EP0685645B1 - Injection valve for a fuel injection system of an internal combustion engine, particularly of a diesel engine - Google Patents

Injection valve for a fuel injection system of an internal combustion engine, particularly of a diesel engine Download PDF

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Publication number
EP0685645B1
EP0685645B1 EP95103560A EP95103560A EP0685645B1 EP 0685645 B1 EP0685645 B1 EP 0685645B1 EP 95103560 A EP95103560 A EP 95103560A EP 95103560 A EP95103560 A EP 95103560A EP 0685645 B1 EP0685645 B1 EP 0685645B1
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EP
European Patent Office
Prior art keywords
valve
valve body
injection valve
injection
nozzle needle
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.)
Expired - Lifetime
Application number
EP95103560A
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German (de)
French (fr)
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EP0685645A3 (en
EP0685645A2 (en
Inventor
Christian Dipl.Masch.Ing. Eth Mathis
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Individual
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Individual
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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
    • 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
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • F02M61/205—Means specially adapted for varying the spring tension or assisting the spring force to close the injection-valve, e.g. with damping of valve lift
    • 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
    • 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
    • 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
    • F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
    • F02M2200/304—Fuel-injection apparatus having mechanical parts, the movement of which is damped using hydraulic means

Definitions

  • the invention relates to an injection valve for a fuel injection system an internal combustion engine, in particular a diesel engine, with a valve housing, one slidably arranged in this multi-part valve body and with at least one in a working cylinder mouth opening through which one of a pressure chamber outgoing fuel supply by controlling the valve body he follows.
  • a generic injection valve according to EP-A1 0 393 590 has a multi-part assembled housing and one in it of a solenoid valve arranged longitudinally displaceable which has a nozzle needle controlling the fuel injection and a piston-like extension part arranged coaxially to it comprises, which consists of a guided in the housing and an in Diameter narrowed lower part.
  • a between that Solenoid valve and the control valve provided with the extension part causes a gradual increase at the beginning of an injection the amount of fuel injected into a combustion cylinder.
  • With a such an injector also has an increased closing speed the nozzle needle achieves what is a positive effect Exhaust emissions from usually several such injection valves having internal combustion engine reduced.
  • the object of the present invention is to: To further develop the injection valve according to the type described in the introduction, that even with increased closing speed like even with a long design of its valve body when closing on the Nozzle tip of the valve acting too fast Overloading this tip leads to the injection valve its structure is not that complicated.
  • the object is achieved in that between the the injection opening controlling the nozzle needle and the at least one overlying valve body part of the multi-part valve body fuel-filled damping chamber with in any position of the Valve body constant inlet cross-sections Derivatives is formed.
  • Fig. Shows an injection valve 2 for a particular as a diesel engine provided internal combustion engine, which is not shown.
  • the injector 2 is suitable for a conventional injection system of a diesel engine, so that in this regard to a detailed explanation can be dispensed with. It essentially instructs Multi-part valve body that can be assembled in a conventional manner 47, 53, a longitudinally displaceably guided valve body 15, which actuates the latter and is designed as an electromagnetic valve 227 Control valve 20, an inflow line 13 for the high pressure standing fuel and a drain line 10.
  • the Multi-part valve body 15 is in the lower part of one of the inflow line 13 surrounded by fuel-fed pressure chamber 14 and it closes or opens one in a working cylinder of the diesel engine leading injection opening 4 or its feed line, which in the in the Working cylinder protruding nozzle tip 24 of the valve housing 47 is included. In the middle area this valve body is in one Passed bore of the valve housing 47 and protrudes at the upper end into a control chamber 17a and there is also a compression spring 97 pressed in the closing direction.
  • the control chamber 17a is with the valve 25 and the inflow line 13 with one High-pressure part containing fuel on the one hand and over the Line part 19 and this closable control valve 20 with the Drain line 10 connected on the other hand.
  • For the inflow line 13 is a radial to the injection valve 2 connection 92 is provided, the one the connecting ring 70 encompassing the valve housing 47 and a feed line 13 has a threaded nut 72 pressing against the housing.
  • damping space 43 between which the injection opening 4 controlling nozzle needle 15a and the one above it Valve body part 15b of the two-part valve body 15 is provided, such as this also in the enlarged partial longitudinal section according to FIG Fig.2 is clarified.
  • This damping space 43 is on the one hand between the nozzle needle 15a and the valve housing 47 and on the other hand, one between the valve body part 15b and the Valve housing 47 formed almost play-free guide fit 44, 45 upstream or downstream. Accordingly, one results in the Amount of restricted inflow or outflow into or out of this steam chamber 43 out of or into the adjacent pressure chamber 14 or chamber 49.
  • the injector 2 is mostly off conventional components can be assembled and therefore does not become more complex to manufacture.
  • the spring force acts when the injection valve 2 is closed and at rest a compression spring 97 on the valve body part 15b against the nozzle needle 15a and leads their end faces 16 located in the damping space 43, 25 to a mutual touch before the next Injection takes place while these end faces 16, 25 after a valve opening slowly move away from each other due to the high pressure from the pressure chambers 14, 49 through the Guide fits 44, 45 flowing in the damping space 43 limited Fuel and because the average pressure in the damping chamber 43 approximately to the pressure of the injection-side surface of the nozzle needle 15a falls off.
  • valve body 15 If the valve body 15 is subsequently closed, there is only a direct impact of the relatively light nozzle needle 15a in the nozzle tip 24, however, also in the closing direction moved valve body part 15b by the between this and the Nozzle needle formed liquid cushion is cushioned and thereby the desired permanent reduction of the maximum load on the lowest point of the injector 2 is reached.
  • the security can be increased by for example, when the control valve 20 is jammed and thus connected, the injection opening 4 of the damping space 43 is constantly supplied with fuel and consequently the nozzle needle 15a from the valve body part 15b to a closure of the Injection opening 4 drifts away.
  • This damping space 43 also preferably has a maximum of one volume on, which approximates the cross-sectional area of the nozzle needle 15a and corresponds to a gap height of a maximum of two millimeters.
  • the control valve 20 designed as an electromagnetic valve 227 has one Control valve body 38 by a lower end valve seat 57 the vertical and then into a horizontal drain line 10 merging line part 19 in the valve housing 47 closes or opens.
  • This control valve body 38 has one of its valve seat 57 outgoing and communicating with the line part 19 60 'on which inside the control valve body 38 for the purpose of generation a closing force acting in the same closing direction is.
  • this bore 60 ' is at the top of an Control valve body 38 arranged coaxially in this longitudinally movable Pin 60 limited, which at its upper end regardless of Control valve body 38, in the present example on the lower Front side of a arranged in the magnetic core 22, with sufficient hardness provided pin is supported.
  • the magnetic core 22 lies with its lower one plan the end face directly on the film disk 61, which in turn is thereby on a flat ring surface of the Valve housing is fixed. Otherwise, the armature 62 and its neighboring parts provided recesses 66 through which at Movement of the armature flows around it Fuel is enabled. By an appropriate choice of Cross section of the recesses 66, the damping effect of adjust the reciprocating control valve body 38.
  • valve 25 is arranged, which via the inflow line 13 one connected to the high pressure part of the control medium annular chamber 28 and a top closing this at the top has annular valve seat 27, which when opening this additional Connection between the high pressure part and the control chamber 17b generated.
  • the valve 25 expediently has a coaxial with Nozzle needle 15 extending valve body 26 in the valve housing 47 is laterally sealing. This cylindrical valve body 26 and the valve housing 47 together form the annular chamber 28 and the valve seat 27 closing off this chamber 28.
  • valve body 26 protrudes with the one facing the nozzle needle 15 Face into the control chamber 17a and with the other face in one communicating with the drain line 10 via the control valve 20 Additional chamber 17b, which with the control chamber 17a via a Valve body 26 through throttle bore 23 is connected and on which borders the valve seat 27 on the circumference.
  • the latter is like this formed that the valve body 26 with its upper oblique ring edge sealing against a corresponding ring surface in the closed state rests in the housing bore and the annular chamber 28 surrounds the valve body 26 at least in its upper region.
  • This but conical valve seat 27 could also be cylindrical or be designed as a flat surface.
  • the valve body 26 with a cross, the inflow line 13 with the control chamber 17b connecting throttle bore 21 provided by means of a permanent connection of the control medium from the high pressure part to it Tax chamber is carried out.
  • valve body 26 In the closed position, the valve body 26 has a predetermined distance to the nozzle needle 15 below and on and between this is also a compression spring 96 that presses them apart provided, while in the open position of the nozzle needle 15, which by releasing the control valve 20 and an associated one Pressure drop in the control chamber 17a causes this nozzle needle 15a strikes on the lower end face 16 of the valve body 26.
  • the injection chamber 2 shown in FIG. 3 is the damping chamber 43 not directly as in the first embodiment Valve housing 47 but from one axially displaceable in the latter Surround ring element 15d, the latter the lower end of the Valve body part 15b forms.
  • the nozzle needle 15a which in turn the Inlet opening 4 opens or closes, projects into it with almost no play Ring element 15d and delimited together with one above it Ring element 15 longitudinally displaceable spacer 15c the damping space 43.
  • the length of the Spacer 15c can be length tolerances of the Valve body 15 together with the valve body 26 and the corresponding length formed by the housing parts 47, 53 compensate.
  • the nozzle needle 15a has at least in the lower area an implied non-circular cross-section, which makes this in the round Bore of the valve housing forms a free space for the pressure chamber. Otherwise, this injection valve 2 works analogously to that 1 and therefore all details are no longer explained. It has the advantage according to FIG. 1 that it has a lower Number of surfaces to be sanded and an accurate Guide fit in the housing 47 is omitted, which makes it from a tougher material can be made and definitely one generated high-frequency oscillating stroke of the nozzle needle 15a becomes.
  • FIG. 4 shows a further variant of an injection valve 2 in the for the invention relevant part shown. It is similar to itself that constructed according to FIG. 3, but the ring element 15d is for this purpose provided independently of the upper valve body part 15b. The latter and the nozzle needle 15a are round in the ring element 15d Training in this led to almost no play in this. According to the invention is again between the nozzle needle 15a and the Valve body part 15b formed damping space 43 is provided. That this surrounding ring element 15d is designed as an inner sealing tube and can with a correspondingly thin wall instead of metallic Material also consist of plastic. It's over the two ends the nozzle needle 15a and the valve body part 15b inserted and forms together with these a tight fit. This is the damping Function of the valve body 15 somewhat reduced.
  • This injector is inexpensive to manufacture and the ring element used therein 15d can transmit tensile forces and exercises a somewhat articulated Function off. If this ring element 15d is ground on the inside and is not stuck on the nozzle needle 15a and on the valve body part 15b, then the compression spring 97 acting on the end of this serves for Positioning of the same.
  • ring element 15d similar that according to Fig.4, which has a different inside Diameter in that with the nozzle needle 15a to that with the Has valve body part 15b in the connected area. It is supported on its upper end face on the compression spring 97.
  • the guide cross section of the Valve body part 15b in the ring element 15d larger than that of the Nozzle needle 15a. So that a full opening stroke Nozzle needle 15a with slight superimposed vibrations reached and when closed, the kinetic energy of the valve body part 15b on the ring member 15d by the reduction in diameter transferred from the latter formed stop surface.
  • damping space 43 could each have one of the guide fits throttle bore connected in parallel with the Pressure chamber to be connected.
  • control medium flowing into the control chambers is usually fuel, which as it were in the storage chamber and subsequently through the injection openings into a fuel cylinder is injected.
  • fuel which as it were in the storage chamber and subsequently through the injection openings into a fuel cylinder is injected.
  • a separate liquid can be used while the fuel would only be provided for injection.
  • damping space 43 could be provided with a a lower pressure than the pressure chamber Leak oil return line must be connected.
  • the pressure chamber 49 could in principle correspond to a lower pressure the drain line 10.
  • the invention Effect of damping is ensured when the through the guide fit 45 to the passage cross section formed by the guide fit 44 is not more than ten times larger.
  • the invention is with the exemplary embodiments explained above adequately demonstrated.
  • the Nozzle needle 15a could be made in two parts and the damping chamber would be arranged above this two-part nozzle needle.

Abstract

The valve has a valve housing, a multi-part valve body displaceably arranged in the housing and at least one entry aperture issuing into a work cylinder. A fuel feed from a pressure chamber occurs via the aperture by control of the valve body. Between the nozzle needle (15a) controlled by the injection aperture (4) and at least one superimposed valve body part (15b) of the multi-part valve body (15) a vapour chamber (43) filled with fuel is formed. The vapour chamber is enclosed directly by the valve housing (47) or by a ring member axially displaceable or stationary in the valve housing. <IMAGE>

Description

Die Erfindung betrifft ein Einspritzventil für eine Kraftstoffeinspritzanlage einer Brennkraftmaschine, insbesondere eines Dieselmotors, mit einem Ventilgehäuse, einem in diesem verschiebbar angeordneten mehrteiligen Ventilkörper und mit mindestens einer in einen Arbeitszylinder mündende Eintrittsöffnung, durch die eine von einer Druckkammer ausgehende Kraftstoffzufuhr durch Steuerung des Ventilkörpers erfolgt.The invention relates to an injection valve for a fuel injection system an internal combustion engine, in particular a diesel engine, with a valve housing, one slidably arranged in this multi-part valve body and with at least one in a working cylinder mouth opening through which one of a pressure chamber outgoing fuel supply by controlling the valve body he follows.

Ein gattungsmässiges Einspritzventil nach der EP-A1 0 393 590 weist ein mehrteiliges zusammensetzbares Gehäuse und einen darin mittels eines Elektromagnetventils längsverschiebbar angeordneten Ventilkörper auf, welcher eine die Kraftstoffeinspritzung steuernde Düsennadel und ein koaxial zu ihr angeordneten kolbenähnlichen Verlängerungsteil umfasst, der sich aus einem im Gehäuse geführten und einem im Durchmesser verengten unteren Teil zusammensetzt. Ein zwischen dem Elektromagnetventil und dem Verlängerungsteil versehenes Regelventil bewirkt dabei zu Beginn einer Einspritzung eine abgestufte Zunahme der Einspritzmenge des Kraftstoffes in einen Brennzylinder. Mit einem solchen Einspritzventil wird darüberhinaus eine erhöhte Schliessgeschwindigkeit der Düsennadel erzielt, was als positiver Effekt die Abgasemissionen der aus üblicherweise mehreren solcher Einspritzventile aufweisenden Brennkraftmaschine vermindert. Weil aber der zweiteilige Ventilkörper relativ lange ist und daher eine entsprechend grosse Masse aufweist, besteht die Gefahr, dass die Düsenkuppe beim Schliessen der Einspritzöffnung durch die Düsennadel zu stark belastet wird und zu Rissen oder gar zu einem Bruch derselben führen kann. Dies hinwiederum hat zur Folge, dass solche Risse oder Brüche in den Verbrennungszylinder führende Leckagen hervorrufen.A generic injection valve according to EP-A1 0 393 590 has a multi-part assembled housing and one in it of a solenoid valve arranged longitudinally displaceable which has a nozzle needle controlling the fuel injection and a piston-like extension part arranged coaxially to it comprises, which consists of a guided in the housing and an in Diameter narrowed lower part. A between that Solenoid valve and the control valve provided with the extension part causes a gradual increase at the beginning of an injection the amount of fuel injected into a combustion cylinder. With a such an injector also has an increased closing speed the nozzle needle achieves what is a positive effect Exhaust emissions from usually several such injection valves having internal combustion engine reduced. But because of that two-part valve body is relatively long and therefore one accordingly has large mass, there is a risk that the nozzle tip at Closing the injection opening by the nozzle needle too much and can lead to cracks or even breakage. This in turn means that such cracks or breaks in the Cause leaks in combustion cylinders.

Aufgabe der vorliegenden Erfindung besteht demgegenüber darin, ein Einspritzventil nach der eingangs beschriebenen Gattung derart weiterzubilden, dass bei ihm auch bei erhöhter Schliessgeschwindigkeit wie auch bei langer Bauart seines Ventilkörpers die beim Schliessen auf die Düsenkuppe des Ventils wirkende Schlagkraft nicht zu einer vorschnellen Überbelastung dieser Kuppe führt und dabei aber das Einspritzventil in seinem Aufbau nicht komplizierter gebaut ist.In contrast, the object of the present invention is to: To further develop the injection valve according to the type described in the introduction, that even with increased closing speed like even with a long design of its valve body when closing on the Nozzle tip of the valve acting too fast Overloading this tip leads to the injection valve its structure is not that complicated.

Erfindungsgemäss ist die Aufgabe dadurch gelöst, dass zwischen der die Einspritzöffnung steuernden Düsennadel und dem wenigstens einen darüberliegenden Ventilkörperteil des mehrteiligen Ventilkörpers ein mit Kraftstoff gefüllter Dämpfraum mit in jeder Position des Ventilkörpers Konstante Durchlassquerschnitte aufweisenden Zu- resp. Ableitungen gebildet ist.According to the invention the object is achieved in that between the the injection opening controlling the nozzle needle and the at least one overlying valve body part of the multi-part valve body fuel-filled damping chamber with in any position of the Valve body constant inlet cross-sections Derivatives is formed.

Mit dieser erfindungsgemässen Lösung wird eine erhebliche Dämpfung der mit erhöhter Schliessgeschwindigkeit in der Ventilspitze aufprallenden Düsennadel erzielt, da die Düsenkuppe der Ventilspitze beim unmittelbaren Aufschlagen des Ventilkörpers nicht dessen gesamte beschleunigte Masse aufnehmen muss. With this solution according to the invention there is considerable damping the one hitting the valve tip with increased closing speed Nozzle needle achieved because the nozzle tip of the valve tip at immediate impact of the valve body does not accelerate its entire Must take up mass.

Ausführungsbeispiele der Erfindung sowie weitere Vorteile derselben sind nachfolgend anhand der Zeichnung näher erläutert. Es zeigt:

Fig. 1
einen Längsschnitt durch ein erfindungsgemässes Einspritzventil,
Fig.2
einen teilweisen Längsschnitt des Einspritzventils nach der Fig. 1,
Fig.3
einen teilweisen Längsschnitt einer Variante eines Einspritzventils,
Fig.4
einen teilweisen Längsschnitt einer anderen Variante eines Einspritzventils und
Fig.5
einen teilweisen Längsschnitt einer weiteren Variante eines Einspritzventils.
Embodiments of the invention and further advantages thereof are explained in more detail below with reference to the drawing. It shows:
Fig. 1
2 shows a longitudinal section through an injection valve according to the invention,
Fig. 2
2 shows a partial longitudinal section of the injection valve according to FIG. 1,
Fig. 3
a partial longitudinal section of a variant of an injection valve,
Fig. 4
a partial longitudinal section of another variant of an injection valve and
Fig. 5
a partial longitudinal section of a further variant of an injection valve.

Fig. zeigt ein Einspritzventil 2 für eine insbesondere als Dieselmotor vorgesehene Brennkraftmaschine, welche nicht dargestellt ist. Das Einspritzventil 2 eignet sich für eine an sich herkömmliche Einspritzanlage eines Dieselmotors, so dass diesbezüglich auf eine detaillierte Erläuterung verzichtet werden kann. Es weist im wesentlichen ein mehrteiliges, auf herkömmliche Weise zusammensetzbares Ventilgehäuse 47, 53, einen darin längsverschiebbar geführten Ventilkörper 15, ein letzteren betätigendes, als Elektromagnetventil 227 ausgebildetes Steuerventil 20, eine Zuflussleitung 13 für den unter Hochdruck stehenden Kraftstoff sowie eine Abflussleitung 10 auf. Der mehrteilige Ventilkörper 15 ist im unteren Teil von einer von der Zuflussleitung 13 mit Kraftstoff gespeisten Druckkammer 14 umgeben und er schliesst oder öffnet eine in einen Arbeitszylinder des Dieselmotors führende Einspritzöffnung 4 oder deren Zuleitung, welche in der in den Arbeitszylinder ragenden Düsenkuppe 24 des Ventilgehäuses 47 enthalten ist. Im mittleren Bereich ist dieser Ventilkörper in einer Passbohrung des Ventilgehäuses 47 geführt und am oberen Ende ragt er in eine Steuerkammer 17a und ist dort fernerhin von einer Druckfeder 97 unterstützend in Schliessrichtung gedrückt. Die Steuerkammer 17a ist über das Ventil 25 und die Zuflussleitung 13 mit einem den Kraftstoff enthaltenden Hochdruckteil einerseits und über den Leitungsteil 19 und das diesen schliessbare Steuerventil 20 mit der Abflussleitung 10 andererseits verbunden. Für die Zuflussleitung 13 ist ein zum Einspritzventil 2 radialer Anschluss 92 vorgesehen, der einen das Ventilgehäuse 47 umgreifenden Anschlussring 70 und eine die Zuflussleitung 13 ans Gehäuse anpressenden Gewindemutter 72 aufweist.Fig. Shows an injection valve 2 for a particular as a diesel engine provided internal combustion engine, which is not shown. The injector 2 is suitable for a conventional injection system of a diesel engine, so that in this regard to a detailed explanation can be dispensed with. It essentially instructs Multi-part valve body that can be assembled in a conventional manner 47, 53, a longitudinally displaceably guided valve body 15, which actuates the latter and is designed as an electromagnetic valve 227 Control valve 20, an inflow line 13 for the high pressure standing fuel and a drain line 10. The Multi-part valve body 15 is in the lower part of one of the inflow line 13 surrounded by fuel-fed pressure chamber 14 and it closes or opens one in a working cylinder of the diesel engine leading injection opening 4 or its feed line, which in the in the Working cylinder protruding nozzle tip 24 of the valve housing 47 is included. In the middle area this valve body is in one Passed bore of the valve housing 47 and protrudes at the upper end into a control chamber 17a and there is also a compression spring 97 pressed in the closing direction. The control chamber 17a is with the valve 25 and the inflow line 13 with one High-pressure part containing fuel on the one hand and over the Line part 19 and this closable control valve 20 with the Drain line 10 connected on the other hand. For the inflow line 13 is a radial to the injection valve 2 connection 92 is provided, the one the connecting ring 70 encompassing the valve housing 47 and a feed line 13 has a threaded nut 72 pressing against the housing.

Erfindungsgemäss ist ein Dämpfraum 43 zwischen der die Einspritzöffnung 4 steuernden Düsennadel 15a und dem darüberliegenden Ventilkörperteil 15b des zweiteiligen Ventilkörpers 15 vorgesehen, wie dies auch in dem vergrösserten teilweisen Längsschnitt gemäss der Fig.2 verdeutlicht ist. Diesem Dämpfraum 43 ist einerseits eine zwischen der Düsennadel 15a sowie dem Ventilgehäuse 47 und andererseits eine zwischen dem Ventilkörperteil 15b und dem Ventilgehäuse 47 gebildete annähernd spielfreie Führungspassung 44, 45 vor- bzw. nachgeschaltet. Demgemäss ergibt sich einen in der Menge beschränkten Zu- bzw. Abfluss in oder aus diesem Dämpfraum 43 aus oder in die benachbarte Druckkammer 14 bzw. Kammer 49. Nebst dem bereits erwähnten erheblichen Vorteil dieser mittels dem Dämpfraum 43 bewirkten Schonung der Düsenkuppe 24 ergibt sich ein weiterer Vorzug darin, dass das Einspritzventil 2 mehrheitlich aus herkömmlichen Bestandteilen zusammengesetzt werden kann und daher nicht aufwendiger in der Herstellung wird.According to the invention, there is a damping space 43 between which the injection opening 4 controlling nozzle needle 15a and the one above it Valve body part 15b of the two-part valve body 15 is provided, such as this also in the enlarged partial longitudinal section according to FIG Fig.2 is clarified. This damping space 43 is on the one hand between the nozzle needle 15a and the valve housing 47 and on the other hand, one between the valve body part 15b and the Valve housing 47 formed almost play-free guide fit 44, 45 upstream or downstream. Accordingly, one results in the Amount of restricted inflow or outflow into or out of this steam chamber 43 out of or into the adjacent pressure chamber 14 or chamber 49. In addition to the considerable advantage already mentioned, this means that Damping space 43 causes protection of the nozzle tip 24 results Another advantage is that the injector 2 is mostly off conventional components can be assembled and therefore does not become more complex to manufacture.

Bei geschlossenem, ruhendem Einspritzventil 2 wirkt die Federkraft einer Druckfeder 97 auf den Ventilkörperteil 15b gegen die Düsennadel 15a hin und führt deren im Dämpfraum 43 befindliche Stirnseiten 16, 25 bis zu einer gegenseitigen Berührung zusammen, bevor der nächste Einspritzvorgang erfolgt, währenddem diese Stirnseiten 16, 25 nach einer Ventilöffnung sich langsam voneinander wegbewegen und zwar aufgrund des von den Druckkammern 14, 49 unter Hochdruck durch die Führungspassungen 44, 45 in den Dämpfraum 43 beschränkt fliessenden Brennstoffes und weil der mittlere Druck im Dämpfraum 43 annähernd auf den Druck der einspritzseitigen Oberfläche der Düsennadel 15a abfällt. Wenn nachfolgend der Ventilkörper 15 geschlossen wird, entsteht nur ein direkter Aufprall der relativ leichten Düsennadel 15a in der Düsenkuppe 24, indessen der ebenfalls in Schliessrichtung bewegte Ventilkörperteil 15b durch das zwischen diesem und der Düsennadel gebildete Flüssigkeitspolster abgefedert wird und dadurch die angestrebte dauerhafte Reduktion der Maximalbelastung der untersten Spitze des Einspritzventils 2 erreicht ist.The spring force acts when the injection valve 2 is closed and at rest a compression spring 97 on the valve body part 15b against the nozzle needle 15a and leads their end faces 16 located in the damping space 43, 25 to a mutual touch before the next Injection takes place while these end faces 16, 25 after a valve opening slowly move away from each other due to the high pressure from the pressure chambers 14, 49 through the Guide fits 44, 45 flowing in the damping space 43 limited Fuel and because the average pressure in the damping chamber 43 approximately to the pressure of the injection-side surface of the nozzle needle 15a falls off. If the valve body 15 is subsequently closed, there is only a direct impact of the relatively light nozzle needle 15a in the nozzle tip 24, however, also in the closing direction moved valve body part 15b by the between this and the Nozzle needle formed liquid cushion is cushioned and thereby the desired permanent reduction of the maximum load on the lowest point of the injector 2 is reached.

Nebstdem kann mit dem erfindungsgemässen Einspritzventil 2 gegenüber bekannten Lösungen die Sicherheit erhöht werden, indem beispielsweise bei einem Klemmen des Steuerventils 20 und dem damit verbundenen Offenbleiben der Einspritzöffnung 4 der Dämpfraum 43 stetig mit Brennstoff versorgt wird und folglich die Düsennadel 15a von dem Ventilkörperteil 15b bis zu einer Schliessung der Einspritzöffnung 4 wegdriftet.In addition, with the injection valve 2 according to the invention compared to known solutions, the security can be increased by for example, when the control valve 20 is jammed and thus connected, the injection opening 4 of the damping space 43 is constantly supplied with fuel and consequently the nozzle needle 15a from the valve body part 15b to a closure of the Injection opening 4 drifts away.

Dieser Dämpfraum 43 weist ferner vorzugsweise maximal ein Volumen auf, das angenähert der Querschnittsfläche der Düsennadel 15a und einer Spalthöhe von maximal zwei Millimetern entspricht.This damping space 43 also preferably has a maximum of one volume on, which approximates the cross-sectional area of the nozzle needle 15a and corresponds to a gap height of a maximum of two millimeters.

Das als Elektromagnetventil 227 ausgebildete Steuerventil 20 hat einen Steuerventilkörper 38, der durch einen unteren stirnseitigen Ventilsitz 57 den vertikalen und nachfolgend in eine waagrechte Abflussleitung 10 übergehenden Leitungsteil 19 im Ventilgehäuse 47 schliesst oder öffnet. Dieser Steuerventilkörper 38 weist eine von seinem Ventilsitz 57 ausgehende und mit dem Leitungsteil 19 kommunizierende Bohrung 60' auf, welche im Innern des Steuerventilkörpers 38 zwecks Erzeugung einer in Schliessrichtung desselben wirkenden Schliesskraft erweitert ist. Zu diesem Zwecke ist diese Bohrung 60' oben von einem im Steuerventilkörper 38 koaxial in diesem längsbeweglich angeordneten Stift 60 begrenzt, der an seinem oberen Ende unabhängig vom Steuerventilkörper 38, in dem vorliegenden Beispiel an der unteren Stirnseite eines im Magnetkern 22 angeordneten, mit genügender Härte versehener Stift abgestützt ist. Der Magnetkern 22 liegt mit seiner unteren planen Stirnseite unmittelbar auf der Folienscheibe 61 auf, welche ihrerseits dadurch auf einer ebenen Ringfläche des Ventilgehäuses fixiert ist. Im übrigen sind in dem Magnetanker 62 und seinen Nachbarteilen Ausnehmungen 66 vorgesehen, durch welche beim Bewegen des Ankers eine Umströmung des diesen umgebenden Brennstoffes ermöglicht ist. Durch eine entsprechende Wahl des Querschnittes der Ausnehmungen 66 lässt sich die Dämpfwirkung des hin- und herbewegten Steuerventilkörpers 38 einstellen. The control valve 20 designed as an electromagnetic valve 227 has one Control valve body 38 by a lower end valve seat 57 the vertical and then into a horizontal drain line 10 merging line part 19 in the valve housing 47 closes or opens. This control valve body 38 has one of its valve seat 57 outgoing and communicating with the line part 19 60 'on which inside the control valve body 38 for the purpose of generation a closing force acting in the same closing direction is. For this purpose, this bore 60 'is at the top of an Control valve body 38 arranged coaxially in this longitudinally movable Pin 60 limited, which at its upper end regardless of Control valve body 38, in the present example on the lower Front side of a arranged in the magnetic core 22, with sufficient hardness provided pin is supported. The magnetic core 22 lies with its lower one plan the end face directly on the film disk 61, which in turn is thereby on a flat ring surface of the Valve housing is fixed. Otherwise, the armature 62 and its neighboring parts provided recesses 66 through which at Movement of the armature flows around it Fuel is enabled. By an appropriate choice of Cross section of the recesses 66, the damping effect of adjust the reciprocating control valve body 38.

Bei dem dargestellten Einspritzventil 2 ist oberhalb dieser Düsennadel 15 zur Erzeugung einer erhöhten Schliessgeschwindigkeit des Ventilkörpers ein weiteres Ventil 25 angeordnet, welches über die Zuflussleitung 13 eine mit dem Hochdruckteil des Steuermediums verbundene ringförmige Kammer 28 und einen diese oben stirnseitig schliessenden ringförmigen Ventilsitz 27 aufweist, welcher beim Öffnen diese zusätzliche Verbindung zwischen dem Hochdruckteil und der Steuerkammer 17b erzeugt. Das Ventil 25 weist zweckmässigerweise einen koaxial zur Düsennadel 15 verlaufenden Ventilkörper 26 auf, der im Ventilgehäuse 47 seitlich abdichtend geführt ist. Dieser zylinderförmige Ventilkörper 26 und das Ventilgehäuse 47 bilden gemeinsam die ringförmige Kammer 28 und den diese Kammer 28 abschliessenden Ventilsitz 27. Der Ventilkörper 26 ragt dabei mit der einen, der Düsennadel 15 zugekehrten Stirnseite in die Steuerkammer 17a und mit der andern Stirnseite in eine mit der Abflussleitung 10 via das Steuerventil 20 kommunizierenden Zusatzkammer 17b, welche mit der Steuerkammer 17a über eine im Ventilkörper 26 durchgehende Drosselbohrung 23 verbunden ist und an die umfangsseitig der Ventilsitz 27 grenzt. Letzterer ist derart ausgebildet, dass der Ventilkörper 26 mit seiner oberen schrägen Ringkante im Schliesszustand abdichtend gegen eine entsprechende Ringfläche in der Gehäusebohrung anliegt und die ringförmige Kammer 28 den Ventilkörper 26 zumindest in seinem oberen Bereich umgibt. Dieser kegelförmig ausgebildete Ventilsitz 27 könnte aber auch zylindrisch oder als ebene Fläche gestaltet sein. Im übrigen ist der Ventilkörper 26 mit einer queren, die Zuflussleitung 13 mit der Steuerkammer 17b verbindenden Drosselbohrung 21 versehen, vermittels der ein permanenter Anschluss des Steuermediums vom Hochdruckteil in diese Steuerkammer erfolgt.In the illustrated injection valve 2 is above this nozzle needle 15 for generating an increased closing speed of the valve body a further valve 25 is arranged, which via the inflow line 13 one connected to the high pressure part of the control medium annular chamber 28 and a top closing this at the top has annular valve seat 27, which when opening this additional Connection between the high pressure part and the control chamber 17b generated. The valve 25 expediently has a coaxial with Nozzle needle 15 extending valve body 26 in the valve housing 47 is laterally sealing. This cylindrical valve body 26 and the valve housing 47 together form the annular chamber 28 and the valve seat 27 closing off this chamber 28. The valve body 26 protrudes with the one facing the nozzle needle 15 Face into the control chamber 17a and with the other face in one communicating with the drain line 10 via the control valve 20 Additional chamber 17b, which with the control chamber 17a via a Valve body 26 through throttle bore 23 is connected and on which borders the valve seat 27 on the circumference. The latter is like this formed that the valve body 26 with its upper oblique ring edge sealing against a corresponding ring surface in the closed state rests in the housing bore and the annular chamber 28 surrounds the valve body 26 at least in its upper region. This but conical valve seat 27 could also be cylindrical or be designed as a flat surface. Otherwise, the valve body 26 with a cross, the inflow line 13 with the control chamber 17b connecting throttle bore 21 provided by means of a permanent connection of the control medium from the high pressure part to it Tax chamber is carried out.

In Schliessstellung weist der Ventilkörper 26 einen vorgegebenen Abstand zu der unter ihr befindlichen Düsennadel 15 auf und zwischen diesen ist überdies eine dieselben auseinanderpressende Druckfeder 96 vorgesehen, währenddem in Offenstellung der Düsennadel 15, welche durch ein Freigeben des Steuerventils 20 und einem damit verbundenen Druckabfall in der Steuerkammer 17a bewirkt wird, diese Düsennadel 15a an der unteren Stirnseite 16 des Ventilkörpers 26 anschlägt. In the closed position, the valve body 26 has a predetermined distance to the nozzle needle 15 below and on and between this is also a compression spring 96 that presses them apart provided, while in the open position of the nozzle needle 15, which by releasing the control valve 20 and an associated one Pressure drop in the control chamber 17a causes this nozzle needle 15a strikes on the lower end face 16 of the valve body 26.

Unmittelbar nach Schliessung des Steuerventils 20 erfolgt einerseits durch die quere Drosselbohrung 21 ein Druckaufbau vorerst in der Zusatzkammer 17b, infolgedessen der Ventilkörper 26 gegen die Düsennadel 15a hin bewegt und damit ein selbsttätiges Öffnen des Ventilsitzes 27 bewirkt wird. Durch dieses Öffnen fliesst ein zusätzlicher Zustrom des unter Hochdruck stehenden Steuermediums in die Zusatzkammer 17b und dadurch die Düsennadel 15a von dem Ventilkörper 26 mit erhöhter Geschwindigkeit in Schliessstellung gebracht wird. Nachdem sie die Schliessposition erreicht hat, wird der Ventilkörper 26 aufgrund des Druckaufbaus in der Steuerkammer 17a und der Federkraftunterstützung der Feder 96 wieder zurück nach oben bewegt und zwar bis seine obere Ringkante in der Gehäusebohrung ansteht und sich damit der Ventilsitz 27 wiederum in Schliessstellung befindet.Immediately after the control valve 20 is closed, on the one hand through the transverse throttle bore 21, a pressure build-up initially in the Additional chamber 17b, consequently the valve body 26 against the Nozzle needle 15a moves and thus an automatic opening of the Valve seat 27 is effected. This opening flows in additional inflow of the high pressure control medium in the additional chamber 17b and thereby the nozzle needle 15a of the Valve body 26 at increased speed in the closed position brought. After it has reached the closing position, the Valve body 26 due to the pressure build-up in the control chamber 17a and the spring force support of the spring 96 back up again moves up to its upper ring edge in the housing bore is present and thus the valve seat 27 in turn in the closed position located.

Beim Einspritzventil 2 gemäss der Fig.3 ist der dargestellte Dämpfraum 43 nicht wie in dem ersten Ausführungsbeispiel unmittelbar vom Ventilgehäuse 47 sondern von einem in letzterem axial verschiebbaren Ringelement 15d umgeben, wobei letzteres das untere Ende des Ventilkörperteils 15b bildet. Die Düsennadel 15a, welche wiederum die Eintrittsöffnung 4 öffnet oder schliesst, ragt annähernd spielfrei in dieses Ringelement 15d und begrenzt zusammen mit einer über ihm im Ringelement 15 längsverschiebbar angeordneten Distanzscheibe 15c den Dämpfraum 43. Durch eine entsprechende Wahl der Länge der Distanzscheibe 15c lassen sich Längentoleranzen der von dem Ventilkörper 15 zusammen mit dem Ventilkörper 26 und der entsprechenden von den Gehäuseteilen 47, 53 gebildeten Länge ausgleichen. Die Düsennadel 15a hat zumindest im unteren Bereich einen angedeuteten unrunden Querschnitt, wodurch diese in der runden Bohrung des Ventilgehäuses einen Freiraum für die Druckkammer bildet. Ansonsten funktioniert dieses Einspritzventil 2 analog demjenigen nach der Fig. 1 und es sind daher nicht mehr alle Einzelheiten erläutert. Es hat zu dem nach der Fig. 1 den Vorteil, dass es mit einer geringeren Anzahl von zu schleifenden Oberflächen versehen ist und eine genaue Führungspassung im Gehäuse 47 entfällt, wodurch es aus einem zäheren Material hergestellt werden kann und auf jeden Fall einen hochfrequent schwingenden Hubverlauf der Düsennadel 15a erzeugt wird.The injection chamber 2 shown in FIG. 3 is the damping chamber 43 not directly as in the first embodiment Valve housing 47 but from one axially displaceable in the latter Surround ring element 15d, the latter the lower end of the Valve body part 15b forms. The nozzle needle 15a, which in turn the Inlet opening 4 opens or closes, projects into it with almost no play Ring element 15d and delimited together with one above it Ring element 15 longitudinally displaceable spacer 15c the damping space 43. By an appropriate choice of the length of the Spacer 15c can be length tolerances of the Valve body 15 together with the valve body 26 and the corresponding length formed by the housing parts 47, 53 compensate. The nozzle needle 15a has at least in the lower area an implied non-circular cross-section, which makes this in the round Bore of the valve housing forms a free space for the pressure chamber. Otherwise, this injection valve 2 works analogously to that 1 and therefore all details are no longer explained. It has the advantage according to FIG. 1 that it has a lower Number of surfaces to be sanded and an accurate Guide fit in the housing 47 is omitted, which makes it from a tougher material can be made and definitely one generated high-frequency oscillating stroke of the nozzle needle 15a becomes.

In Fig.4 ist eine weitere Variante eines Einspritzventils 2 in dem für die Erfindung massgeblichen Teil dargestellt. Es ist an sich ähnlich wie dasjenige nach der Fig.3 aufgebaut, das Ringelement 15d ist aber hierzu unabhängig von dem oberen Ventilkörperteil 15b vorgesehen. Letzterer und die Düsennadel 15a sind im Ringelement 15d bei runder Ausbildung darin annähernd spielfrei in diesem geführt. Erfindungsgemäss ist abermals ein zwischen der Düsennadel 15a und dem Ventilkörperteil 15b gebildeter Dämpfraum 43 vorgesehen. Das diesen umgebende Ringelement 15d ist als innen dichtendes Rohr ausgebildet und kann bei entsprechend dünner Wandung statt aus metallischem Werkstoff auch aus Kunststoff bestehen. Es ist über die beiden Enden der Düsennadel 15a und des Ventilkörperteils 15b gesteckt und bildet mit diesen zusammen einen festen Sitz. Dadurch ist die dämpfende Funktion des Ventilkörpers 15 etwas reduziert. Dieses Einspritzventil ist aber kostengünstig herstellbar und das darin eingesetzte Ringelement 15d kann Zugkräfte übertragen und übt eine etwas gelenkige Funktion aus. Wenn dieses Ringelement 15d innen geschliffen ist und nicht an der Düsennadel 15a und an dem Ventilkörperteil 15b festsitzt, dann dient die stirnseitig an diesem angreifende Druckfeder 97 zur Positionierung desselben.4 shows a further variant of an injection valve 2 in the for the invention relevant part shown. It is similar to itself that constructed according to FIG. 3, but the ring element 15d is for this purpose provided independently of the upper valve body part 15b. The latter and the nozzle needle 15a are round in the ring element 15d Training in this led to almost no play in this. According to the invention is again between the nozzle needle 15a and the Valve body part 15b formed damping space 43 is provided. That this surrounding ring element 15d is designed as an inner sealing tube and can with a correspondingly thin wall instead of metallic Material also consist of plastic. It's over the two ends the nozzle needle 15a and the valve body part 15b inserted and forms together with these a tight fit. This is the damping Function of the valve body 15 somewhat reduced. This injector is inexpensive to manufacture and the ring element used therein 15d can transmit tensile forces and exercises a somewhat articulated Function off. If this ring element 15d is ground on the inside and is not stuck on the nozzle needle 15a and on the valve body part 15b, then the compression spring 97 acting on the end of this serves for Positioning of the same.

Das Einspritzventil gemäss der Fig.5 hat ein Ringelement 15d ähnlich demjenigen nach der Fig.4, welches innen einen unterschiedlichen Durchmesser in dem mit der Düsennadel 15a zu dem mit dem Ventilkörperteil 15b in Verbindung stehenden Bereich aufweist. Abgestützt ist es an seiner oberen Stirnseite an der Druckfeder 97. In dem gezeigten Ausführungsbeispiel ist der Führungsquerschnitt des Ventilkörperteils 15b in dem Ringelement 15d grösser als derjenige der Düsennadel 15a. Damit wird ein vollständiger Öffnungshub der Düsennadel 15a mit geringen überlagerten Schwingungen erreicht und beim Schliessen wird die Bewegungsenergie des Ventilkörperteils 15b auf das Ringelement 15d durch die von der Durchmesserverringerung von letzterem gebildete Anschlagfläche übertragen. 5 has a ring element 15d similar that according to Fig.4, which has a different inside Diameter in that with the nozzle needle 15a to that with the Has valve body part 15b in the connected area. It is supported on its upper end face on the compression spring 97. In the exemplary embodiment shown is the guide cross section of the Valve body part 15b in the ring element 15d larger than that of the Nozzle needle 15a. So that a full opening stroke Nozzle needle 15a with slight superimposed vibrations reached and when closed, the kinetic energy of the valve body part 15b on the ring member 15d by the reduction in diameter transferred from the latter formed stop surface.

Grundsätzlich könnte der Dämpfraum 43 über je eine zu den Führungspassungen parallelgeschaltete Drosselbohrung zusätzlich mit der Druckkammer verbunden sein.In principle, the damping space 43 could each have one of the guide fits throttle bore connected in parallel with the Pressure chamber to be connected.

Bei dem in die Steuerkammern fliessenden Steuermedium handelt es sich im Normalfall um Kraftstoff, welcher gleichsam in die Speicherkammer und nachfolgend durch die Einspritzöffnungen in einen Kraftstoffzylinder eingespritzt wird. Im Prinzip könnte aber als Steuermedium ein separate Flüssigkeit verwendet werden, während der Kraftstoff nur für die Einspritzung vorgesehen wäre.It is the control medium flowing into the control chambers is usually fuel, which as it were in the storage chamber and subsequently through the injection openings into a fuel cylinder is injected. In principle, however, could be used as a control medium a separate liquid can be used while the fuel would only be provided for injection.

Ferner könnte der Dämpfraum 43 mit einer vom Einspritzventil wegführenden, einen geringeren Druck als die Druckkammer aufweisenden Leckölrücklaufleitung verbunden sein.Furthermore, the damping space 43 could be provided with a a lower pressure than the pressure chamber Leak oil return line must be connected.

Die Druckkammer 49 könnte im Prinzip einen niederen Druck entsprechend der Abflussleitung 10 aufweisen. Der erfindungsgemässe Effekt der Dämpfung ist gewährleistet, wenn der durch die Führungspassung 45 zu dem von der Führungspassung 44 gebildete Durchlassquerschnitt nicht mehr als zehnmal grösser ist.The pressure chamber 49 could in principle correspond to a lower pressure the drain line 10. The invention Effect of damping is ensured when the through the guide fit 45 to the passage cross section formed by the guide fit 44 is not more than ten times larger.

Die Erfindung ist mit den oben erläuterten Ausführungsbeispielen ausreichend dargetan. Als ergänzende Variante wäre denkbar, dass die Düsennadel 15a zweiteilig ausgeführt sein könnte und der Dämpfraum oberhalb dieser zweiteiligen Düsennadel angeordnet wäre.The invention is with the exemplary embodiments explained above adequately demonstrated. As a supplementary variant, it would be conceivable that the Nozzle needle 15a could be made in two parts and the damping chamber would be arranged above this two-part nozzle needle.

Claims (10)

  1. Injection valve (2) for a fuel injection system of an internal combustion engine, particularly of a Diesel engine, having a valve housing (47, 53), a multiple part valve body (15) displaceably mounted within said housing and with at least one inlet opening (4) leading into a working cylinder through which a fuel supply issuing from a pressure chamber (14) takes place by a separate control of the valve body (15), characterized in that there is formed between a nozzle needle (15a) controlling the injection opening (4) and at least one body part (15b) arranged above it of said multiple part valve body (15) and a damping chamber (43) filled with fuel, said chamber having in each position of the valve body (15) supply and discharge passages with constant throughflow sections.
  2. Injection valve (2) as claimed in claim 1, characterized in that said damping chamber (43) is preceded or followed respectively by a guiding passage (44, 45) substantially free from play and formed on the one hand between the nozzle needle (15a) and the valve housing (47) and on the other hand between said valve body part (15b) and the valve housing (47), said damping chamber (43) being therefore connected with said fuel containing pressure chamber (14).
  3. Injection valve (2) as claimed in claim 1 or 2, characterized in that with the injection valve (2) closed a supporting spring force is acting on said valve body part (15b), thereby displacing the later towards the nozzle needle (15a) until mutual contact of their front faces (16), whilst the latter with the inlet opening (4) in open state are spaced from each other in a defined slow manner due to the limited supply of fuel from the pressure chamber (14) into the damping chamber (43).
  4. Injection valve (2) as claimed in any of the foregoing claims, characterized in that said damping chamber (43) is additionally connected with the pressure chamber (14) by throttle bores extending each parallely to said guiding passages (44, 45).
  5. Injection valve (2) as claimed in any of the foregoing claims, characterized in that the damping chamber (43) is connected via at least one guiding passage (45) with a leakoil return duct having a lower pressure than the pressure chamber (14) and extending away from the injection valve (2).
  6. Injection valve as claimed in any of the foregoing claims, characterized in that the damping chamber (43) is directly enclosed by said valve housing (47) or by a ring element (15d) which is stationary or displaceable axially within said valve housing.
  7. Injection valve as claimed in claim 6, characterized in that said ring element (15d) is guided as part of said valve body part (15b) or independently of said valve housing (47).
  8. Injection valve (2) as claimed in claim 6 or 7, characterized in that the nozzle needle (15a) and a spacer (15c) mounted thereon are guided substantially without play in said ring element (15d) and in that said damping chamber (43) is enclosing said spacer (15c).
  9. Injection valve (2) as claimed in any of the foregoing claims, characterized in that the nozzle needle (15a) in its part projecting into the damping chamber (43) presents a cross section which is larger or smaller than that of the adjacent valve body part (15b).
  10. Injection valve (2) as claimed in claim 6, characterized in that the guiding cross section of said valve body part (15b) in the ring element (15d) is larger than that of the nozzle needle (15a), such that during closing the displacement energy of the valve body part (15b) is transmitted onto the ring element (15d) by an abutment surface formed by the reduction of the diameter of the latter.
EP95103560A 1994-05-02 1995-03-13 Injection valve for a fuel injection system of an internal combustion engine, particularly of a diesel engine Expired - Lifetime EP0685645B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
CH01358/94A CH689267A5 (en) 1994-05-02 1994-05-02 An injection valve for a fuel injection system of an internal combustion engine, especially a diesel engine.
CH1358/94 1994-05-02
CH135894 1994-05-02

Publications (3)

Publication Number Publication Date
EP0685645A2 EP0685645A2 (en) 1995-12-06
EP0685645A3 EP0685645A3 (en) 1997-03-26
EP0685645B1 true EP0685645B1 (en) 2001-06-06

Family

ID=4208593

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95103560A Expired - Lifetime EP0685645B1 (en) 1994-05-02 1995-03-13 Injection valve for a fuel injection system of an internal combustion engine, particularly of a diesel engine

Country Status (6)

Country Link
US (1) US5692683A (en)
EP (1) EP0685645B1 (en)
JP (1) JP3710163B2 (en)
AT (1) ATE201920T1 (en)
CH (1) CH689267A5 (en)
DE (1) DE59509315D1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012130452A1 (en) 2011-03-31 2012-10-04 Fuechslin Raphael Injection valve

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19917190A1 (en) * 1999-04-16 2000-10-26 Mtu Friedrichshafen Gmbh Fuel injector for internal combustion engine; has high pressure channel to supply fuel and nozzle needle in guide bore and has high pressure space behind guide bore to receive overflowing fuel
JP4066959B2 (en) * 2004-01-27 2008-03-26 株式会社デンソー Fuel injection device
FR2871876B1 (en) * 2004-06-21 2006-09-29 Valeo Climatisation Sa HEAT EXCHANGE DEVICE HAVING SEVERAL ROWS OF TUBES, ESPECIALLY FOR MOTOR VEHICLES
US7900604B2 (en) * 2005-06-16 2011-03-08 Siemens Diesel Systems Technology Dampening stop pin
JP6137030B2 (en) * 2014-04-10 2017-05-31 株式会社デンソー Fuel injection valve

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Publication number Priority date Publication date Assignee Title
DE2710138A1 (en) * 1977-03-09 1978-09-14 Maschf Augsburg Nuernberg Ag MULTI-HOLE INJECTION NOZZLE
GB2096701A (en) * 1981-04-11 1982-10-20 Lucas Industries Ltd I.C. engine fuel injection nozzles
DE3220398A1 (en) * 1982-01-26 1983-07-28 Robert Bosch Gmbh, 7000 Stuttgart FUEL INJECTION NOZZLE FOR INTERNAL COMBUSTION ENGINES
US4566635A (en) * 1983-08-10 1986-01-28 Robert Bosch Gmbh Fuel injection nozzle for internal combustion engines
GB8809269D0 (en) * 1988-04-20 1988-05-25 Lucas Ind Plc Fuel injection nozzle
EP0343147A3 (en) * 1988-05-16 1990-10-03 Steyr-Daimler-Puch Aktiengesellschaft Injection valve for air-compressing fuel injection engines
DE3844373A1 (en) * 1988-12-30 1990-07-05 Mak Maschinenbau Krupp Method and apparatus for setting a defined nozzle opening pressure of an injection valve
US5156132A (en) * 1989-04-17 1992-10-20 Nippondenso Co., Ltd. Fuel injection device for diesel engines
DE4126698A1 (en) * 1991-08-13 1992-10-15 Daimler Benz Ag Fuel injection nozzle for IC engine - has two flow connections between spring and damper chambers, for alternately dampened/non-dampener opening stroke

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012130452A1 (en) 2011-03-31 2012-10-04 Fuechslin Raphael Injection valve
DE102011015753A1 (en) 2011-03-31 2012-10-04 Raphael Füchslin Injector

Also Published As

Publication number Publication date
EP0685645A3 (en) 1997-03-26
EP0685645A2 (en) 1995-12-06
US5692683A (en) 1997-12-02
DE59509315D1 (en) 2001-07-12
JP3710163B2 (en) 2005-10-26
JPH0842422A (en) 1996-02-13
CH689267A5 (en) 1999-01-15
ATE201920T1 (en) 2001-06-15

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