as in the prior art in the housing, but loose and not sealingly inserted into the opening in the housing. This allows easy installation and removal of the control body. Furthermore, the control body can be produced more cost-effectively, since the dimensional accuracy and the machining quality do not have to be so demanding.
  • the sealing of the high-pressure chamber with respect to the low-pressure chamber is ensured on the one hand by the interaction of sealing surfaces on the control body and on the holding body and on the other hand by the concern of a further sealing surface on the holding body on a seat formed on the housing.
  • fuel injector 1 has a housing 2, which is formed by an upper housing part 2a and a valve seat member 2b.
  • the valve seat element 2b is tightly connected to the upper housing part 2a by means of a holding element 3 designed as a clamping nut.
  • the valve seat element 2b has a valve seat 4 and injection openings 5.
  • a central, coaxial to the longitudinal axis A of the housing 2 bore 6 is formed over its length changing diameter, which defines a high-pressure chamber 7.
  • This high-pressure chamber 7 communicates with a high-pressure fuel inlet 8 and extends to the valve seat 4.
  • the housing longitudinal axis A coaxial injection valve member 9 is arranged, which in the in the FIG. 1 shown closed position with its tip with the valve seat 4 cooperates to close the injection openings 5.
  • the injection valve member 9 by means of a hydraulic control device 10, whose construction on hand Figures 2 and 3 will be explained in more detail, lifted off the valve seat 4.
  • the injection valve member 9 is guided by means of a narrow slide fit in the valve seat element 2b with a section designed as a guide 9a.
  • the injection valve member 9 is provided with grinding surfaces in the region of this guide 9a.
  • the injection valve member 9 is pressed by means of a closing spring 11 in the closing direction down.
  • the closing spring 11 is supported at its lower end on a support ring 12 which rests on a shoulder 13 on the injection valve member 9. At the other end, the closing spring 11 is supported on a spacer sleeve 14 surrounding the injection valve member 9.
  • the relatively long, hollow cylindrical spacer sleeve 14 spans the region of the confluence of the fuel high pressure inlet 8 in the central bore 6 and is guided at their ends by means of guide surfaces 15, 16 on the wall of the bore 6 ( Fig. 2 ).
  • the clearance between the guide surface 15, 16 and the wall of the bore 6 is between 1/100 and 1/10 mm.
  • the spacer sleeve 14 has a smaller diameter, so that between the wall of the bore 6 and the outer periphery of the spacer sleeve, an annular space 17 is formed, which with the Fuel high pressure inlet 8 is in communication.
  • the spacer sleeve 14 is provided with passage openings 18, can pass through the fuel from the annular space 17 into the interior of the spacer sleeve 14.
  • a stop shoulder 19 is formed which serves as a stop for the spacer sleeve 14 with a displacement of the same upward and cooperate with a formed at the lower end of the spacer sleeve 14 stop surface 20 is determined ( Fig. 2 ).
  • the spacer sleeve 14 presses against a hollow cylindrical guide sleeve 21 belonging to the hydraulic control device 10, which is guided at the upper end by means of a guide surface 22 in the central bore 6.
  • annular space 23 is present, which is connected via passages 24, which are provided at the lower end of the guide sleeve 21 or at the upper end of the spacer sleeve 14, with the interior of the spacer sleeve 14 and the high-pressure chamber. 7 belongs.
  • the injection valve member 9 has a double-acting control piston 25, which is guided in the guide sleeve 21 in a close sliding fit.
  • the control piston 25 is acted upon on its underside by the high fuel pressure in the high-pressure chamber 7 and limited with its upper side a control chamber 26 which is bounded laterally by the guide sleeve 21.
  • an intermediate valve body 27 which in the direction the longitudinal axis A is displaceable and has a lower end face 27a.
  • the intermediate valve body 27 is guided in the guide sleeve 21 with a play of typically 0.03 to 0.2 millimeters.
  • In the intermediate valve body 27 extends a coaxial to the longitudinal axis A throttle passage 31, which extends between the lower and upper end face 27 a, 27 b of the intermediate valve body 27.
  • a spring element 28 is arranged, which is supported on the one hand on the intermediate valve body 27 and on the other hand on a support member 29 which rests on an annular shoulder 30 on the guide sleeve 21 ( Fig. 3 ).
  • the spring element 28 surrounds a central projection 25a of the control piston 25 and generates on the intermediate valve body 27 a force which is substantially smaller than the force exerted by the closing spring 11 force.
  • the lower end face 27a of the intermediate valve body 27 is arranged at a distance a from the upper side 29a of the support element 29 (see FIG FIG. 3 ).
  • the support member 29 serves as the movement of the intermediate valve body 27 downwardly limiting stop.
  • the support element 29 could also be integral with the guide sleeve 21 and formed with the latter as a workpiece.
  • the upper end face 27b of the intermediate valve body 27 is located on a lower, serving as a sealing surface end face 32a of a control body 32 which is loosely, that is not arranged in the central bore 6.
  • the lower end 32a of the control body 32 seals together with the top 21a of the guide sleeve 21 from the control chamber 26 with respect to the high-pressure chamber 7 from.
  • the control body 32 is located at a upper end face 32b on the underside 33a of a holding body 33 at.
  • the holding body 33 is screwed by means of an external thread 34 into a recess 35 in the housing 2.
  • the holding body 33 is provided with countersunk holes 36, which serve to insert a tool for screwing and tightening the holding body 33 (see also FIG. 4 ).
  • the holding body 33 is screwed so tightly into the housing recess 35 that it rests with a formed on its underside 33 a, first annular sealing surface 37 on a seat 38 which is formed at the bottom of the recess 35 in the housing 2 and the central bore 6 surrounds.
  • first sealing surface 37 of the holding body 33 includes a second, also annular sealing surface 39, which lies in the same plane as the first sealing surface 37.
  • second sealing surface 39 is formed on the upper end face 32b of the control body 32 sealing surface 40 at.
  • the sealing surfaces 37, 38, 39 and 40 preferably close close to the circumference of the bore 6.
  • the sealing surfaces 37 and 39 of the holding body 33 are advantageously formed on a single planar end face of the holding body 33.
  • the control body 32 has a coaxial with the longitudinal direction A extending, continuous control passage 41 which has a throttle restriction 42 at its opening into the upper end face 32b of the control body 32 end.
  • the control passage 41 is in hydraulic communication with the throttle passage 31 in the inter-valve body 27.
  • the sealing surface 40 on the upper end face 32b of the control body 32 surrounds the control passage 41.
  • passages 43 are further formed, which are offset laterally relative to the control passage 41 and which open into the lower end face 32a of the control body 32.
  • the passages 43 are connected to an annular groove 44 on the outer circumference of the control body 32 in connection, which is connected to the annular space 23 and in which therefore the high fuel pressure prevails.
  • an electromagnetically actuated pilot valve 45 is housed in the housing 2, which has a displaceable valve stem 46 and a separate therefrom closure body 47 which rests between the injections on serving as a valve seat surface upper end face 32b of the control body 32 and the Closes control passage 41.
  • a pilot valve spring 48 On the valve stem 46 and thus also on the closure body 47 acts a pilot valve spring 48, which presses the closure body 47 to the upper end face 32b of the control body 32.
  • an electromagnet arrangement 49 is present, which consists of a magnetic body 50 with a magnetic coil 51 and a magnet armature 52.
  • the valve stem 46 is fixedly connected to the armature 52 and is slidably guided in the magnet body 50.
  • the holding body 33 has in addition to the countersunk holes 36 and a central bore 53 (see also FIG. 4 ), in the valve stem 46 extends and in which the closure body 47 is guided displaceably.
  • this central bore 53 projects into a stop shoulder 54, which engages in an annular groove 55 on the valve stem 46.
  • the maximum stop stroke b of the valve stem 46 is smaller than the distance c between the armature 52 and the magnet body 50, so that even when the open pilot valve 45 of Magnetic armature 52 is not applied to the magnetic body 50.
  • the stop shoulder 54 for the valve stem 46 is outside the effective magnetic field of the solenoid assembly 49th
  • valve stem 46 In order to use the valve stem 46 in the holding body 33, the latter is provided with an eccentrically arranged recess 56 which is open to the central bore 53.
  • the valve stem 46 is laterally offset relative to the axis of the central bore 53 inserted into the recess 56. If the annular groove 55 of the valve stem 46 is at the level of the stop shoulder 54, the valve stem 46 is displaced transversely into the central bore 53.
  • the closure body 47 guided loosely in the bore 53 serves, in addition to closing the control passage 41, to precisely set the stroke b of the valve stem 46.
  • the closure body 47 By inserting a closure body 47 of a certain height, the size of the stroke b can be set precisely. If such an accurate adjustment should not be necessary - which may be the case, for example, in another embodiment of the stroke limitation of the valve stem 46 - the closure body 47 can be dispensed with.
  • the control passage 41 is directly through the valve stem 46 is closed, as for example from the EP-A-1 273 791 is known.
  • the lower, crowned end 46a of the valve stem 46 acts on the flat upper end face 47b of the closure body 47 (FIG. Fig. 3 ).
  • the upper end surface 47b of the closure body 47 could be crowned and cooperate with a flat end surface 46a of the valve stem 46. In both cases, the tightness of the pilot valve 45 is improved.
  • the central bore 53 and the recess 56 in the holding body 33 belong to a low-pressure chamber 57 which is connected to a low-pressure outlet 58 (FIG. Fig. 1 and 2 ) is fluidly connected. From this low pressure outlet 58, a line, not shown, leads back to a fuel reservoir.
  • the closure body 47 is provided with longitudinal grooves 47a which allow a fuel flow from the control passage 41 into the low-pressure space 57 when the closure body 47 is lifted off the control body 32.
  • the annular groove 44 in the control body 32 of the high fuel pressure which may be 2000 bar and more.
  • the first sealing surface 37 of the holding body 33 screwed into the housing 2 is sealingly connected to the annular groove 44 belonging to the high pressure chamber 7
  • Seat 38 pressed in the housing 2.
  • the control body 32 is pressed by the fuel pressure in the high pressure chamber 7 with its sealing surface 40 against the other sealing surface 39 on the holding body 33. At the surface quality of the sealing surfaces 37, 39 and 40 and the seat 38 are not made too high demands.
  • the functioning of the in the Figures 1 - 3 The fuel injection valve 1 shown is as follows: Starting from the state shown in these figures, in which the injection valve member 9 is in the closed position and the intermediate valve body 27 sealingly abuts the control body 32. The solenoid assembly 49 is not energized and the closure body 47 closes the control passage 41. In the control chamber 26, the same pressure prevails as in the high pressure chamber. 7
  • an injection cycle is triggered.
  • the magnetic armature 52 is pulled against the magnetic body 50, with the result that the valve stem 46 lifts off from the closure body 47.
  • the closure body 47 can now move upwards under the effect of the fuel pressure in the control passage 41 and releases the control passage 41.
  • the control passage 41 and thus also the control chamber 26 are now connected to the low-pressure chamber 57.
  • the pressure in the control chamber 26 begins to decrease.
  • the injection valve member 9 moves away from the valve seat 4 and releases the injection openings 5.
  • the injection process begins. In this case, fuel from the control chamber 26 through the Throttling passage 31 and the control passage 41 displaced in the low-pressure space 57.
  • the solenoid assembly 49 is de-energized. This has the consequence that under the force of the pilot valve spring 48 of the valve stem 46 and with it the closure body 47 are moved downward until the closure body 47 comes to rest on the control body 32.
  • the low-pressure side opening of the control passage 41 is closed by the closure body 47 again.
  • the pressure in the control passage 41 starts to increase. This, together with the fact that in the passages 43 in the control body 32 of the high fuel pressure, leads to a Wegbesselssel the intermediate valve body 27 away from the sealing contact with the control body 32.
  • the downward movement of the intermediate valve body 27 is terminated by abutting the top 29 a of the support member 29 , Characterized in that by moving away the intermediate valve body 27 from the control body 32, the passages 43 are opened in the control body 32 can flow through these passages 43 and the throttle passage 31 and along the entire circumference of the intermediate valve body 27 fuel under high pressure, resulting in the closing of the injection valve member. 9 strongly accelerated. As soon as the injection valve member 9 abuts the valve seat 4 again and closes the injection openings 5, the injection process is ended.
  • the spacer sleeve 14 transmits the force of the closing spring 11 via the guide sleeve 21 on the control body 32nd
  • the injection valve member 9 is inserted with the closing spring 11 and slipped spacer sleeve 14 in the valve seat member 2b, this sub-assembly is inserted into the upper housing part 2a and secured by means of the holding element 3 on the upper housing part 2a.
  • the stop shoulder 19 in the upper housing part 2 a limits the insertion path of the spacer sleeve 14 in the central bore 6, which greatly simplifies the assembly of the control body 32.
  • the support member 29 serves as mentioned as a stop for the intermediate valve body 27, whereby the Oe Albanysweg the intermediate valve body 27 is limited. This brings advantages in pre-injections with short time intervals.
  • control body 32 is loosely inserted into the central bore 6, no special requirements must be made of the control body 32 in terms of production and processing. In addition, the installation of the Control body 32 in the housing 2 comparatively simple. All this has a favorable effect on the costs.
  • the described special constructive solutions can also be used in fuel injection valves, in which the fuel supply to the valve seat via a relative to the housing longitudinal axis A laterally offset feed channel, as for example from US-A-5,775,301 is known.

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

Abstract

The movement of an injection valve member, which can be longitudinally displaced and guided in a housing and which is used to close and release injection openings, is controlled of a hydraulic control device which comprises a control body which is maintained in a central bore on the periphery thereof and which is provided with a control duct which is connected to a control area on a lower front-surface side of the control body and which is sealed on another upper front-surface side of the control body and which can be connected to a low pressure area by a pilot valve.

Description

Die vorliegende Erfindung betrifft ein Brennstoffeinspritzventil zur intermittierenden Brennstoffeinspritzung in den Brennraum einer Verbrennungskraftmaschine gemäss Oberbegriff des Anspruches 1 wie beispielsweise in US 5 685 483 A offenbart.The present invention relates to a fuel injection valve for intermittent fuel injection into the combustion chamber of an internal combustion engine according to the preamble of claim 1 such as in US 5 685 483 A disclosed.

Aus der EP-A-1 273 791 ist ein Brennstoffeinspritzventil dieser Art bekannt, bei dem der Steuerkörper mittels einer Schrumpfverbindung fest in einer Gehäusebohrung sitzt und so den Niederdruckraum vom Hochdruckraum abdichtet. Dies trifft auch auf das in der EP-B-0 426 205 offenbarte Brennstoffeinspritzventil zu. Das Einpressen des Steuerkörpers in die Gehäusebohrung erfordert einen gewissen montagetechnischen Aufwand.From the EP-A-1 273 791 a fuel injection valve of this type is known, in which the control body by means of a shrink fit sits firmly in a housing bore and thus seals the low-pressure chamber from the high-pressure chamber. This also applies to the in the EP-B-0 426 205 disclosed fuel injector too. The pressing of the control body in the housing bore requires a certain mounting technical effort.

In der WO-A-03/095825 ist ein Injektor zur Kraftstoffeinspritzung offenbart, bei dem zwischen einem Injektorkörper und einem in diesen eingesetzten, als separates Bauteil ausgebildeten Drosselmodul ein Ringspalt ausgebildet ist. Zur Abdichtung dieses Ringspaltes sind am Drosselmodul plastisch verformbare Schneidkanten vorgesehen, die bei der Montage des Drosselmoduls an Stufen im Injektorgehäuse angedrückt werden.In the WO-A-03/095825 An injector for fuel injection is disclosed, in which an annular gap is formed between an injector body and a throttle module inserted therein and designed as a separate component. To seal this annular gap plastically deformable cutting edges are provided on the throttle module, which are pressed during the assembly of the throttle module to stages in the injector.

Bei dem in der WO-A-02/084106 beschriebenen, nicht gattungsgleichen Kraftstoffeinspritzventil wird ein Steuerraum auf der einen Seite durch einen Federteller begrenzt, der lose, d. h. nicht dichtend, in einer Bohrung eines Düsenkörpers angeordnet ist. Dieser Federteller wird durch den im Hochdruckraum des Ventils herrschenden Druck und die Kraft einer Feder an einen Gegenkörper angedrückt. Der vorliegenden Erfindung liegt nun die Aufgabe zugrunde, ein Brennstoffeinspritzventil der eingangs genannten Art zu schaffen, bei dem die Herstellung und das Einbauen des Steuerkörpers in das Gehäuse im Vergleich zu den bekannten Brennstoffeinspritzventilen einfacher und damit kostengünstiger ist.In the in the WO-A-02/084106 described, not generic same fuel injector, a control chamber is limited on the one hand by a spring plate, which is loose, that is not sealing, arranged in a bore of a nozzle body. This spring plate is pressed by the pressure prevailing in the high pressure chamber of the valve and the force of a spring against a counter body. The present invention is based on the object to provide a fuel injection valve of the type mentioned, in which the manufacture and installation of the control body in the housing in comparison to the known fuel injection valves is simpler and therefore less expensive.

Diese Aufgabe wird erfindungsgemäss mit einem Brennstoffeinspritzventil mit den Merkmalen des Anspruches 1 gelöst.This object is achieved according to the invention with a fuel injection valve having the features of claim 1.

Der Steuerkörper ist nicht mehr wie beim Stand der Technik in das Gehäuse eingepresst, sondern lose und nicht dichtend in die Oeffnung im Gehäuse eingesetzt. Dies ermöglicht ein einfaches Ein- und Ausbauen des Steuerkörpers. Im Weiteren lässt sich der Steuerkörper kostengünstiger herstellen, da an die Massgenauigkeit und die Bearbeitungsqualität nicht so hohe Anforderungen gestellt werden müssen.The control body is no longer pressed as in the prior art in the housing, but loose and not sealingly inserted into the opening in the housing. This allows easy installation and removal of the control body. Furthermore, the control body can be produced more cost-effectively, since the dimensional accuracy and the machining quality do not have to be so demanding.

Die Abdichtung des Hochdruckraumes gegenüber dem Niederdruckraum wird einerseits durch das Zusammenwirken von Dichtflächen am Steuerkörper und am Haltekörper und andererseits durch das Anliegen einer weiteren Dichtfläche am Haltekörper an einer am Gehäuse ausgebildeten Sitzfläche sicher gestellt.The sealing of the high-pressure chamber with respect to the low-pressure chamber is ensured on the one hand by the interaction of sealing surfaces on the control body and on the holding body and on the other hand by the concern of a further sealing surface on the holding body on a seat formed on the housing.

Bevorzugte Weiterausgestaltungen des erfindungsgemässen Brennstoffeinspritzventils sind in den abhängigen Ansprüchen umschrieben.Preferred further developments of the fuel injection valve according to the invention are described in the dependent claims.

Im Folgenden wird unter Bezugnahme auf die Figuren ein Ausführungsbeispiel des Erfindungsgegenstandes näher erläutert. Es zeigt rein schematisch:

Fig. 1
im Längsschnitt ein Brennstoffeinspritzventil,
Fig. 2
im Längsschnitt und in im Vergleich zur Fig. 1 vergrössertem Massstab einen Teilbereich des Brennstoffeinspritzventils gemäss Fig. 1,
Fig. 3
im Längsschnitt und in im Vergleich zur Fig. 2 vergrössertem Massstab einen Teilbereich der Darstellung gemäss Fig. 2, und
Fig. 4
in einer perspektivischen Darstellung den Haltekörper des in den Fig. 1-3 gezeigten Brennstoffeinspritzventils.
In the following an embodiment of the subject invention is explained in detail with reference to the figures. It shows purely schematically:
Fig. 1
in longitudinal section a fuel injector,
Fig. 2
in longitudinal section and in comparison to Fig. 1 enlarged scale a portion of the fuel injection valve according to Fig. 1 .
Fig. 3
in longitudinal section and in comparison to Fig. 2 enlarged scale a portion of the representation according to Fig. 2 , and
Fig. 4
in a perspective view of the holding body of the in the Fig. 1-3 shown fuel injector.

Das in der Figur 1 schematisch im Längsschnitt dargestellte Brennstoffeinspritzventil 1 weist ein Gehäuse 2 auf, das durch einen oberen Gehäuseteil 2a und ein Ventilsitzelement 2b gebildet ist. Das Ventilsitzelement 2b ist mittels eines als Spannmutter ausgebildeten Halteelements 3 mit dem oberen Gehäuseteil 2a dicht verbunden.That in the FIG. 1 schematically illustrated in longitudinal section fuel injector 1 has a housing 2, which is formed by an upper housing part 2a and a valve seat member 2b. The valve seat element 2b is tightly connected to the upper housing part 2a by means of a holding element 3 designed as a clamping nut.

Das Ventilsitzelement 2b weist einen Ventilsitz 4 sowie Einspritzöffnungen 5 auf. Im Innern des Gehäuses 2 ist eine zentrale, zur Längsachse A des Gehäuses 2 koaxiale Bohrung 6 mit sich über ihre Länge änderndem Durchmesser ausgebildet, die einen Hochdruckraum 7 festlegt. Dieser Hochdruckraum 7 steht mit einem Brennstoffhochdruckeinlass 8 in Verbindung und erstreckt sich bis zum Ventilsitz 4 hin.The valve seat element 2b has a valve seat 4 and injection openings 5. In the interior of the housing 2, a central, coaxial to the longitudinal axis A of the housing 2 bore 6 is formed over its length changing diameter, which defines a high-pressure chamber 7. This high-pressure chamber 7 communicates with a high-pressure fuel inlet 8 and extends to the valve seat 4.

Im Innern des Gehäuses 2, d.h. in der Bohrung 6, ist ein als Ventilnadel ausgebildetes, zur Gehäuselängsachse A koaxiales Einspritzventilglied 9 angeordnet, das in der in der Figur 1 gezeigten Schliessstellung mit seiner Spitze mit dem Ventilsitz 4 zusammenwirkt, um die Einspritzöffnungen 5 zu verschliessen. Zum Freigeben der Einspritzöffnungen 5 wird das Einspritzventilglied 9 mittels einer hydraulischen Steuervorrichtung 10, deren Aufbau an Hand der Figuren 2 und 3 näher erläutert werden wird, vom Ventilsitz 4 abgehoben. Das Einspritzventilglied 9 ist mit einem als Führung 9a ausgebildeten Teilstück mittels einer engen Gleitpassung im Ventilsitzelement 2b geführt. Zur Gewährleistung einer hydraulischen Verbindung ist das Einspritzventilglied 9 im Bereich dieser Führung 9a mit Anschliffflächen versehen. Das Einspritzventilglied 9 wird mittels einer Schliessfeder 11 in Schliessrichtung nach unten gedrückt. Die Schliessfeder 11 stützt sich an ihrem unteren Ende auf einem Stützring 12 ab, der auf einer Schulter 13 am Einspritzventilglied 9 aufliegt. Am anderen Ende ist die Schliessfeder 11 an einer das Einspritzventilglied 9 umgebenden Distanzhülse 14 abgestützt.In the interior of the housing 2, that is, in the bore 6, a formed as a valve needle, the housing longitudinal axis A coaxial injection valve member 9 is arranged, which in the in the FIG. 1 shown closed position with its tip with the valve seat 4 cooperates to close the injection openings 5. To release the injection openings 5, the injection valve member 9 by means of a hydraulic control device 10, whose construction on hand Figures 2 and 3 will be explained in more detail, lifted off the valve seat 4. The injection valve member 9 is guided by means of a narrow slide fit in the valve seat element 2b with a section designed as a guide 9a. To ensure a hydraulic connection, the injection valve member 9 is provided with grinding surfaces in the region of this guide 9a. The injection valve member 9 is pressed by means of a closing spring 11 in the closing direction down. The closing spring 11 is supported at its lower end on a support ring 12 which rests on a shoulder 13 on the injection valve member 9. At the other end, the closing spring 11 is supported on a spacer sleeve 14 surrounding the injection valve member 9.

Die verhältnismässig lange, hohlzylindrische Distanzhülse 14 überspannt den Bereich der Einmündung des Brennstoffhockdruckeinlasses 8 in die zentrale Bohrung 6 und ist an ihren Enden mittels Führungsflächen 15, 16 an der Wand der Bohrung 6 geführt (Fig. 2). Dabei beträgt das Spiel zwischen der Führungsfläche 15, 16 und der Wand der Bohrung 6 zwischen 1/100 und 1/10 mm. Zwischen ihren mit den Führungsflächen 15, 16 versehenen Enden hat die Distanzhülse 14 einen kleineren Durchmesser, so dass sich zwischen der Wand der Bohrung 6 und dem Aussenumfang der Distanzhülse ein Ringraum 17 bildet, der mit dem Brennstoffhochdruckeinlass 8 in Verbindung steht. Die Distanzhülse 14 ist mit Durchlassöffnungen 18 versehen, durch die Brennstoff aus dem Ringraum 17 ins Innere der Distanzhülse 14 treten kann.The relatively long, hollow cylindrical spacer sleeve 14 spans the region of the confluence of the fuel high pressure inlet 8 in the central bore 6 and is guided at their ends by means of guide surfaces 15, 16 on the wall of the bore 6 ( Fig. 2 ). The clearance between the guide surface 15, 16 and the wall of the bore 6 is between 1/100 and 1/10 mm. Between their provided with the guide surfaces 15, 16 ends the spacer sleeve 14 has a smaller diameter, so that between the wall of the bore 6 and the outer periphery of the spacer sleeve, an annular space 17 is formed, which with the Fuel high pressure inlet 8 is in communication. The spacer sleeve 14 is provided with passage openings 18, can pass through the fuel from the annular space 17 into the interior of the spacer sleeve 14.

Im Gehäuse 2 ist eine Anschlagschulter 19 ausgebildet, die als Anschlag für die Distanzhülse 14 bei einer Verschiebung derselben nach oben dient und mit einer am unteren Ende der Distanzhülse 14 ausgebildeten Anschlagfläche 20 zusammenzuwirken bestimmt ist (Fig. 2). An ihrem oberen Ende drückt die Distanzhülse 14 gegen eine zur hydraulischen Steuervorrichtung 10 gehörenden hohlzylindrischen Führungshülse 21, die am oberen Ende mittels einer Führungsfläche 22 in der zentralen Bohrung 6 geführt ist. Zwischen der Führungshülse 21 und der Wand der Bohrung 6 ist ein Ringraum 23 vorhanden, der über Durchlässe 24, die am unteren Ende der Führungshülse 21 oder am oberen Ende der Distanzhülse 14 vorgesehen sind, mit dem Inneren der Distanzhülse 14 verbunden ist und zum Hochdruckraum 7 gehört.In the housing 2, a stop shoulder 19 is formed which serves as a stop for the spacer sleeve 14 with a displacement of the same upward and cooperate with a formed at the lower end of the spacer sleeve 14 stop surface 20 is determined ( Fig. 2 ). At its upper end, the spacer sleeve 14 presses against a hollow cylindrical guide sleeve 21 belonging to the hydraulic control device 10, which is guided at the upper end by means of a guide surface 22 in the central bore 6. Between the guide sleeve 21 and the wall of the bore 6, an annular space 23 is present, which is connected via passages 24, which are provided at the lower end of the guide sleeve 21 or at the upper end of the spacer sleeve 14, with the interior of the spacer sleeve 14 and the high-pressure chamber. 7 belongs.

Im folgenden werden unter Bezugnahme auf die Figuren 2 und 3 weitere Elemente der hydraulischen Steuervorrichtung 10 beschrieben.The following are with reference to the Figures 2 and 3 further elements of the hydraulic control device 10 described.

An seinem dem Ventilsitz 4 gegenüberliegenden Ende weist das Einspritzventilglied 9 einen doppelt wirkenden Steuerkolben 25 auf, der in der Führungshülse 21 in einer engen Gleitpassung geführt ist. Der Steuerkolben 25 wird auf seiner Unterseite vom Brennstoffhochdruck im Hochdruckraum 7 beaufschlagt und begrenzt mit seiner Oberseite einen Steuerraum 26, der seitlich durch die Führungshülse 21 begrenzt ist. In der Führungshülse 21 befindet sich ein Zwischenventilkörper 27, der in Richtung der Längsachse A verschiebbar ist und eine untere Stirnseite 27a aufweist. Der Zwischenventilkörper 27 ist in der Führungshülse 21 mit einem Spiel von typischerweise 0,03 bis 0,2 Millimeter geführt. Im Zwischenventilkörper 27 verläuft ein zur Längsachse A koaxialer Drosseldurchlass 31, der sich zwischen der unteren und oberen Stirnseite 27a, 27b des Zwischenventilkörpers 27 erstreckt.At its end opposite the valve seat 4, the injection valve member 9 has a double-acting control piston 25, which is guided in the guide sleeve 21 in a close sliding fit. The control piston 25 is acted upon on its underside by the high fuel pressure in the high-pressure chamber 7 and limited with its upper side a control chamber 26 which is bounded laterally by the guide sleeve 21. In the guide sleeve 21 is an intermediate valve body 27, which in the direction the longitudinal axis A is displaceable and has a lower end face 27a. The intermediate valve body 27 is guided in the guide sleeve 21 with a play of typically 0.03 to 0.2 millimeters. In the intermediate valve body 27 extends a coaxial to the longitudinal axis A throttle passage 31, which extends between the lower and upper end face 27 a, 27 b of the intermediate valve body 27.

Im Steuerraum 26 ist ein Federelement 28 angeordnet, das sich einerseits am Zwischenventilkörper 27 und andererseits an einem Stützelement 29 abstützt, das auf einer Ringschulter 30 an der Führungshülse 21 aufliegt (Fig. 3). Das Federelement 28 umgibt einen zentralen Vorsprung 25a des Steuerkolbens 25 und erzeugt auf den Zwischenventilkörper 27 eine Kraft, die wesentlich kleiner ist, als die von der Schliessfeder 11 ausgeübte Kraft. Bei geschlossenem Einspritzventil 1 ist die untere Stirnseite 27a des Zwischenventilkörpers 27 in einem Abstand a von der Oberseite 29a des Stützelementes 29 angeordnet (siehe Figur 3). Das Stützelement 29 dient als die Bewegung des Zwischenventilkörpers 27 nach abwärts begrenzender Anschlag. Das Stützelement 29 könnte auch mit der Führungshülse 21 einteilig sein und mit letzterer als ein Werkstück ausgebildet werden.In the control chamber 26, a spring element 28 is arranged, which is supported on the one hand on the intermediate valve body 27 and on the other hand on a support member 29 which rests on an annular shoulder 30 on the guide sleeve 21 ( Fig. 3 ). The spring element 28 surrounds a central projection 25a of the control piston 25 and generates on the intermediate valve body 27 a force which is substantially smaller than the force exerted by the closing spring 11 force. When the injection valve 1 is closed, the lower end face 27a of the intermediate valve body 27 is arranged at a distance a from the upper side 29a of the support element 29 (see FIG FIG. 3 ). The support member 29 serves as the movement of the intermediate valve body 27 downwardly limiting stop. The support element 29 could also be integral with the guide sleeve 21 and formed with the latter as a workpiece.

Mit der oberen Stirnseite 27b liegt der Zwischenventilkörper 27 an einer unteren, als Dichtfläche dienenden Stirnseite 32a eines Steuerkörpers 32 an, der lose, d.h. nicht dichtend, in der zentralen Bohrung 6 angeordnet ist. Die untere Stirnseite 32a des Steuerkörpers 32 dichtet zusammen mit der Oberseite 21a der Führungshülse 21 den Steuerraum 26 gegenüber dem Hochdruckraum 7 ab. Der Steuerkörper 32 liegt mit einer oberen Stirnseite 32b an der Unterseite 33a eines Haltekörpers 33 an. Der Haltekörper 33 ist mittels eines Aussengewindes 34 in eine Ausnehmung 35 im Gehäuse 2 eingeschraubt. Der Haltekörper 33 ist mit Senklöchern 36 versehen, die zum Einführen eines Werkzeuges zum Einschrauben und Anziehen des Haltekörpers 33 dienen (siehe auch Figur 4).With the upper end face 27b of the intermediate valve body 27 is located on a lower, serving as a sealing surface end face 32a of a control body 32 which is loosely, that is not arranged in the central bore 6. The lower end 32a of the control body 32 seals together with the top 21a of the guide sleeve 21 from the control chamber 26 with respect to the high-pressure chamber 7 from. The control body 32 is located at a upper end face 32b on the underside 33a of a holding body 33 at. The holding body 33 is screwed by means of an external thread 34 into a recess 35 in the housing 2. The holding body 33 is provided with countersunk holes 36, which serve to insert a tool for screwing and tightening the holding body 33 (see also FIG. 4 ).

Der Haltekörper 33 ist derart fest in die Gehäuseausnehmung 35 eingeschraubt, dass er mit einer an seiner Unterseite 33a ausgebildeten, ersten ringförmigen Dichtfläche 37 an einer Sitzfläche 38 anliegt, die am Boden der Ausnehmung 35 im Gehäuse 2 ausgebildet ist und die zentrale Bohrung 6 umgibt. An diese erste Dichtfläche 37 des Haltekörpers 33 schliesst eine zweite, ebenfalls ringförmige Dichtfläche 39 an, die in derselben Ebene liegt wie die erste Dichtfläche 37. An dieser zweiten Dichtfläche 39 liegt eine an der oberen Stirnseite 32b des Steuerkörpers 32 ausgebildete Dichtfläche 40 an. Die Dichtflächen 37, 38, 39 und 40 dichten vorzugsweise nahe am Umfang der Bohrung 6. Dabei sind die Dichtflächen 37 und 39 des Haltekörpers 33 mit Vorteil an einer einzigen ebenen Endfläche des Haltekörpers 33 ausgebildet.The holding body 33 is screwed so tightly into the housing recess 35 that it rests with a formed on its underside 33 a, first annular sealing surface 37 on a seat 38 which is formed at the bottom of the recess 35 in the housing 2 and the central bore 6 surrounds. At this first sealing surface 37 of the holding body 33 includes a second, also annular sealing surface 39, which lies in the same plane as the first sealing surface 37. At this second sealing surface 39 is formed on the upper end face 32b of the control body 32 sealing surface 40 at. The sealing surfaces 37, 38, 39 and 40 preferably close close to the circumference of the bore 6. In this case, the sealing surfaces 37 and 39 of the holding body 33 are advantageously formed on a single planar end face of the holding body 33.

Der Steuerkörper 32 weist einen koaxial zur Längsrichtung A verlaufenden, durchgehenden Steuerdurchlass 41 auf, der an seinem in die obere Stirnfläche 32b des Steuerkörpers 32 mündenden Ende eine Drosselverengung 42 hat. Der Steuerdurchlass 41 steht mit dem Drosseldurchlass 31 im Zwischenventilkörper 27 in hydraulischer Verbindung.The control body 32 has a coaxial with the longitudinal direction A extending, continuous control passage 41 which has a throttle restriction 42 at its opening into the upper end face 32b of the control body 32 end. The control passage 41 is in hydraulic communication with the throttle passage 31 in the inter-valve body 27.

Die Dichtfläche 40 an der oberen Stirnseite 32b des Steuerkörpers 32 umgibt den Steuerdurchlass 41.The sealing surface 40 on the upper end face 32b of the control body 32 surrounds the control passage 41.

Im Steuerkörper 32 sind weiter Durchlässe 43 ausgebildet, die gegenüber dem Steuerdurchlass 41 seitlich versetzt sind und die in die untere Stirnseite 32a des Steuerkörpers 32 münden. Am anderen Ende stehen die Durchlässe 43 mit einer Ringnut 44 am Aussenumfang des Steuerkörpers 32 in Verbindung, die mit dem Ringraum 23 verbunden ist und in der daher der Brennstoffhochdruck herrscht. Beim sich in der Schliessstellung befindlichen Einspritzventil 1, d.h. also zwischen den Einspritzvorgängen, sind die Durchlässe 43 durch den Zwischenventilkörper 27 verschlossen, der mit seiner oberen Stirnseite 27b an die untere Stirnseite 32a des Steuerkörpers 32 gedrückt wird.In the control body 32 passages 43 are further formed, which are offset laterally relative to the control passage 41 and which open into the lower end face 32a of the control body 32. At the other end, the passages 43 are connected to an annular groove 44 on the outer circumference of the control body 32 in connection, which is connected to the annular space 23 and in which therefore the high fuel pressure prevails. When located in the closed position injection valve 1, ie between the injection processes, the passages 43 are closed by the intermediate valve body 27 which is pressed with its upper end face 27b to the lower end face 32a of the control body 32.

Zur Steuerung der Bewegung des Einspritzventilgliedes 9 ist im Gehäuse 2 ein elektromagnetisch betätigtes Pilotventil 45 untergebracht, das einen verschiebbaren Ventilschaft 46 sowie einen von diesem getrennten Verschlusskörper 47 aufweist, der zwischen den Einspritzvorgängen auf der als Ventilsitzfläche dienenden oberen Stirnseite 32b des Steuerkörpers 32 aufliegt und den Steuerdurchlass 41 verschliesst. Auf den Ventilschaft 46 und damit auch auf den Verschlusskörper 47 wirkt eine Pilotventilfeder 48, die den Verschlusskörper 47 an die obere Stirnseite 32b des Steuerkörpers 32 andrückt.To control the movement of the injection valve member 9, an electromagnetically actuated pilot valve 45 is housed in the housing 2, which has a displaceable valve stem 46 and a separate therefrom closure body 47 which rests between the injections on serving as a valve seat surface upper end face 32b of the control body 32 and the Closes control passage 41. On the valve stem 46 and thus also on the closure body 47 acts a pilot valve spring 48, which presses the closure body 47 to the upper end face 32b of the control body 32.

Zur Betätigung des Ventilschaftes 46 ist eine Elektromagnetanordnung 49 vorhanden, die aus einem Magnetkörper 50 mit Magnetspule 51 sowie einem Magnetanker 52 besteht. Der Ventilschaft 46 ist mit dem Magnetanker 52 fest verbunden und ist im Magnetkörper 50 verschiebbar geführt.For actuating the valve stem 46, an electromagnet arrangement 49 is present, which consists of a magnetic body 50 with a magnetic coil 51 and a magnet armature 52. The valve stem 46 is fixedly connected to the armature 52 and is slidably guided in the magnet body 50.

Der Haltekörper 33 weist neben den Senklöchern 36 auch eine zentrale Bohrung 53 auf (siehe auch Figur 4), in der der Ventilschaft 46 verläuft und in der der Verschlusskörper 47 verschiebbar geführt ist. In diese zentrale Bohrung 53 ragt eine Anschlagschulter 54 hinein, die in eine Ringnut 55 am Ventilschaft 46 eingreift. Die Anschlagschulter 54 dient zur Begrenzung des Hubes des Ventilschaftes 46 bei einer Erregung der Elektromagnetanordnung 49. Der maximal mögliche Hub b des Ventilschaftes 46 ist dabei kleiner als der Abstand c zwischen dem Magnetanker 52 und dem Magnetkörper 50, so dass auch bei offenem Pilotventil 45 der Magnetanker 52 nicht am Magnetkörper 50 anliegt. Die Anschlagschulter 54 für den Ventilschaft 46 liegt ausserhalb des wirksamen magnetischen Feldes der Elektromagnetanordnung 49.The holding body 33 has in addition to the countersunk holes 36 and a central bore 53 (see also FIG. 4 ), in the the valve stem 46 extends and in which the closure body 47 is guided displaceably. In this central bore 53 projects into a stop shoulder 54, which engages in an annular groove 55 on the valve stem 46. The maximum stop stroke b of the valve stem 46 is smaller than the distance c between the armature 52 and the magnet body 50, so that even when the open pilot valve 45 of Magnetic armature 52 is not applied to the magnetic body 50. The stop shoulder 54 for the valve stem 46 is outside the effective magnetic field of the solenoid assembly 49th

Um den Ventilschaft 46 in den Haltekörper 33 einsetzen zu können, ist letzterer mit einer exzentrisch angeordneten Ausnehmung 56 versehen, die zur zentralen Bohrung 53 hin offen ist. Der Ventilschaft 46 wird gegenüber der Achse der zentralen Bohrung 53 seitlich versetzt in die Ausnehmung 56 eingeführt. Befindet sich die Ringnut 55 des Ventilschaftes 46 auf der Höhe der Anschlagschulter 54, wird der Ventilschaft 46 in Querrichtung in die zentrale Bohrung 53 verschoben.In order to use the valve stem 46 in the holding body 33, the latter is provided with an eccentrically arranged recess 56 which is open to the central bore 53. The valve stem 46 is laterally offset relative to the axis of the central bore 53 inserted into the recess 56. If the annular groove 55 of the valve stem 46 is at the level of the stop shoulder 54, the valve stem 46 is displaced transversely into the central bore 53.

Der lose in der Bohrung 53 geführte Verschlusskörper 47 dient neben dem Verschliessen des Steuerdurchlasses 41 dazu, den Hub b des Ventilschaftes 46 genau einzustellen. Durch Einsetzen eines Verschlusskörpers 47 einer bestimmten Höhe lässt sich die Grösse des Hubes b genau festlegen. Falls eine solche genaue Einstellung nicht nötig sein sollte - was zum Beispiel bei einer anderen Ausgestaltung der Hubbegrenzung des Ventilschaftes 46 der Fall sein kann - kann der Verschlusskörper 47 entfallen. In diesem Fall wird der Steuerdurchlass 41 direkt durch den Ventilschaft 46 verschlossen, wie das beispielsweise aus der EP-A-1 273 791 bekannt ist. Bei der in den Figuren gezeigten Lösung wirkt das untere, ballige Ende 46a des Ventilschaftes 46 auf die ebene obere Endfläche 47b des Verschlusskörpers 47 (Fig. 3). Umgekehrt könnte die obere Endfläche 47b des Verschlusskörpers 47 ballig ausgebildet sein und mit einer ebenen Endfläche 46a des Ventilschaftes 46 zusammenwirken. In beiden Fällen wird die Dichtheit des Pilotventils 45 verbessert.The closure body 47 guided loosely in the bore 53 serves, in addition to closing the control passage 41, to precisely set the stroke b of the valve stem 46. By inserting a closure body 47 of a certain height, the size of the stroke b can be set precisely. If such an accurate adjustment should not be necessary - which may be the case, for example, in another embodiment of the stroke limitation of the valve stem 46 - the closure body 47 can be dispensed with. In this case, the control passage 41 is directly through the valve stem 46 is closed, as for example from the EP-A-1 273 791 is known. In the solution shown in the figures, the lower, crowned end 46a of the valve stem 46 acts on the flat upper end face 47b of the closure body 47 (FIG. Fig. 3 ). Conversely, the upper end surface 47b of the closure body 47 could be crowned and cooperate with a flat end surface 46a of the valve stem 46. In both cases, the tightness of the pilot valve 45 is improved.

Die zentrale Bohrung 53 und die Ausnehmung 56 im Haltekörper 33 gehören zu einem Niederdruckraum 57, der mit einem Niederdruckauslass 58 (Fig. 1 und 2) strömungsverbunden ist. Von diesem Niederdruckauslass 58 führt eine nicht dargestellte Leitung zurück zu einem Brennstoffreservoir. Der Verschlusskörper 47 ist mit Längsnuten 47a versehen, die bei vom Steuerkörper 32 abgehobenem Verschlusskörper 47 einen Brennstoffdurchfluss vom Steuerdurchlass 41 in den Niederdruckraum 57 erlauben.The central bore 53 and the recess 56 in the holding body 33 belong to a low-pressure chamber 57 which is connected to a low-pressure outlet 58 (FIG. Fig. 1 and 2 ) is fluidly connected. From this low pressure outlet 58, a line, not shown, leads back to a fuel reservoir. The closure body 47 is provided with longitudinal grooves 47a which allow a fuel flow from the control passage 41 into the low-pressure space 57 when the closure body 47 is lifted off the control body 32.

Wie bereits erwähnt herrscht in der Ringnut 44 im Steuerkörper 32 der Brennstoffhochdruck, der 2000 bar und mehr betragen kann. Um zu verhindern, dass aus dieser zum Hockdruckraum 7 gehörenden Ringnut 44 grössere Mengen von Brennstoff am nicht dichtend in das Gehäuse 2 eingesetzten Steuerkörper 32 vorbei zum Niederdruckraum 57 gelangen können, wird die erste Dichtfläche 37 des in das Gehäuse 2 eingeschraubten Haltkörpers 33 dichtend an die Sitzfläche 38 im Gehäuse 2 angepresst. Im Weiteren wird der Steuerkörper 32 durch den Brennstoffdruck im Hochdruckraum 7 mit seiner Dichtfläche 40 gegen die andere Dichtfläche 39 am Haltekörper 33 gedrückt. An die Oberflächengüte der Dichtflächen 37, 39 und 40 und die Sitzfläche 38 werden dabei nicht allzu hohe Anforderungen gestellt. Es kann genügen, diese Flächen zu schleifen, um eine genügende Dichtwirkung zu erzielen, denn die Dichtwirkung muss nicht hundertprozentig sein. Teure Nachbearbeitungsschritte sind somit nicht zwingend nötig. Falls eine hundertprozentige Dichtwirkung notwendig oder erwünscht sein sollte, kann eine solche mit fein geläppten Flächen erreicht werden. Ist jedoch die Leckage wesentlich kleiner als die über den Steuerdurchlass 41 entlastete Brennstoffmenge (z.B. 10% der letzteren oder weniger), so spielt die Leckage in der Regel praktisch keine Rolle.As already mentioned prevails in the annular groove 44 in the control body 32 of the high fuel pressure, which may be 2000 bar and more. In order to prevent larger amounts of fuel from passing through the control body 32, which is not sealingly inserted into the housing 2, to the low-pressure chamber 57, the first sealing surface 37 of the holding body 33 screwed into the housing 2 is sealingly connected to the annular groove 44 belonging to the high pressure chamber 7 Seat 38 pressed in the housing 2. Furthermore, the control body 32 is pressed by the fuel pressure in the high pressure chamber 7 with its sealing surface 40 against the other sealing surface 39 on the holding body 33. At the surface quality of the sealing surfaces 37, 39 and 40 and the seat 38 are not made too high demands. It can It is sufficient to grind these surfaces in order to achieve a sufficient sealing effect, because the sealing effect need not be one hundred percent. Expensive post-processing steps are therefore not absolutely necessary. If a one hundred percent sealing effect is necessary or desired, one with finely lapped surfaces can be achieved. However, if the leakage is substantially smaller than the amount of fuel discharged through the control passage 41 (eg, 10% of the latter or less), leakage tends to be practically irrelevant.

Die Funktionsweise des in den Figuren 1 - 3 gezeigten Brennstoffeinspritzventils 1 ist wie folgt: Ausgegangen wird vom in diesen Figuren gezeigten Zustand, in welchem sich das Einspritzventilglied 9 in Schliessstellung befindet und der Zwischenventilkörper 27 dichtend am Steuerkörper 32 anliegt. Die Elektromagnetanordnung 49 ist nicht erregt und der Verschlusskörper 47 verschliesst den Steuerdurchlass 41. Im Steuerraum 26 herrscht derselbe Druck wie im Hochdruckraum 7.The functioning of the in the Figures 1 - 3 The fuel injection valve 1 shown is as follows: Starting from the state shown in these figures, in which the injection valve member 9 is in the closed position and the intermediate valve body 27 sealingly abuts the control body 32. The solenoid assembly 49 is not energized and the closure body 47 closes the control passage 41. In the control chamber 26, the same pressure prevails as in the high pressure chamber. 7

Durch das Erregen der Elektromagnetanordnung 49 wird ein Einspritzzyklus ausgelöst. Dabei wird der Magnetanker 52 gegen den Magnetkörper 50 gezogen, was zur Folge hat, dass sich der Ventilschaft 46 vom Verschlusskörper 47 abhebt. Der Verschlusskörper 47 kann sich nun unter der Wirkung des Brennstoffdruckes im Steuerdurchlass 41 nach oben verschieben und gibt den Steuerdurchlass 41 frei. Der Steuerdurchlass 41 und damit auch der Steuerraum 26 sind jetzt mit dem Niederdruckraum 57 verbunden. Der Druck im Steuerraum 26 beginnt zu sinken. Das Einspritzventilglied 9 bewegt sich dadurch vom Ventilsitz 4 weg und gibt die Einspritzöffnungen 5 frei. Der Einspritzvorgang beginnt. Dabei wird Brennstoff aus dem Steuerraum 26 durch den Drosseldurchlass 31 und den Steuerdurchlass 41 in den Niederdruckraum 57 verdrängt. Während des gesamten Oeffnungsvorgangs des Einspritzventilgliedes 9 bleibt der Zwischenventilkörper 27 in Anlage am Steuerkörper 32. Der Oeffnungshub des Einspritzventilgliedes 9 wird z. B. dadurch begrenzt, dass der Vorsprung 25a des Steuerkolbens 25 am Zwischenventilkörper 27 zur Anlage kommt.By energizing the solenoid assembly 49, an injection cycle is triggered. In this case, the magnetic armature 52 is pulled against the magnetic body 50, with the result that the valve stem 46 lifts off from the closure body 47. The closure body 47 can now move upwards under the effect of the fuel pressure in the control passage 41 and releases the control passage 41. The control passage 41 and thus also the control chamber 26 are now connected to the low-pressure chamber 57. The pressure in the control chamber 26 begins to decrease. As a result, the injection valve member 9 moves away from the valve seat 4 and releases the injection openings 5. The injection process begins. In this case, fuel from the control chamber 26 through the Throttling passage 31 and the control passage 41 displaced in the low-pressure space 57. During the entire opening operation of the injection valve member 9 of the intermediate valve body 27 remains in contact with the control body 32. The opening stroke of the injection valve member 9 is z. Example, characterized in that the projection 25a of the control piston 25 comes to the intermediate valve body 27 to the plant.

Zum Beenden des Einspritzvorganges wird die Elektromagnetanordnung 49 entregt. Dies hat zur Folge, dass unter der Kraft der Pilotventilfeder 48 der Ventilschaft 46 und mit ihm der Verschlusskörper 47 nach abwärts bewegt werden, bis der Verschlusskörper 47 zur Anlage am Steuerkörper 32 gelangt. Die niederdruckseitige Mündung des Steuerdurchlasses 41 wird durch den Verschlusskörper 47 wieder verschlossen. Der Druck im Steuerdurchlass 41 beginnt zu steigen. Dies zusammen mit dem Umstand, dass in den Durchlässen 43 im Steuerkörper 32 der Brennstoffhochdruck herrscht, führt zu einem Wegbewegen des Zwischenventilkörpers 27 weg von der dichtenden Anlage am Steuerkörper 32. Die Abwärtsbewegung des Zwischenventilkörpers 27 wird durch Anschlagen an der Oberseite 29a des Stützelementes 29 beendet. Dadurch, dass durch das Wegbewegen des Zwischenventilkörpers 27 vom Steuerkörper 32 die Durchlässe 43 im Steuerkörper 32 geöffnet werden, kann durch diese Durchlässe 43 und den Drosseldurchlass 31 sowie entlang des gesamten Umfanges des Zwischenventilkörpers 27 Brennstoff unter hohem Druck nachfliessen, was den Schliessvorgang des Einspritzventilgliedes 9 stark beschleunigt. Sobald das Einspritzventilglied 9 wieder am Ventilsitz 4 anliegt und die Einspritzöffnungen 5 verschliesst, wird der Einspritzvorgang beendet.To end the injection process, the solenoid assembly 49 is de-energized. This has the consequence that under the force of the pilot valve spring 48 of the valve stem 46 and with it the closure body 47 are moved downward until the closure body 47 comes to rest on the control body 32. The low-pressure side opening of the control passage 41 is closed by the closure body 47 again. The pressure in the control passage 41 starts to increase. This, together with the fact that in the passages 43 in the control body 32 of the high fuel pressure, leads to a Wegbewegen the intermediate valve body 27 away from the sealing contact with the control body 32. The downward movement of the intermediate valve body 27 is terminated by abutting the top 29 a of the support member 29 , Characterized in that by moving away the intermediate valve body 27 from the control body 32, the passages 43 are opened in the control body 32 can flow through these passages 43 and the throttle passage 31 and along the entire circumference of the intermediate valve body 27 fuel under high pressure, resulting in the closing of the injection valve member. 9 strongly accelerated. As soon as the injection valve member 9 abuts the valve seat 4 again and closes the injection openings 5, the injection process is ended.

Unmittelbar danach wird der Zwischenventilkörper 27 unter der Kraft des Federelementes 28 in seine Dichtstellung zurückbewegt. Das Brennstoffeinspritzventil 1 ist nun bereit für den nächsten Einspritzvorgang.Immediately thereafter, the intermediate valve body 27 is moved back under the force of the spring element 28 in its sealing position. The fuel injection valve 1 is now ready for the next injection process.

Die Distanzhülse 14, die den Bereich des Brennstoffhochdruckeinlasses 8 überspannt, ermöglicht es, die Schliessfeder 11 unterhalb des Brennstoffhochdruckeinlasses 8 anzuordnen, so dass die Wandstärke des Gehäuses 2 im Bereich des Brennstoffhochdruckeinlasses 8 gross gehalten werden kann, ohne dass der Aussendurchmesser des Gehäuses 2 vergrössert werden muss. Die Distanzhülse 14 überträgt die Kraft der Schliessfeder 11 über die Führungshülse 21 auf den Steuerkörper 32.The spacer sleeve 14, which spans the region of the high-pressure fuel inlet 8, makes it possible to arrange the closing spring 11 below the high-pressure fuel inlet 8, so that the wall thickness of the housing 2 in the area of the high-pressure fuel inlet 8 can be kept large without enlarging the outer diameter of the housing 2 got to. The spacer sleeve 14 transmits the force of the closing spring 11 via the guide sleeve 21 on the control body 32nd

Bei der Montage wird das Einspritzventilglied 9 mit der Schliessfeder 11 und übergestülpter Distanzhülse 14 in das Ventilsitzelement 2b eingesetzt, diese Unterbaueinheit in den oberen Gehäuseteil 2a eingebracht und mittels des Halteelementes 3 am oberen Gehäuseteil 2a befestigt. Die Anschlagschulter 19 im oberen Gehäuseteil 2a begrenzt den Einschubweg der Distanzhülse 14 in der zentralen Bohrung 6, was die Montage des Steuerkörpers 32 ganz wesentlich vereinfacht.During assembly, the injection valve member 9 is inserted with the closing spring 11 and slipped spacer sleeve 14 in the valve seat member 2b, this sub-assembly is inserted into the upper housing part 2a and secured by means of the holding element 3 on the upper housing part 2a. The stop shoulder 19 in the upper housing part 2 a limits the insertion path of the spacer sleeve 14 in the central bore 6, which greatly simplifies the assembly of the control body 32.

Das Stützelement 29 dient wie erwähnt als Anschlag für den Zwischenventilkörper 27, wodurch der Oeffnungsweg des Zwischenventilkörpers 27 begrenzt wird. Das bringt Vorteile bei Voreinspritzungen mit kurzen Zeitabständen.The support member 29 serves as mentioned as a stop for the intermediate valve body 27, whereby the Oeffnungsweg the intermediate valve body 27 is limited. This brings advantages in pre-injections with short time intervals.

Dadurch, dass der Steuerkörper 32 lose in die zentrale Bohrung 6 eingelegt ist, müssen an den Steuerkörper 32 hinsichtlich Herstellung und Bearbeitung keine besonderen Anforderungen gestellt werden. Zudem ist der Einbau des Steuerkörpers 32 in das Gehäuse 2 vergleichsweise einfach. Das alles wirkt sich günstig auf die Kosten aus.Characterized in that the control body 32 is loosely inserted into the central bore 6, no special requirements must be made of the control body 32 in terms of production and processing. In addition, the installation of the Control body 32 in the housing 2 comparatively simple. All this has a favorable effect on the costs.

Beim gezeigten Ausführungsbeispiel erfolgt die Brennstoffzufuhr zum Ventilsitz 4 über die zentrale Gehäusebohrung 6. Die beschriebenen besonderen konstruktiven Lösungen können aber auch bei Brennstoffeinspritzventilen Anwendung finden, bei denen die Brennstoffzufuhr zum Ventilsitz über einen gegenüber der Gehäuselängsachse A seitlich versetzten Zuführkanal erfolgt, wie das beispielsweise aus der US-A-5,775,301 bekannt ist.In the embodiment shown, the fuel supply to the valve seat 4 via the central housing bore 6. The described special constructive solutions can also be used in fuel injection valves, in which the fuel supply to the valve seat via a relative to the housing longitudinal axis A laterally offset feed channel, as for example from US-A-5,775,301 is known.

Claims (17)

  1. Fuel injection valve for the intermittent injection of fuel into the combustion chamber of an internal combustion engine, having an elongate housing (2), a valve seat (4) with injection openings (5), a high pressure space (7) in the housing (2) which is connected to a high pressure fuel inlet (8) and to the valve seat (4), an injection valve element (9) which is guided in the housing (2) in a longitudinally adjustable manner and interacts with the valve seat (4) for closing and opening the injection openings (5), and a hydraulic control apparatus (10) for controlling the adjusting movement of the injection valve element (9), which hydraulic control apparatus (10) has a control body (32) which is held on its circumference in the housing (2) in an opening (6) which is connected to the high pressure space (7), and which control body (32) is provided with a control passage (41) which is connected to a control space (26) on the one, first end side (32a) of the control body (32), is closed on the other, second end side (32b) of the control body (32) and can be connected to a low pressure space (57) by means of a pilot valve (45), characterized in that the control body (32) is held on its circumference in a non-sealing manner in the opening (6) of the housing (2) and has a flat sealing face (40) on its second end side (32b), which flat sealing face (40) surrounds the control passage (41) and with which the control body (32) bears sealingly, under the action of the fuel pressure in the high pressure space (7), against a first sealing face (39) of a holding body (33) which is held fixedly in the housing (2) and on which a second sealing face (37) is formed which lies in a common flat end face with the first sealing face (39) on the holding body (33) and with which the holding body (33) bears sealingly against a seat face (38) which is formed in the housing (2) and surrounds the opening (6) in the housing (2).
  2. Fuel injection valve according to Claim 1, characterized in that the hydraulic control apparatus (10) has a control piston (25) which is guided in a longitudinally displaceable manner, is operatively connected to the injection valve element (9) and is loaded firstly by the fuel system pressure which prevails in the high pressure space (7) and secondly by the fuel control pressure in the control space (26).
  3. Fuel injection valve according to Claim 1 or 2, characterized in that a displaceable intermediate valve body (27) is arranged in the opening (6) in the housing (2), which displaceable intermediate valve body (27) bears against the first end side (32a) of the control body (32) in the closed state of the fuel injection valve (1) and in the process closes at least one passage (43) which is formed in the control body (32) and opens firstly into the first end side (32a) of the control body (32) and secondly is flow-connected to the high pressure space (7).
  4. Fuel injection valve according to Claim 3, characterized in that a stop (29a) is provided in the housing (2) for limiting the displacement movement of the intermediate valve body (27).
  5. Fuel injection valve according to Claim 3, characterized in that the intermediate valve body (27) is guided with play in a guide sleeve (21) which is arranged in the opening (6) in the housing (2) and bears against the first end side (32a) of the control body (32).
  6. Fuel injection valve according to Claims 4 and 5, characterized in that the stop (29a) is formed on the guide sleeve (21).
  7. Fuel injection valve according to Claims 4 and 5, characterized in that the stop (29a) is formed on a supporting element (29) which is supported in the guide sleeve (21) and serves as a rest for a spring element (28) which presses the intermediate valve body (27) against the control body (32).
  8. Fuel injection valve according to one of Claims 1 to 7, characterized by a spacer sleeve (14) which is arranged in the hole (6) in the housing (2), surrounds the injection valve element (9), and on which a closing spring (11) is supported with its one end, which closing spring (11) is supported on the injection valve element (9) with its other end.
  9. Fuel injection valve according to Claims 5 and 8, characterized in that the spacer sleeve (14) bears against the guide sleeve (21) at that end of the latter which faces away from the control body (32).
  10. Fuel injection valve according to one of Claims 1 to 9, characterized in that the pilot valve (45) has a valve stem (46) which extends in the holding body (33) and, when an electromagnet arrangement (49) is excited for opening the control passage (41), can be moved in the direction away from the control passage (41) counter to the force of a pilot valve spring (48), the opening stroke (b) of the valve stem (46) being limited by means of a stop (54) which is formed in the holding body (33).
  11. Fuel injection valve according to Claim 10, characterized in that the valve stem (46) is connected to a magnet armature (52) which interacts with a magnet coil (51), and in that the stop (54) is arranged on that side of the magnet armature (52) which faces away from the magnet coil (51).
  12. Fuel injection valve according to Claim 10 or 11, characterized in that the stop is formed on the holding body (33).
  13. Fuel injection valve according to Claim 12, characterized in that the stop is formed by a stop shoulder (54) which is formed on the holding body (33) and engages with axial play into a groove (55) of the valve stem (46).
  14. Fuel injection valve according to one of Claims 10 to 13, characterized in that a closure body (47) which is guided loosely in the holding body (33) is arranged between the valve stem (46) and the control body (32), which closure body (47) is pressed by the valve stem (46) against the second end side (32b) of the control body (32) when the electromagnet arrangement (49) is not excited and in the process closes the control passage (41).
  15. Fuel injection valve according to Claim 14, characterized in that the closure body (47) and that end (46a) of the valve stem (46) which interacts with the former are arranged coaxially with respect to the longitudinal axis (A) of the housing (2).
  16. Fuel injection valve according to one of Claims 1 to 15, characterized in that the holding body (33) is screwed into a recess (35) in the housing (2).
  17. Fuel injection valve according to one of Claims 1 to 16, characterized in that at least one passage (43) is formed in the control body (32), which passage (43) firstly opens into the first end side (32a) of the control body (32) and secondly is connected to a recess (44) which is formed on the outer circumference of the control body (32) and is flow-connected to the high pressure space (7).
EP05706519A 2004-02-25 2005-02-21 Fuel injection valve for internal combustion engines Active EP1718862B1 (en)

Applications Claiming Priority (2)

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CH3102004 2004-02-25
PCT/CH2005/000098 WO2005080785A1 (en) 2004-02-25 2005-02-21 Fuel injection valve for internal combustion engines

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EP1718862A1 EP1718862A1 (en) 2006-11-08
EP1718862B1 true EP1718862B1 (en) 2010-11-03

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US (1) US7591436B2 (en)
EP (1) EP1718862B1 (en)
AT (1) ATE487057T1 (en)
DE (1) DE502005010478D1 (en)
ES (1) ES2355146T3 (en)
WO (1) WO2005080785A1 (en)

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US7591436B2 (en) 2009-09-22
US20060278731A1 (en) 2006-12-14
ES2355146T3 (en) 2011-03-23
DE502005010478D1 (en) 2010-12-16
ATE487057T1 (en) 2010-11-15
WO2005080785A1 (en) 2005-09-01
EP1718862A1 (en) 2006-11-08

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