EP0685645A2 - 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
EP0685645A2
EP0685645A2 EP95103560A EP95103560A EP0685645A2 EP 0685645 A2 EP0685645 A2 EP 0685645A2 EP 95103560 A EP95103560 A EP 95103560A EP 95103560 A EP95103560 A EP 95103560A EP 0685645 A2 EP0685645 A2 EP 0685645A2
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EP
European Patent Office
Prior art keywords
valve body
valve
injection
injection valve
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.)
Granted
Application number
EP95103560A
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German (de)
French (fr)
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EP0685645A3 (en
EP0685645B1 (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 of an internal combustion engine, in particular a diesel engine, with a valve housing, a multi-part valve body displaceably arranged therein and with at least one inlet opening opening into a working cylinder, through which a fuel supply emanating from a pressure chamber takes place by controlling the valve body.
  • a generic injection valve according to EP-A1 0 393 590 has a multi-part assembly which can be assembled and a means therein a solenoid valve which is arranged to be longitudinally displaceable and which comprises a nozzle needle controlling the fuel injection and a piston-like extension part arranged coaxially to it and composed of a lower part which is guided in the housing and a lower part with a reduced diameter.
  • a control valve provided between the electromagnetic valve and the extension part causes a gradual increase in the injection quantity of the fuel into a combustion cylinder at the beginning of an injection. With such an injection valve, an increased closing speed of the nozzle needle is also achieved, which, as a positive effect, reduces the exhaust gas emissions of the internal combustion engine, which usually has several such injection valves.
  • the two-part valve body is relatively long and therefore has a correspondingly large mass, there is a risk that the nozzle tip will be overloaded by the nozzle needle when the injection opening is closed and may lead to cracks or even breakage thereof. This in turn has the consequence that such cracks or breaks cause leaks leading into the combustion cylinder.
  • the object of the present invention is to develop an injection valve of the type described in the introduction in such a way that even with increased closing speed and with a long design of its valve body, the impact force acting on the nozzle tip of the valve when closing does not lead to a premature overload of this tip and the structure of the injection valve is not that complicated.
  • the object is achieved in that a damping space filled with fuel is formed between the nozzle needle controlling the injection opening and the at least one overlying valve body part of the multi-part valve body.
  • the injection valve 2 for an internal combustion engine which is provided in particular as a diesel engine and which is not shown.
  • the injection valve 2 is suitable for a conventional injection system of a diesel engine, so that a detailed explanation can be dispensed with in this regard. It essentially has a multi-part valve housing 47, 53 which can be assembled in a conventional manner, a valve body 15 which is guided longitudinally displaceably therein, a control valve 20 which actuates the latter and is designed as an electromagnetic valve 227, an inflow line 13 for the fuel under high pressure and an outflow line 10.
  • the multi-part valve body 15 is surrounded in the lower part by a pressure chamber 14 supplied with fuel by the inflow line 13 and it closes or opens an injection opening 4 leading into a working cylinder of the diesel engine or its feed line, which extends into the nozzle tip 24 of the valve housing 47 projecting into the working cylinder is included.
  • this valve body In the central region, this valve body is guided in a fitting bore in the valve housing 47 and at the upper end it projects into a control chamber 17a and is further pressed there in the closing direction by a compression spring 97.
  • the control chamber 17a is connected via the valve 25 and the inflow line 13 with a high-pressure part containing the fuel on the one hand and via the line part 19 and the control valve 20 which can be closed with the Drain line 10 connected on the other hand.
  • a radial connection 92 to the injection valve 2 is provided for the inflow line 13, which has a connecting ring 70 encompassing the valve housing 47 and a threaded nut 72 pressing the inflow line 13 against the housing.
  • a damping space 43 is provided between the nozzle needle 15a controlling the injection opening 4 and the valve body part 15b above it of the two-part valve body 15, as is also illustrated in the enlarged partial longitudinal section according to FIG. 2.
  • this damping space 43 is preceded or followed by an almost play-free guide fit 44, 45 formed between the nozzle needle 15a and the valve housing 47 and, on the other hand, between the valve body part 15b and the valve housing 47. Accordingly, there is a limited inflow or outflow into or out of this damping space 43 from or into the adjacent pressure chamber 14 or chamber 49. In addition to the considerable advantage already mentioned, this protects the nozzle tip 24 by means of the damping space 43
  • Another advantage is that the majority of the injection valve 2 can be composed of conventional components and therefore does not become more complex to manufacture.
  • 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, meanwhile the valve body part 15b, which is also moved in the closing direction, is cushioned by the liquid cushion formed between it and the nozzle needle and thereby the desired permanent reduction of the maximum load of the lowest tip of the injection valve 2 has been reached.
  • the safety can be increased, for example, when the control valve 20 is jammed and the injection opening 4 remains open, the damping chamber 43 is continuously 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 volume that corresponds approximately to the cross-sectional area of the nozzle needle 15a and a gap height of a maximum of two millimeters.
  • the control valve 20, designed as an electromagnetic valve 227, has a control valve body 38, which closes or opens the vertical line part 19 in the valve housing 47, which subsequently merges into a horizontal drain line 10, through a lower end valve seat 57.
  • This control valve body 38 has a bore 60 'which starts from its valve seat 57 and communicates with the line part 19 and which is widened in the interior of the control valve body 38 for the purpose of generating a closing force acting in the closing direction thereof.
  • this bore 60 ' is delimited at the top by a pin 60, which is arranged coaxially in the control valve body 38 and is longitudinally movably arranged at its upper end independently of the control valve body 38, in the present example on the lower end face of a pin arranged in the magnetic core 22, with sufficient hardness provided pin is supported.
  • the lower end face of the magnetic core 22 lies directly on the film disk 61, which in turn is thereby fixed on a flat annular surface of the valve housing.
  • recesses 66 are provided in the magnet armature 62 and its neighboring parts, through which the fuel surrounding the armature can flow around when the armature is moved.
  • the damping effect of the reciprocating control valve body 38 can be set by a corresponding choice of the cross section of the recesses 66.
  • a further valve 25 is arranged above this nozzle needle 15 in order to produce an increased closing speed of the valve body, said valve having an annular chamber 28 connected to the high-pressure part of the control medium via the inflow line 13 and an annular valve seat 27 closing it at the top on the front side, which when opening this additional connection between the high pressure part and the control chamber 17b generated.
  • the valve 25 expediently has a valve body 26 which extends coaxially to the nozzle needle 15 and is guided laterally in a sealing manner in the valve housing 47. This cylindrical valve body 26 and the valve housing 47 together form the annular chamber 28 and the valve seat 27 that closes off this chamber 28.
  • the valve body 26 projects with one end facing the nozzle needle 15 into the control chamber 17a and with the other end into one with the Drain line 10 via the additional chamber 17b communicating with the control valve 20, which is connected to the control chamber 17a via a throttle bore 23 which is continuous in the valve body 26 and adjoins the circumferential side of the valve seat 27.
  • the latter is designed in such a way that the valve body 26 with its upper oblique ring edge lies in the closed state in a sealing manner against a corresponding ring surface in the housing bore and the annular chamber 28 surrounds the valve body 26 at least in its upper region.
  • This conical valve seat 27 could also be cylindrical or a flat surface.
  • the valve body 26 is provided with a transverse throttle bore 21 connecting the inflow line 13 to the control chamber 17b, by means of which the control medium is permanently connected from the high-pressure part into this control chamber.
  • valve body 26 In the closed position, the valve body 26 is at a predetermined distance from the nozzle needle 15 located beneath it, and a compression spring 96 which presses it apart is provided between them, while in the open position the nozzle needle 15, which is released by releasing the control valve 20 and a pressure drop associated therewith Control chamber 17a is caused, this nozzle needle 15a strikes the lower end face 16 of the valve body 26.
  • the transverse throttle bore 21 builds up pressure in the additional chamber 17b, as a result of which the valve body 26 moves against the nozzle needle 15a and thus causes the valve seat 27 to open automatically.
  • an additional inflow of the high-pressure control medium flows into the additional chamber 17b and, as a result, the nozzle needle 15a is brought into the closed position by the valve body 26 at an increased speed.
  • the valve body 26 is moved back up again due to the pressure build-up in the control chamber 17a and the spring force support of the spring 96, namely until its upper ring edge abuts the housing bore and the valve seat 27 is again in the closed position.
  • the illustrated damping space 43 is not, as in the first exemplary embodiment, directly surrounded by the valve housing 47 but by an annular element 15d which is axially displaceable in the latter, the latter forming the lower end of the valve body part 15b.
  • the nozzle needle 15a which in turn opens or closes the inlet opening 4, projects almost without play into this ring element 15d and, together with a spacer 15c arranged above it in the ring element 15, delimits the damping space 43.
  • Length tolerances can be selected by a corresponding choice of the length of the spacer 15c compensate for the length formed by the valve body 15 together with the valve body 26 and the corresponding length formed by the housing parts 47, 53.
  • the nozzle needle 15a has, at least in the lower region, a non-circular cross-section, as a result of which it forms a free space for the pressure chamber in the round bore of the valve housing. Otherwise, this injection valve 2 functions analogously to that according to FIG. 1 and therefore all details are no longer explained. It has the advantage according to FIG. 1 that it is provided with a smaller number of surfaces to be ground and there is no precise guiding fit in the housing 47, as a result of which it can be produced from a tougher material and in any case one high-frequency oscillating stroke of the nozzle needle 15a is generated.
  • FIG. 4 shows a further variant of an injection valve 2 in the part relevant to the invention. It is constructed in a manner similar to that according to FIG. 3, but the ring element 15d is provided for this purpose independently of the upper valve body part 15b. The latter and the nozzle needle 15a are guided in the ring element 15d with a round design with almost no play therein. According to the invention, a damping space 43 is again provided between the nozzle needle 15a and the valve body part 15b.
  • the ring element 15d surrounding this is designed as an internally sealing tube and, with a correspondingly thin wall, can also consist of plastic instead of a metallic material. It is placed over the two ends of the nozzle needle 15a and the valve body part 15b and forms a tight fit together with them.
  • this injection valve is inexpensive to manufacture and the ring element 15d used therein can transmit tensile forces and has a somewhat articulated function. 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 face serves to position the same.
  • the valve body 5 has a ring element 15d similar to that according to FIG. 4, which has a different inside diameter in the area connected to the nozzle needle 15a to the area connected to the valve body part 15b. 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 is larger than that of the nozzle needle 15a. A complete opening stroke of the nozzle needle 15a is thus achieved with slight superimposed vibrations and upon closing the kinetic energy of the valve body part 15b is transmitted to the ring element 15d through the stop surface formed by the diameter reduction of the latter.
  • damping space 43 could additionally be connected to the pressure chamber via a throttle bore connected in parallel with the guide fits.
  • control medium flowing into the control chambers is normally fuel which is, as it were, injected into the storage chamber and subsequently through the injection openings into a fuel cylinder.
  • a separate liquid could be used as the control medium, while the fuel would only be provided for the injection.
  • damping chamber 43 could be connected to a leakage oil return line leading away from the injection valve and having a lower pressure than the pressure chamber.
  • the pressure chamber 49 could have a low pressure corresponding to the drain line 10.
  • the damping effect according to the invention is ensured if the passage cross section through the guide fitting 45 to the passage cross section formed by the guide fitting 44 is not more than ten times larger.
  • the invention is sufficiently demonstrated with the exemplary embodiments explained above.
  • the nozzle needle 15a could be made in two parts and the damping space would be arranged above this two-part nozzle needle.

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

Abstract

The 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 of an internal combustion engine, in particular a diesel engine, with a valve housing, a multi-part valve body displaceably arranged therein and with at least one inlet opening opening into a working cylinder, through which a fuel supply emanating from a pressure chamber takes place by controlling the valve body.

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 assembly which can be assembled and a means therein a solenoid valve which is arranged to be longitudinally displaceable and which comprises a nozzle needle controlling the fuel injection and a piston-like extension part arranged coaxially to it and composed of a lower part which is guided in the housing and a lower part with a reduced diameter. A control valve provided between the electromagnetic valve and the extension part causes a gradual increase in the injection quantity of the fuel into a combustion cylinder at the beginning of an injection. With such an injection valve, an increased closing speed of the nozzle needle is also achieved, which, as a positive effect, reduces the exhaust gas emissions of the internal combustion engine, which usually has several such injection valves. However, because the two-part valve body is relatively long and therefore has a correspondingly large mass, there is a risk that the nozzle tip will be overloaded by the nozzle needle when the injection opening is closed and may lead to cracks or even breakage thereof. This in turn has the consequence that such cracks or breaks cause leaks leading into the combustion cylinder.

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 develop an injection valve of the type described in the introduction in such a way that even with increased closing speed and with a long design of its valve body, the impact force acting on the nozzle tip of the valve when closing does not lead to a premature overload of this tip and the structure of the injection valve 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 gebildet ist.According to the invention, the object is achieved in that a damping space filled with fuel is formed between the nozzle needle controlling the injection opening and the at least one overlying valve body part of the multi-part valve body.

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, a considerable damping of the nozzle needle impinging at an increased closing speed in the valve tip is achieved, since the nozzle tip of the valve tip does not have to absorb all of its accelerated mass when the valve body strikes directly.

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.
Exemplary 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. 1 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.1 shows an injection valve 2 for an internal combustion engine which is provided in particular as a diesel engine and which is not shown. The injection valve 2 is suitable for a conventional injection system of a diesel engine, so that a detailed explanation can be dispensed with in this regard. It essentially has a multi-part valve housing 47, 53 which can be assembled in a conventional manner, a valve body 15 which is guided longitudinally displaceably therein, a control valve 20 which actuates the latter and is designed as an electromagnetic valve 227, an inflow line 13 for the fuel under high pressure and an outflow line 10. The multi-part valve body 15 is surrounded in the lower part by a pressure chamber 14 supplied with fuel by the inflow line 13 and it closes or opens an injection opening 4 leading into a working cylinder of the diesel engine or its feed line, which extends into the nozzle tip 24 of the valve housing 47 projecting into the working cylinder is included. In the central region, this valve body is guided in a fitting bore in the valve housing 47 and at the upper end it projects into a control chamber 17a and is further pressed there in the closing direction by a compression spring 97. The control chamber 17a is connected via the valve 25 and the inflow line 13 with a high-pressure part containing the fuel on the one hand and via the line part 19 and the control valve 20 which can be closed with the Drain line 10 connected on the other hand. A radial connection 92 to the injection valve 2 is provided for the inflow line 13, which has a connecting ring 70 encompassing the valve housing 47 and a threaded nut 72 pressing the inflow line 13 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, a damping space 43 is provided between the nozzle needle 15a controlling the injection opening 4 and the valve body part 15b above it of the two-part valve body 15, as is also illustrated in the enlarged partial longitudinal section according to FIG. 2. On the one hand, this damping space 43 is preceded or followed by an almost play-free guide fit 44, 45 formed between the nozzle needle 15a and the valve housing 47 and, on the other hand, between the valve body part 15b and the valve housing 47. Accordingly, there is a limited inflow or outflow into or out of this damping space 43 from or into the adjacent pressure chamber 14 or chamber 49. In addition to the considerable advantage already mentioned, this protects the nozzle tip 24 by means of the damping space 43 Another advantage is that the majority of the injection valve 2 can be composed of conventional components 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.When the injection valve 2 is closed and at rest, the spring force of a compression spring 97 acts on the valve body part 15b against the nozzle needle 15a and brings its end faces 16, 25 located in the damping space 43 together until they come into contact with one another before the next injection process takes place, while these end faces 16, 25 move slowly away from one another after a valve opening, specifically because of the fuel flowing from the pressure chambers 14, 49 under high pressure through the guide fits 44, 45 into the damping chamber 43 and because the mean pressure in the damping chamber 43 is approximately equal to the pressure of the injection-side surface of the nozzle needle 15a drops. 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, meanwhile the valve body part 15b, which is also moved in the closing direction, is cushioned by the liquid cushion formed between it and the nozzle needle and thereby the desired permanent reduction of the maximum load of the lowest tip of the injection valve 2 has been 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 safety can be increased, for example, when the control valve 20 is jammed and the injection opening 4 remains open, the damping chamber 43 is continuously 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 volume that corresponds approximately to the cross-sectional area of the nozzle needle 15a and 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 sieh die Dämpfwirkung des hin- und herbewegten Steuerventilkörpers 38 einstellen.The control valve 20, designed as an electromagnetic valve 227, has a control valve body 38, which closes or opens the vertical line part 19 in the valve housing 47, which subsequently merges into a horizontal drain line 10, through a lower end valve seat 57. This control valve body 38 has a bore 60 'which starts from its valve seat 57 and communicates with the line part 19 and which is widened in the interior of the control valve body 38 for the purpose of generating a closing force acting in the closing direction thereof. For this purpose, this bore 60 'is delimited at the top by a pin 60, which is arranged coaxially in the control valve body 38 and is longitudinally movably arranged at its upper end independently of the control valve body 38, in the present example on the lower end face of a pin arranged in the magnetic core 22, with sufficient hardness provided pin is supported. The lower end face of the magnetic core 22 lies directly on the film disk 61, which in turn is thereby fixed on a flat annular surface of the valve housing. Incidentally, recesses 66 are provided in the magnet armature 62 and its neighboring parts, through which the fuel surrounding the armature can flow around when the armature is moved. The damping effect of the reciprocating control valve body 38 can be set by a corresponding choice of the cross section of the recesses 66.

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, a further valve 25 is arranged above this nozzle needle 15 in order to produce an increased closing speed of the valve body, said valve having an annular chamber 28 connected to the high-pressure part of the control medium via the inflow line 13 and an annular valve seat 27 closing it at the top on the front side, which when opening this additional connection between the high pressure part and the control chamber 17b generated. The valve 25 expediently has a valve body 26 which extends coaxially to the nozzle needle 15 and is guided laterally in a sealing manner in the valve housing 47. This cylindrical valve body 26 and the valve housing 47 together form the annular chamber 28 and the valve seat 27 that closes off this chamber 28. The valve body 26 projects with one end facing the nozzle needle 15 into the control chamber 17a and with the other end into one with the Drain line 10 via the additional chamber 17b communicating with the control valve 20, which is connected to the control chamber 17a via a throttle bore 23 which is continuous in the valve body 26 and adjoins the circumferential side of the valve seat 27. The latter is designed in such a way that the valve body 26 with its upper oblique ring edge lies in the closed state in a sealing manner against a corresponding ring surface in the housing bore and the annular chamber 28 surrounds the valve body 26 at least in its upper region. This conical valve seat 27 could also be cylindrical or a flat surface. In addition, the valve body 26 is provided with a transverse throttle bore 21 connecting the inflow line 13 to the control chamber 17b, by means of which the control medium is permanently connected from the high-pressure part into this control chamber.

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 is at a predetermined distance from the nozzle needle 15 located beneath it, and a compression spring 96 which presses it apart is provided between them, while in the open position the nozzle needle 15, which is released by releasing the control valve 20 and a pressure drop associated therewith Control chamber 17a is caused, this nozzle needle 15a strikes 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 the transverse throttle bore 21 builds up pressure in the additional chamber 17b, as a result of which the valve body 26 moves against the nozzle needle 15a and thus causes the valve seat 27 to open automatically. As a result of this opening, an additional inflow of the high-pressure control medium flows into the additional chamber 17b and, as a result, the nozzle needle 15a is brought into the closed position by the valve body 26 at an increased speed. After it has reached the closing position, the valve body 26 is moved back up again due to the pressure build-up in the control chamber 17a and the spring force support of the spring 96, namely until its upper ring edge abuts the housing bore and the valve seat 27 is again in the closed position.

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.In the injection valve 2 according to FIG. 3, the illustrated damping space 43 is not, as in the first exemplary embodiment, directly surrounded by the valve housing 47 but by an annular element 15d which is axially displaceable in the latter, the latter forming the lower end of the valve body part 15b. The nozzle needle 15a, which in turn opens or closes the inlet opening 4, projects almost without play into this ring element 15d and, together with a spacer 15c arranged above it in the ring element 15, delimits the damping space 43. Length tolerances can be selected by a corresponding choice of the length of the spacer 15c compensate for the length formed by the valve body 15 together with the valve body 26 and the corresponding length formed by the housing parts 47, 53. The nozzle needle 15a has, at least in the lower region, a non-circular cross-section, as a result of which it forms a free space for the pressure chamber in the round bore of the valve housing. Otherwise, this injection valve 2 functions analogously to that according to FIG. 1 and therefore all details are no longer explained. It has the advantage according to FIG. 1 that it is provided with a smaller number of surfaces to be ground and there is no precise guiding fit in the housing 47, as a result of which it can be produced from a tougher material and in any case one high-frequency oscillating stroke of the nozzle needle 15a is generated.

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 part relevant to the invention. It is constructed in a manner similar to that according to FIG. 3, but the ring element 15d is provided for this purpose independently of the upper valve body part 15b. The latter and the nozzle needle 15a are guided in the ring element 15d with a round design with almost no play therein. According to the invention, a damping space 43 is again provided between the nozzle needle 15a and the valve body part 15b. The ring element 15d surrounding this is designed as an internally sealing tube and, with a correspondingly thin wall, can also consist of plastic instead of a metallic material. It is placed over the two ends of the nozzle needle 15a and the valve body part 15b and forms a tight fit together with them. As a result, the damping function of the valve body 15 is somewhat reduced. However, this injection valve is inexpensive to manufacture and the ring element 15d used therein can transmit tensile forces and has a somewhat articulated function. 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 face serves to position 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 to that according to FIG. 4, which has a different inside diameter in the area connected to the nozzle needle 15a to the area connected to the valve body part 15b. It is supported on its upper end face on the compression spring 97. In the exemplary embodiment shown, the guide cross section of the valve body part 15b in the ring element 15d is larger than that of the nozzle needle 15a. A complete opening stroke of the nozzle needle 15a is thus achieved with slight superimposed vibrations and upon closing the kinetic energy of the valve body part 15b is transmitted to the ring element 15d through the stop surface formed by the diameter reduction of the latter.

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 additionally be connected to the pressure chamber via a throttle bore connected in parallel with the guide fits.

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.The control medium flowing into the control chambers is normally fuel which is, as it were, injected into the storage chamber and subsequently through the injection openings into a fuel cylinder. In principle, however, a separate liquid could be used as the control medium, while the fuel would only be provided for the injection.

Ferner könnte der Dämpfraum 43 mit einer vom Einspritzventil wegführenden, einen geringeren Druck als die Druckkammer aufweisenden Leckölrücklaufleitung verbunden sein.Furthermore, the damping chamber 43 could be connected to a leakage oil return line leading away from the injection valve and having a lower pressure than the pressure chamber.

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.In principle, the pressure chamber 49 could have a low pressure corresponding to the drain line 10. The damping effect according to the invention is ensured if the passage cross section through the guide fitting 45 to the passage cross section formed by the guide fitting 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 sufficiently demonstrated with the exemplary embodiments explained above. As a supplementary variant, it would be conceivable that the nozzle needle 15a could be made in two parts and the damping space would be arranged above this two-part nozzle needle.

Claims (10)

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, dadurch gekennzeichnet, dass zwischen der die Einspritzöffnung (4) steuernden Düsennadel (15a) und dem wenigstens einen darüberliegenden Ventilkörperteil (15b) des mehrteiligen Ventilkörpers (15) ein mit Kraftstoff gefüllter Dämpfraum (43) gebildet ist.Injection valve for a fuel injection system of an internal combustion engine, in particular a diesel engine, with a valve housing, a multi-part valve body displaceably arranged therein and with at least one inlet opening opening into a working cylinder, through which a fuel supply originating from a pressure chamber takes place by controlling the valve body, characterized in that A damping space (43) filled with fuel is formed between the nozzle needle (15a) controlling the injection opening (4) and the at least one valve body part (15b) of the multi-part valve body (15) located above it. Einspritzventil nach Anspruch 1, dadurch gekennzeichnet, dass dem Dämpfraum (43) 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 ist und dieser Dämpfraum (43) infolgedessen mit der den Brennstoff enthaltenden Druckkammer (14) verbunden ist.Injection valve according to claim 1, characterized in that the damping space (43) has on the one hand an almost play-free guide fit (44,) formed between the nozzle needle (15a) and the valve housing (47) and on the other hand between the valve body part (15b) and the valve housing (47). 45) is connected upstream or downstream and this damping chamber (43) is consequently connected to the pressure chamber (14) containing the fuel. Einspritzventil nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass bei geschlossenem Einspritzventil (2) eine unterstützend wirkende Federkraft auf den Ventilkörperteil (15b) diesen gegen die Düsennadel (15a) hin bis zu einer gegenseitigen Berührung ihrer Stirnseiten (16) zusammenführt, während diese bei offener Einspritzöffnung (4) aufgrund des von der Druckkammer (14) in den Dämpfraum (43) beschränkt fliessenden Brennstoffes definiert langsam auseinandergehen.Injection valve according to claim 1 or 2, characterized in that when the injection valve (2) is closed, a supporting spring force acting on the valve body part (15b) brings it together against the nozzle needle (15a) up to a mutual contact of its end faces (16) while the latter open injection opening (4) due to the fuel flowing from the pressure chamber (14) into the damping space (43) limitedly slowly diverge. Einspritzventil nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Dämpfraum (43) über je eine zu den Führungspassungen parallelgeschaltete Drosselbohrung zusätzlich mit der Druckkammer (14) verbunden ist.Injection valve according to one of the preceding claims, characterized in that the damping chamber (43) is additionally connected to the pressure chamber (14) via a throttle bore connected in parallel with the guide fits. Einspritzventil nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Dämpfraum über mindestens eine Führungspassung mit einer vom Einspritzventil wegführenden, einen geringeren Druck als die Druckkammer aufweisenden Leckölrücklaufleitung verbunden ist.Injection valve according to one of the preceding claims, characterized in that the damping space is connected via at least one guide fit to a leakage oil return line leading away from the injection valve and having a lower pressure than the pressure chamber. Einspritzventil nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Dämpfraum (43) unmittelbar vom Ventilgehäuse (47) oder von einem in letzterem axial verschiebbaren oder stationären Ringelement (15d) umschlossen ist.Injection valve according to one of the preceding claims, characterized in that the damping space (43) is directly surrounded by the valve housing (47) or by an annular element (15d) which is axially displaceable or stationary in the latter. Einspritzventil nach Anspruch 6, dadurch gekennzeichnet, dass das Ringelement (15d) Teil des Ventilkörperteils (15b) oder unabhängig vom Ventilgehäuse (47) geführt ist.Injection valve according to Claim 6, characterized in that the ring element (15d) is part of the valve body part (15b) or is guided independently of the valve housing (47). Einspritzventil nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass im Ringelement (15d) die Düsennadel (15a) und eine in diesem angeordnete Distanzscheibe (15c) annähernd spielfrei geführt sind und der Dämpfraum (43) die Distanzscheibe (15c) umgibt.Injection valve according to one of the preceding claims, characterized in that the nozzle needle (15a) and a spacer (15c) arranged in the ring element (15d) are guided with almost no play and the damping space (43) surrounds the spacer (15c). Einspritzventil nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Düsennadel in dem in den Dämpfraum ragenden Bereich einen unterschiedlichen, entweder grösseren oder aber kleineren Querschnitt als derjenige des angrenzenden Ventilkörperteils aufweist.Injection valve according to one of the preceding claims, characterized in that the nozzle needle in the region projecting into the damping space has a different, either larger or smaller cross-section than that of the adjacent valve body part. Einspritzventil nach Anspruch 9, dadurch gekennzeichnet, dass der Führungsquerschnitt des Ventilkörperteils (15b) in dem Ringelement (15d) grösser als derjenige der Düsennadel (15a) ist und damit beim Schliessen die Bewegungsenergie des Ventilkörperteils (15b) auf das Ringelement (15d) durch die von der Durchmesserverringerung von letzterem gebildete Anschlagfläche übertragen wird.Injection valve according to claim 9, characterized in that the guide cross section of the valve body part (15b) in the ring element (15d) is larger than that of the nozzle needle (15a) and thus the kinetic energy of the valve body part (15b) on the ring element (15d) by the closing is transmitted by the reduction in diameter formed by the latter stop surface.
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.
CH135894 1994-05-02
CH1358/94 1994-05-02

Publications (3)

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

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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

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

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FR2871876A1 (en) * 2004-06-21 2005-12-23 Valeo Climatisation Sa HEAT EXCHANGE DEVICE HAVING SEVERAL ROWS OF TUBES, ESPECIALLY FOR MOTOR VEHICLES
WO2012130452A1 (en) * 2011-03-31 2012-10-04 Fuechslin Raphael Injection valve

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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
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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GB2096701A (en) * 1981-04-11 1982-10-20 Lucas Industries Ltd I.C. engine fuel injection nozzles
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
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 (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2871876A1 (en) * 2004-06-21 2005-12-23 Valeo Climatisation Sa HEAT EXCHANGE DEVICE HAVING SEVERAL ROWS OF TUBES, ESPECIALLY FOR MOTOR VEHICLES
WO2006008389A1 (en) * 2004-06-21 2006-01-26 Valeo Systemes Thermiques Heat exchanger device comprising several rows of tubes, particularly for motor vehicles
WO2012130452A1 (en) * 2011-03-31 2012-10-04 Fuechslin Raphael Injection valve

Also Published As

Publication number Publication date
DE59509315D1 (en) 2001-07-12
JPH0842422A (en) 1996-02-13
EP0685645A3 (en) 1997-03-26
JP3710163B2 (en) 2005-10-26
US5692683A (en) 1997-12-02
EP0685645B1 (en) 2001-06-06
CH689267A5 (en) 1999-01-15
ATE201920T1 (en) 2001-06-15

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