EP0392187B1 - Control device for shutting down a diesel internal combustion engine - Google Patents

Control device for shutting down a diesel internal combustion engine Download PDF

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Publication number
EP0392187B1
EP0392187B1 EP90104259A EP90104259A EP0392187B1 EP 0392187 B1 EP0392187 B1 EP 0392187B1 EP 90104259 A EP90104259 A EP 90104259A EP 90104259 A EP90104259 A EP 90104259A EP 0392187 B1 EP0392187 B1 EP 0392187B1
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EP
European Patent Office
Prior art keywords
valve
suction
control device
feed pump
pressure
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP90104259A
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German (de)
French (fr)
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EP0392187A1 (en
Inventor
Heinz Dipl.-Ing. Kuschmierz
Reinhard Dipl.-Ing. Fenchel
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Robert Bosch GmbH
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Robert Bosch GmbH
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D33/00—Controlling delivery of fuel or combustion-air, not otherwise provided for
    • F02D33/003—Controlling the feeding of liquid fuel from storage containers to carburettors or fuel-injection apparatus ; Failure or leakage prevention; Diagnosis or detection of failure; Arrangement of sensors in the fuel system; Electric wiring; Electrostatic discharge
    • F02D33/006—Controlling the feeding of liquid fuel from storage containers to carburettors or fuel-injection apparatus ; Failure or leakage prevention; Diagnosis or detection of failure; Arrangement of sensors in the fuel system; Electric wiring; Electrostatic discharge depending on engine operating conditions, e.g. start, stop or ambient conditions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D17/00—Controlling engines by cutting out individual cylinders; Rendering engines inoperative or idling
    • F02D17/04—Controlling engines by cutting out individual cylinders; Rendering engines inoperative or idling rendering engines inoperative or idling, e.g. caused by abnormal conditions
    • 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
    • F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
    • F02M37/0011—Constructional details; Manufacturing or assembly of elements of fuel systems; Materials therefor
    • F02M37/0023—Valves in the fuel supply and return system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0205—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively for cutting-out pumps or injectors in case of abnormal operation of the engine or the injection apparatus, e.g. over-speed, break-down of fuel pumps or injectors ; for cutting-out pumps for stopping the engine
    • F02M63/0215—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively for cutting-out pumps or injectors in case of abnormal operation of the engine or the injection apparatus, e.g. over-speed, break-down of fuel pumps or injectors ; for cutting-out pumps for stopping the engine by draining or closing fuel conduits
    • 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

Definitions

  • the invention relates to a control device for stopping a diesel internal combustion engine according to the generic preamble of the main claim.
  • Such a control device is already known from DE-OS 30 14 712, in which the delivery pump can be reversed by means of a reversing valve for stopping the internal combustion engine and the suction chamber of the fuel injection pump is connected to the suction side of the delivery pump and the pressure side of the delivery pump to the tank.
  • This device is intended to generate a vacuum in the suction space, supplemented by two vacuum-tight check valves, one in the inlet and one in the return of the fuel injection pump. So much fuel is withdrawn from the suction space of the fuel injection pump that the fuel injection pump can no longer deliver fuel and the diesel engine stops.
  • the reversing valve is a separate component which is separate from the feed pump and to which four lines are assigned at its connections.
  • These many hose connections can be the starting point of malfunctions of the Be an internal combustion engine, especially if one takes into account the vibration stress of a diesel unit and the associated load on the line connection points.
  • control device designed with the characterizing features of the main claim, has the advantage over the prior art that the previous management effort of the control device can be eliminated.
  • the arrangement and design of the control device according to the invention as a unit integrated into the feed pump improves the functional and operational safety of the injection system for the internal combustion engine with a reduced maintenance effort derived therefrom, on the other hand there are structural advantages due to the simplified design of the control device and a reduced space requirement and economic advantages due to the reduced material and assembly costs.
  • FIG. 1 The first exemplary embodiment of the control device is shown in FIG. 1 in a normal operating position and in FIG. 2 in a stop position, while in FIG. 3 the second exemplary embodiment of the control device is again shown in the normal operating position.
  • the first exemplary embodiment shown schematically in FIG. 1, shows a feed pump 10, which is inserted into the fuel circuit of a fuel injection pump 9 for operating an internal combustion engine and is known per se and which, in normal use, is mounted on the injection pump in the engagement area of a cam 11.
  • the feed pump 10, which works on the displacement principle, is encompassed by a pump housing 12 and the force is introduced into the feed pump 10 by means of the stroke of the cam 11 via a piston rod 14 onto a feed piston 16 which can be displaced in the direction of an arrow 18.
  • the delivery piston 16 During its inward stroke, in the direction of arrow 18, the delivery piston 16 is displaced counter to the restoring force of a prestressed working spring 20, the delivery piston 16 moving fuel into a working space 22 when the delivery pump 10 is ready for operation.
  • the working space 22 is delimited by one end face of the delivery piston 16, a suction valve 25 which, in the closed state, blocks the working space 22 from a suction line 26 connected to the tank 27 and by a pressure valve 28 and accommodates a stationary bearing block 24 .
  • the other end of the delivery piston 16 closes a displacement chamber 30 in the pump housing 12, which opens into a pressure line 32, which in turn is connected to a suction chamber 33 of the fuel injection pump 9.
  • the suction valve 25 forms a switching element 34 in a rigid coupling by means of a coupling member 60 with the pressure valve 28.
  • the suction valve 25 has a first valve seat support 35 which forms an interior 36 in which a valve closing member 38 is arranged with a base body 40 designed as a plate
  • the base body 40 carries closing surfaces 42, 44 formed on both sides as ring seat surfaces, a front closing surface 42 facing the suction line 26 and a rear closing surface 44 facing the working space 22. Both closing surfaces 42, 44 are opposite corresponding valve seats 43, 45 on the first valve seat carrier 35, and a front valve seat 43 and a rear valve seat 45.
  • a guide element 46 is attached to the base body 40 in the center thereof, perpendicular to the closing surfaces 42, 44, which is guided in a first bore 48 of the bearing block 24 and here for a valve spring 50 a first spring abutment 51 forms.
  • This valve spring 50 partially surrounds the guide element 46 and presses against the base body 40 on the side of the rear closing surface 44.
  • the base body 40 In extension to the valve spring 50, the base body 40 is opposed on the side of the front closing surface 42 by an additional valve spring 52 which is supported on a first auxiliary spring abutment 53 fixed to the housing and whose length dimension is not sufficient to engage the base body in the first exemplary embodiment shown in FIG 40 to come.
  • the first valve seat carrier 35 has a sealing displaceability within the working space 22 on its outer contour.
  • the first valve seat support 35 is rigidly coupled to a part of the pressure valve 28, a second valve seat support 65 via the coupling member 60, which can be displaced by a control element 62 connected to it within a bearing in the bearing block 24 in the direction of movement of the first guide element 46.
  • the pressure valve 28 is constructed in the same way as the suction valve 25 and thus has the same assignment and corresponding design: the second valve seat carrier 65, an interior 66, a valve closing member 68, a base body 70, an annular front closing surface 72, a front valve seat 73, an annular rear closing surface 74, a rear valve seat 75, a guide element 76 which is guided in a second bore 78, which runs in the pump housing 12, with a valve spring 80, a second spring abutment 81, an additional valve spring 82, which is on a second Additional spring abutment 83, which is formed on the valve body 24, supports and whose length dimension is not sufficient to come into engagement with the base body 70 in the first exemplary embodiment shown in FIG.
  • the volume flowing out of the working chamber 22 does not reach the pressure line 32, since it essentially compensates for the vacuum level left in the displacement chamber 30 by the delivery piston 16.
  • a delivery from the tank 27 via the feed pump 10 to the fuel injection pump 9 is thus shown.
  • the described delivery direction of the feed pump 10 is reversible by moving the actuator 62 in the direction of arrow 90 and the switching element 34 rigidly coupled to it from a normal operating position as shown in FIG. 1 to a stop position as shown in FIG. 2.
  • the two valve seat supports 35, 65 in the illustration according to FIG. 2 come into a position in which the pressure valve 28 takes over the function of a suction valve and the suction valve 25 takes over the function of a pressure valve.
  • the displacement of the two valve seat supports 35, 65 also changes the position of the two valve closing members 38, 68, both base bodies 40, 70 detaching from the front valve seats 43, 73 with their front closing surfaces 42, 72 and with their rear closing surfaces 44, 74 come into contact with the rear valve seats 45, 74, lose the frictional connection with the valve springs 50, 80 and come into engagement with the additional valve springs 52, 82.
  • the pressure valve 28 which works as a suction valve, opens and the fuel ejected can flow into the working space 22, where it largely compensates for the negative pressure created by the volume expansion of the working space 22.
  • FIG. 3 In a constructive modification of the first exemplary embodiment according to FIGS. 1 and 2, a functionally equivalent solution is disclosed in FIG. 3 on the basis of a second exemplary embodiment.
  • FIG. 3 corresponding to FIG. 1, the normal operating position of the coupling member 160 is shown; However, its stop position is no longer shown, since the associated action sequences in the feed pump 110 run in the same sense as shown in FIG. 2 in the first exemplary embodiment.
  • the suction valve is 125 and that Modified pressure valve 128 so that the two valve seat supports 135, 165 are fixed to the housing and the switching function is performed by the movable spring abutments 151, 181 or additional spring abutments 153, 183, which can also be arranged offset by 90 °.
  • the spring abutments 151, 181 and additional abutments 153, 183 are connected to the coupling member 160, which can be moved by the actuator 62 from the normal operating position shown in the stop position.
  • valve springs 150, 180 load the base body 140, 170, so that the suction valve 125 and the pressure valve 128 are initially closed.
  • the spring abutments 151, 181 or additional spring abutments 153, 183 are displaced such that the base bodies 140, 170 lose the frictional connection to the valve springs 150, 180 and under the action of force the additional valve springs 152, 182 come, whereby the function reversal is achieved in the suction valve 125 and in the pressure valve 128 and thus also in the feed pump 110.
  • control device as a structural unit integrated in the feed pump 10, 110 improves the functional and operational safety of the injection system for the internal combustion engine and achieves economic advantages through reduced material and assembly costs.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Steuereinrichtung zum Stillsetzen einer Dieselbrennkraftmaschine nach dem gattungsbildenden Oberbegriff des Hauptanspruchs.The invention relates to a control device for stopping a diesel internal combustion engine according to the generic preamble of the main claim.

Durch die DE-OS 30 14 712 ist bereits eine solche Steuereinrichtung bekannt, bei der zum Stillsetzen der Brennkraftmaschine die Förderpumpe mittels eines Umsteuerventils umsteuerbar ist und der Saugraum der Kraftstoffeinspritzpumpe mit der Saugseite der Förderpumpe und die Druckseite der Förderpumpe mit dem Tank verbunden wird. Diese Einrichtung ist zur Erzeugung eines Unterdruckes im Saugraum, ergänzt durch zwei unterdruckdichte Rückschlagventile, je eines im Zu- und im Rücklauf der Kraftstoffeinspritzpumpe, bestimmt. Damit wird dem Saugraum der Kraftstoffeinspritzpumpe soviel Kraftstoff entzogen, daß die Kraftstoffeinspritzpumpe keinen Kraftstoff mehr fördern kann und die Dieselbrennkraftmaschine stehenbleibt.Such a control device is already known from DE-OS 30 14 712, in which the delivery pump can be reversed by means of a reversing valve for stopping the internal combustion engine and the suction chamber of the fuel injection pump is connected to the suction side of the delivery pump and the pressure side of the delivery pump to the tank. This device is intended to generate a vacuum in the suction space, supplemented by two vacuum-tight check valves, one in the inlet and one in the return of the fuel injection pump. So much fuel is withdrawn from the suction space of the fuel injection pump that the fuel injection pump can no longer deliver fuel and the diesel engine stops.

Bei dieser bekannten Steuereinrichtung ist jedoch das Umsteuerventil ein von der Förderpumpe getrenntes separates Bauteil, dem an seinen Anschlüssen vier Leitungen zugeordnet sind. Diese vielen Schlauchverbindungen können der Ausgangspunkt von Betriebsstörungen der Brennkraftmaschine sein, insbesondere, wenn man die Schwingungsbeanspruchung eines Dieselaggregats und die damit verbundene Belastung der Leitungsverbindungsstellen mit in Betracht zieht.In this known control device, however, the reversing valve is a separate component which is separate from the feed pump and to which four lines are assigned at its connections. These many hose connections can be the starting point of malfunctions of the Be an internal combustion engine, especially if one takes into account the vibration stress of a diesel unit and the associated load on the line connection points.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße, mit den kennzeichnenden Merkmalen des Hauptanspruchs ausgestaltete Steuereinrichtung hat dem gegenüber den Vorteil, daß der bisherige Leitungsaufwand der Steuereinrichtung entfallen kann. Die erfindungsgemäße Anordnung und Ausführung der Steuereinrichtung als in die Förderpumpe integrierte Baueinheit verbessert zum einen die Funktions- und Betriebssicherheit des Einspritzsystems für die Brennkraftmaschine mit einem daraus abgeleiteten reduzierten Wartungsaufwand, zum anderen ergeben sich konstruktive Vorteile durch die vereinfachte Gestaltung der Steuereinrichtung sowie ein verringerter Bauraumbedarf und wirtschaftliche Vorteile wegen des verminderten Material- und Montageaufwands.The control device according to the invention, designed with the characterizing features of the main claim, has the advantage over the prior art that the previous management effort of the control device can be eliminated. The arrangement and design of the control device according to the invention as a unit integrated into the feed pump improves the functional and operational safety of the injection system for the internal combustion engine with a reduced maintenance effort derived therefrom, on the other hand there are structural advantages due to the simplified design of the control device and a reduced space requirement and economic advantages due to the reduced material and assembly costs.

Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen der im Hauptanspruch angegebenen Steuereinrichtung erreichbar. So ist durch die kennzeichneten Merkmale des Anspruchs 2 eine sichere Betriebsweise und gemäß Anspruch 3 auch die Möglichkeit gegeben, die Hauptelemente der Steuereinrichtung, das sind die beiden Ventilsitzträger, feststehend und, die zugeordneten Federwiderlager als Schaltelement über ein Stellglied verschiebbar zu gestalten, wodurch zum einen die bewegten Massen geringer werden und zum anderen keine nachteiligen Auswirkungen durch Verkanten oder wegen Fluchtungsfehlern auftreten, was eine toleranzentfeinerte Fertigung ermöglicht.Advantageous further developments and improvements of the control device specified in the main claim can be achieved by the measures listed in the subclaims. So is characterized by the features of claim 2, a safe operation and according to claim 3 also the possibility to design the main elements of the control device, that is, the two valve seat supports, and to design the associated spring abutment as a switching element via an actuator, whereby on the one hand the moving masses are reduced and, on the other hand, there are no adverse effects due to tilting or misalignment, which enables tolerance-reduced production.

Zeichnungdrawing

Zwei Ausführungsbeispiele der Erfindung sind in der Zeichnung im Schnitt dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es wird das erste Ausführungsbeispiel der Steuereinrichtung in Figur 1 in einer Normalbetriebsstellung und in Figur 2 in einer Stoppstellung gezeigt, während in Figur 3 das zweite Ausführungsbeispiel der Steuereinrichtung wiederum in der Normalbetriebsstellung dargestellt ist.Two embodiments of the invention are shown in section in the drawing and explained in more detail in the following description. The first exemplary embodiment of the control device is shown in FIG. 1 in a normal operating position and in FIG. 2 in a stop position, while in FIG. 3 the second exemplary embodiment of the control device is again shown in the normal operating position.

Beschreibung der AusführungsbeispieleDescription of the embodiments

Das in Figur 1 schematisch dargestellte erste Ausführungsbeispiel zeigt eine in den Kraftstoffkreislauf einer Kraftstoffeinspritzpumpe 9 zum Betrieb einer Brennkraftmaschine eingefügte und an sich bekannte Förderpumpe 10, die im üblichen Gebrauch im Eingriffsbereich eines Nockens 11 an der Einspritzpumpe angebaut ist. Die nach dem Verdrängerprinzip arbeitende Förderpumpe 10 wird von einem Pumpengehäuse 12 umfaßt und durch den Hub des Nockens 11 erfolgt die Krafteinleitung in die Förderpumpe 10 über eine Kolbenstange 14 auf einen Förderkolben 16, der in der Richtung eines Pfeiles 18 verschiebbar ist.The first exemplary embodiment, shown schematically in FIG. 1, shows a feed pump 10, which is inserted into the fuel circuit of a fuel injection pump 9 for operating an internal combustion engine and is known per se and which, in normal use, is mounted on the injection pump in the engagement area of a cam 11. The feed pump 10, which works on the displacement principle, is encompassed by a pump housing 12 and the force is introduced into the feed pump 10 by means of the stroke of the cam 11 via a piston rod 14 onto a feed piston 16 which can be displaced in the direction of an arrow 18.

Bei seinem Einwärtshub, in Richtung des Pfeiles 18, wird der Förderkolben 16 entgegen der Rückstellkraft einer vorgespannten Arbeitsfeder 20 verschoben, wobei der Förderkolben 16 bei betriebsbereiter Förderpumpe 10 Kraftstoff in einen Arbeitsraum 22 verschiebt.During its inward stroke, in the direction of arrow 18, the delivery piston 16 is displaced counter to the restoring force of a prestressed working spring 20, the delivery piston 16 moving fuel into a working space 22 when the delivery pump 10 is ready for operation.

Der Arbeitsraum 22 wird innerhalb des Pumpengehäuses 12 von der einen Stirnseite des Förderkolbens 16, einem Saugventil 25, das in geschlossenem Zustand den Arbeitsraum 22 von einer mit dem Tank 27 verbundenen Saugleitung 26 absperrt und von einem Druckventil 28 begrenzt und nimmt einen ortsfesten Lagerbock 24 auf.Within the pump housing 12, the working space 22 is delimited by one end face of the delivery piston 16, a suction valve 25 which, in the closed state, blocks the working space 22 from a suction line 26 connected to the tank 27 and by a pressure valve 28 and accommodates a stationary bearing block 24 .

Die andere Stirnseite des Förderkolbens 16 schließt im Pumpengehäuse 12 einen Verdrängungsraum 30 ab, der in eine Druckleitung 32 mündet, die wiederum mit einem Saugraum 33 der Kraftstoffeinspritzpumpe 9 in Verbindung steht.The other end of the delivery piston 16 closes a displacement chamber 30 in the pump housing 12, which opens into a pressure line 32, which in turn is connected to a suction chamber 33 of the fuel injection pump 9.

Das Saugventil 25 bildet in einer starren Kopplung mittels eines Kopplungsgliedes 60 mit dem Druckventil 28 ein Schaltelement 34. Das Saugventil 25 weist einen ersten Ventilsitzträger 35 auf, der einen Innenraum 36 bildet, in dem ein Ventilschließglied 38 angeordnet ist mit einem als Platte ausgebildeten Grundkörper 40. Der Grundkörper 40 trägt beidseitig als Ringsitzflächen ausgebildete Schließflächen 42, 44, eine der Saugleitung 26 zugewandte vordere Schließfläche 42 und eine dem Arbeitsraum 22 zugewandte hintere Schließfläche 44. Beiden Schließflächen 42, 44 stehen am ersten Ventilsitzträger 35 entsprechende Ventilsitze 43, 45 gegenüber, und zwar ein vorderer Ventilsitz 43 und ein hinterer Ventilsitz 45. Dem Lagerbock 24 zugewandt ist am Grundkörper 40 in dessen Zentrum senkrecht zu den Schließflächen 42, 44 ein Führungselement 46 angebracht, das in einer ersten Bohrung 48 des Lagerbocks 24 geführt ist und hier für eine Ventilfeder 50 ein erstes Federwiderlager 51 bildet. Diese Ventilfeder 50 umgibt das Führungselement 46 partiell und drückt vorgespannt gegen den Grundkörper 40 auf der Seite der hinteren Schließfläche 44.The suction valve 25 forms a switching element 34 in a rigid coupling by means of a coupling member 60 with the pressure valve 28. The suction valve 25 has a first valve seat support 35 which forms an interior 36 in which a valve closing member 38 is arranged with a base body 40 designed as a plate The base body 40 carries closing surfaces 42, 44 formed on both sides as ring seat surfaces, a front closing surface 42 facing the suction line 26 and a rear closing surface 44 facing the working space 22. Both closing surfaces 42, 44 are opposite corresponding valve seats 43, 45 on the first valve seat carrier 35, and a front valve seat 43 and a rear valve seat 45. Facing the bearing block 24, a guide element 46 is attached to the base body 40 in the center thereof, perpendicular to the closing surfaces 42, 44, which is guided in a first bore 48 of the bearing block 24 and here for a valve spring 50 a first spring abutment 51 forms. This valve spring 50 partially surrounds the guide element 46 and presses against the base body 40 on the side of the rear closing surface 44.

In Verlängerung zur Ventilfeder 50 steht dem Grundkörper 40 auf der Seite der vorderen Schließfläche 42 eine Zusatzventilfeder 52 entgegen, die auf einem gehäusefesten ersten Zusatzfederwiderlager 53 abgestützt ist und deren Längenmaß nicht ausreicht, um bei dem in Figur 1 gezeigten ersten Ausführungsbeispiel in Eingriff mit dem Grundkörper 40 zu kommen.In extension to the valve spring 50, the base body 40 is opposed on the side of the front closing surface 42 by an additional valve spring 52 which is supported on a first auxiliary spring abutment 53 fixed to the housing and whose length dimension is not sufficient to engage the base body in the first exemplary embodiment shown in FIG 40 to come.

Der erste Ventilsitzträger 35 weist an seiner Außenkontur eine dichtende Verschiebbarkeit innerhalb des Arbeitsraumes 22 auf. Des weiteren ist der erste Ventilsitzträger 35 über das Kopplungsglied 60, welches von einem mit ihm verbundenen Stellglied 62 innerhalb einer Lagerung im Lagerbock 24 in der Bewegungsrichtung des ersten Führungselements 46 verschiebbar ist, mit einem Teil des Druckventils 28, einem zweiten Ventilsitzträger 65 starr gekoppelt.The first valve seat carrier 35 has a sealing displaceability within the working space 22 on its outer contour. Of Furthermore, the first valve seat support 35 is rigidly coupled to a part of the pressure valve 28, a second valve seat support 65 via the coupling member 60, which can be displaced by a control element 62 connected to it within a bearing in the bearing block 24 in the direction of movement of the first guide element 46.

Das Druckventil 28 ist gleichartig wie das Saugventil 25 aufgebaut und weist somit in gleicher Zuordnung und in entsprechender Ausbildung auf: Den zweiten Ventilsitzträger 65, einen Innenraum 66, ein Ventilschließglied 68, einen Grundkörper 70, eine ringförmige vordere Schließfläche 72, einen vorderen Ventilsitz 73, eine ringförmige hintere Schließfläche 74, einen hinteren Ventilsitz 75, ein Führungselement 76, das in einer zweiten Bohrung 78, die im Pumpengehäuse 12 verläuft, geführt ist, mit einer Ventilfeder 80, einem zweiten Federwiderlager 81, einer Zusatzventilfeder 82, die sich auf einem zweiten Zusatzfederwiderlager 83, das am Ventilkörper 24 gebildet ist, abstützt und deren Längenmaß nicht ausreicht, um bei dem in Figur 1 gezeigten ersten Ausführungsbeispiel in Eingriff mit dem Grundkörper 70 zu kommen.The pressure valve 28 is constructed in the same way as the suction valve 25 and thus has the same assignment and corresponding design: the second valve seat carrier 65, an interior 66, a valve closing member 68, a base body 70, an annular front closing surface 72, a front valve seat 73, an annular rear closing surface 74, a rear valve seat 75, a guide element 76 which is guided in a second bore 78, which runs in the pump housing 12, with a valve spring 80, a second spring abutment 81, an additional valve spring 82, which is on a second Additional spring abutment 83, which is formed on the valve body 24, supports and whose length dimension is not sufficient to come into engagement with the base body 70 in the first exemplary embodiment shown in FIG.

Die zuvor beschriebene Anordnungsdarstellung ergibt folgenden Funktions- und Wirkungsablauf. Ausgehend von einem nockengesteuerten Einwärtshub des Förderkolbens 12 in Richtung des Pfeiles 18 verringert dieser das Volumen des Arbeitsraumes 22, wodurch im Arbeitsraum 22 der Druck ansteigt. Dadurch wird beim Saugventil 25, bei dem, hervorgerufen durch die Vorspannung der Ventilfeder 50, die vordere Schließfläche 42 gegen den vorderen Ventilsitz 43 gedrückt wird, die Schließwirkung weiter unterstützt.The arrangement representation described above results in the following functional and effect sequence. Starting from a cam-controlled inward stroke of the delivery piston 12 in the direction of arrow 18, the latter reduces the volume of the working space 22, as a result of which the pressure in the working space 22 increases. As a result, the closing action is further supported in the suction valve 25, in which, caused by the pretensioning of the valve spring 50, the front closing surface 42 is pressed against the front valve seat 43.

Hingegen wird beim Druckventil 28, bei dem, hervorgerufen durch die Vorspannung der Ventilfeder 80, die vordere Schließfläche 72 gegen den vorderen Ventilsitz 73 gedrückt wird, das Ventilschließglied 68 entgegen der Rückstellkraft der Ventilfeder 80 betätigt und dadurch, einen normalen Arbeitshub des Förderkolbens 16 vorausgesetzt, das Druckventil 28 geöffnet.On the other hand, in the pressure valve 28, in which, caused by the pretension of the valve spring 80, the front closing surface 72 is pressed against the front valve seat 73, the valve closing member 68 is actuated against the restoring force of the valve spring 80 and thereby, assuming a normal working stroke of the delivery piston 16, the pressure valve 28 opened.

Das aus dem Arbeitsraum 22 abströmende Volumen gelangt jedoch nicht in die Druckleitung 32, da es im wesentlichen das durch den Förderkolben 16 im Verdrängungsraum 30 hinterlassene Unterdruckniveau ausgleicht.However, the volume flowing out of the working chamber 22 does not reach the pressure line 32, since it essentially compensates for the vacuum level left in the displacement chamber 30 by the delivery piston 16.

Beim nockengesteuerten Auswärtshub des Förderkolbens 12 entgegen der Richtung des Pfeiles 18 bleibt die Kolbenstange 14 infolge der mittelbar auf sie einwirkenden Rückstellkraft der vorgespannten Arbeitsfeder 20 in Kraftschluß mit der zurückweichenden Nockenbahn. Dabei wird im Arbeitsraum 22 ein Unterdruck erzeugt, der die Schließstellung am Druckventil 28 unterstützt und das Saugventil 25 öffnet.During the cam-controlled outward stroke of the delivery piston 12 against the direction of arrow 18, the piston rod 14 remains in positive engagement with the retracting cam track due to the restoring force of the prestressed working spring 20 acting indirectly on it. In this case, a negative pressure is generated in the working space 22, which supports the closed position on the pressure valve 28 and opens the suction valve 25.

Verbunden mit der Abwärtsbewegung des Förderkolbens 16 ist des weiteren eine Verringerung des Volumens im Verdrängungsraum 30. Durch die Schließlage des Druckventils 28 gelangt der Kraftstoff nun nicht mehr in den Arbeitsraum 22 zurück, sondern wird in die Druckleitung 32 der Förderpumpe 10 zum Saugraum 33 der Kraftstoffeinspritzpumpe 9 hin verdrängt.Connected to the downward movement of the delivery piston 16 is further a reduction in the volume in the displacement space 30. Due to the closed position of the pressure valve 28, the fuel no longer comes back into the working area 22, but instead becomes into the pressure line 32 of the delivery pump 10 to the suction area 33 of the fuel injection pump 9 ousted.

Damit ist ein Arbeitszyklus, bestehend aus einem Einwärts- und einem Auswärtshub des Förderkolbens 16 bei sich in einer Normalbetriebsstellung befindlichem Schaltelement 34 vollzogen, wobei während des Einwärtshubs des Förderkolbens 16 Kraftstoff aus dem Arbeitsraum 22 in den Verdrängungsraum 30 verlagert und während des Abwärtshubs des Förderkolbens 16 Kraftstoff aus dem Verdrängungsraum 30 zum Saugraum 33 der Kraftstoffeinspritzpumpe 9 hin verdrängt wird und zugleich Kraftstoff aus dem Tank 27 in den Arbeitsraum 22 nachströmt.This completes a work cycle consisting of an inward and an outward stroke of the delivery piston 16 when the switching element 34 is in a normal operating position, fuel being shifted from the work chamber 22 into the displacement chamber 30 during the inward stroke of the delivery piston 16 and during the downward stroke of the Delivery piston 16 fuel is displaced from the displacement chamber 30 to the suction chamber 33 of the fuel injection pump 9 and at the same time fuel flows from the tank 27 into the working chamber 22.

Somit ist eine Förderung vom Tank 27 über die Förderpumpe 10 zur Kraftstoffeinspritzpumpe 9 dargestellt.A delivery from the tank 27 via the feed pump 10 to the fuel injection pump 9 is thus shown.

Die geschilderte Förderrichtung der Förderpumpe 10 ist umkehrbar durch eine Verschiebung des Stellgliedes 62 in Richtung des Pfeiles 90 und des mit ihr starr gekoppelten Schaltelements 34 von einer Normalbetriebsstellung entsprechend der Darstellung nach Figur 1 in eine Stoppstellung entsprechend der Darstellung nach Figur 2.The described delivery direction of the feed pump 10 is reversible by moving the actuator 62 in the direction of arrow 90 and the switching element 34 rigidly coupled to it from a normal operating position as shown in FIG. 1 to a stop position as shown in FIG. 2.

Abweichend von Figur 1 gelangen die beiden Ventilsitzträger 35, 65 in der Darstellung nach Figur 2 in eine Lage, in der das Druckventil 28 die Funktion eines Saugventils und das Saugventil 25 die Funktion eines Druckventils übernimmt. Durch die Verlagerung der beiden Ventilsitzträger 35, 65 verändert sich auch die Position der beiden Ventilschließglieder 38, 68, wobei sich beide Grundkörper 40, 70 mit ihren vorderen Schließflächen 42, 72 von den vorderen Ventilsitzen 43, 73 lösen, mit ihren hinteren Schließflächen 44, 74 zur Anlage an die hinteren Ventilsitze 45, 74 kommen, den Kraftschluß mit den Ventilfedern 50, 80 verlieren und in Eingriff kommen mit den Zusatzventilfedern 52, 82.In a departure from FIG. 1, the two valve seat supports 35, 65 in the illustration according to FIG. 2 come into a position in which the pressure valve 28 takes over the function of a suction valve and the suction valve 25 takes over the function of a pressure valve. The displacement of the two valve seat supports 35, 65 also changes the position of the two valve closing members 38, 68, both base bodies 40, 70 detaching from the front valve seats 43, 73 with their front closing surfaces 42, 72 and with their rear closing surfaces 44, 74 come into contact with the rear valve seats 45, 74, lose the frictional connection with the valve springs 50, 80 and come into engagement with the additional valve springs 52, 82.

Bei einem Einwärtshub des Förderkolbens 16 in Richtungs des Pfeils 18 erhöht sich der Druck im Arbeitsraum 22, das als Saugventil arbeitende Druckventil 28 wird in seiner Schließwirkung unterstützt, das als Druckventil arbeitende Saugventil 25 öffnet entgegen der Rückstellkraft der Zusatzventilfeder 52 so weit, daß Kraftstoff den Grundkörper 40 umströmen kann und aus dem Saugraum 22 zum Tank 27 gelangt, wodurch sich der Druck im Arbeitsraum 22 wieder absenkt. Andererseits entsteht durch den Einwärtshub des Förderkolbens 16 durch Volumenvergrößerung im Verdrängungsraum 30 Unterdruck, der sich bei geschlossenem, als Saugventil arbeitendem Druckventil 28 nicht über den Arbeitsraum 22 ausgleichen kann, sondern zu einer Kraftstoffabsaugung aus dem Saugraum 33 der Kraftstoffeinspritzpumpe 9 über die Druckleitung 32 zum Verdrängungsraum 30 führt.With an inward stroke of the delivery piston 16 in the direction of arrow 18, the pressure in the working space 22 increases, the pressure valve 28 working as a suction valve is supported in its closing action, the suction valve 25 working as a pressure valve opens against the restoring force of the additional valve spring 52 so far that fuel the Can flow around the base body 40 and from the suction chamber 22 to the tank 27 arrives, whereby the pressure in the working space 22 drops again. On the other hand, due to the inward stroke of the delivery piston 16 due to volume increase in the displacement chamber 30, negative pressure is created which, when the pressure valve 28 working as a suction valve is closed, cannot be compensated for via the working chamber 22, but rather for fuel extraction from the suction chamber 33 of the fuel injection pump 9 via the pressure line 32 to the displacement chamber 30 leads.

Bei einem Auswärtshub des Förderkolbens 16 entgegen der Richtung des Pfeiles 18 schiebt der Förderkolben 16 Kraftstoff aus dem Verdrängungsraum 30 aus. Dabei öffnet sich das als Saugventil arbeitende Druckventil 28 und der ausgeschobene Kraftstoff kann in den Arbeitsraum 22 einfließen, wo er den durch die Volumenerweiterung des Arbeitsraumes 22 entstandene Unterdruck weitgehend ausgleicht.When the delivery piston 16 moves outward in the opposite direction of the arrow 18, the delivery piston 16 pushes fuel out of the displacement space 30. The pressure valve 28, which works as a suction valve, opens and the fuel ejected can flow into the working space 22, where it largely compensates for the negative pressure created by the volume expansion of the working space 22.

Abweichend von der in Figur 1 dargestellten Normalbetriebsstellung des ersten Ausführungsbeispiels findet bei der in Figur 2 dargestellten Stoppstellung des ersten Ausführungsbeispiels eine Kraftstoffverlagerung beim Auswärtshub und eine Kraftstofförderung beim Einwärtshub des Förderkolbens 16 statt, wobei die Richtung der Kraftstofförderung jetzt vom Saugraum 33 der Kraftstoffeinspritzpumpe 9 über die Förderpumpe 10 zum Tank 27 erfolgt.Deviating from the normal operating position of the first exemplary embodiment shown in FIG. 1, in the stop position of the first exemplary embodiment shown in FIG. 2, fuel is displaced during the outward stroke and fuel is conveyed during the inward stroke of the delivery piston 16, the direction of fuel delivery now being from the suction space 33 of the fuel injection pump 9 via the Delivery pump 10 to the tank 27 takes place.

In konstruktiver Abwandlung des ersten Ausführungsbeispiels nach Figur 1 und 2 wird in Figur 3 anhand eines zweiten Ausführungsbeispiels eine funktionell gleichwirkende Lösung offenbart.In a constructive modification of the first exemplary embodiment according to FIGS. 1 and 2, a functionally equivalent solution is disclosed in FIG. 3 on the basis of a second exemplary embodiment.

In der Figur 3 ist dabei, der Figur 1 entsprechend, die Normalbetriebsstellung des Kopplungsgliedes 160 gezeigt; nicht mehr dargestellt ist jedoch dessen Stoppstellung, da die damit verbundenen Wirkungsabläufe in der Förderpumpe 110 in gleichem Sinne verlaufen wie beim ersten Ausführungsbeispiel in Figur 2 gezeigt. Bei dem zweiten Ausführungsbeispiel ist das Saugventil 125 und das Druckventil 128 so abgewandelt, daß die beiden Ventilsitzträger 135, 165 gehäusefest sind und die Umschaltfunktion von den beweglich ausgeführten Federwiderlagern 151, 181 bzw. Zusatzfederwiderlagern 153, 183, die auch um 90° versetzt angeordnet sein können, wahrgenommen wird.In FIG. 3, corresponding to FIG. 1, the normal operating position of the coupling member 160 is shown; However, its stop position is no longer shown, since the associated action sequences in the feed pump 110 run in the same sense as shown in FIG. 2 in the first exemplary embodiment. In the second embodiment, the suction valve is 125 and that Modified pressure valve 128 so that the two valve seat supports 135, 165 are fixed to the housing and the switching function is performed by the movable spring abutments 151, 181 or additional spring abutments 153, 183, which can also be arranged offset by 90 °.

Die Federwiderlager 151, 181 bzw. Zusatzwiderlager 153, 183 sind mit dem Kopplungsglied 160 verbunden, welches durch das Stellglied 62 von der gezeichneten Normalbetriebslage in die Stoppstellung verschiebbar ist.The spring abutments 151, 181 and additional abutments 153, 183 are connected to the coupling member 160, which can be moved by the actuator 62 from the normal operating position shown in the stop position.

In der in Figur 3 dargestellten Normalbetriebslage belasten die Ventilfedern 150, 180 die Grundkörper 140, 170, so daß das Saugventil 125 und das Druckventil 128 anfangs geschlossen sind.In the normal operating position shown in Figure 3, the valve springs 150, 180 load the base body 140, 170, so that the suction valve 125 and the pressure valve 128 are initially closed.

Beim Einwärtshub des Förderkolbens 16 in Richtung des Pfeiles 18 entgegen der Rückstellkraft der vorgespannten Kolbenarbeitsfeder 20 verlagert sich unter Öffnung des Druckventils 128 Kraftstoff vom Arbeitsraum 22 zum Verdrängungsraum 30, während beim Auswärtshub des Förderkolbens 16 entgegen der Richtung des Pfeiles 18 einerseits der Kraftstoffeinspritzpumpe 9 über die Druckleitung 32 Kraftstoff aus dem Verdrängungsraum 30 zugeliefert wird, andererseits dem Arbeitsraum 22 Kraftstoff vom Tank 27 über die Saugleitung 26 durch das nun geöffnete Saugventil 125 zufließt.During the inward stroke of the delivery piston 16 in the direction of arrow 18 against the restoring force of the prestressed piston working spring 20, fuel is displaced from the working chamber 22 to the displacement chamber 30 while opening the pressure valve 128, while during the outward stroke of the delivery piston 16 against the direction of arrow 18 on the one hand the fuel injection pump 9 via the Pressure line 32 fuel is supplied from the displacement chamber 30, on the other hand, fuel flows into the working chamber 22 from the tank 27 via the suction line 26 through the now opened suction valve 125.

Beim Übergang des Kopplungsgliedes 160 in Richtung des Pfeiles 190 von der Normalbetriebslage in die Stoppstellung verlagern sich die Federwiderlager 151, 181 bzw. Zusatzfederwiderlager 153, 183 so, daß die Grundkörper 140, 170 den Kraftschluß zu den Ventilfedern 150, 180 verlieren und unter die Kraftwirkung der Zusatzventilfedern 152, 182 kommen, wodurch beim Saugventil 125 und beim Druckventil 128 und damit auch bei der Förderpumpe 110 die Funktionsumkehr erreicht wird.At the transition of the coupling member 160 in the direction of arrow 190 from the normal operating position to the stop position, the spring abutments 151, 181 or additional spring abutments 153, 183 are displaced such that the base bodies 140, 170 lose the frictional connection to the valve springs 150, 180 and under the action of force the additional valve springs 152, 182 come, whereby the function reversal is achieved in the suction valve 125 and in the pressure valve 128 and thus also in the feed pump 110.

Mit der Kraftstoffabsaugung vom Saugraum 33 der Kraftstoffeinspritzpumpe 9 mittels der Förderpumpe 110 zum Tank 27 wird der Kraftstoffeinspritzpumpe 9 die Grundlage für die eigene Kraftstofförderung entzogen und damit die Brennkraftmaschine sicher abgestellt.With the fuel extraction from the suction chamber 33 of the fuel injection pump 9 by means of the feed pump 110 to the tank 27, the basis for the own fuel delivery is withdrawn from the fuel injection pump 9 and the internal combustion engine is thus safely shut off.

Durch die erfindungsgemäße Ausführung der Steuereinrichtung als in die Förderpumpe 10, 110 integrierte Baueinheit wird die Funktions- und Betriebssicherheit des Einspritzsystems für die Brennkraftmaschine verbessert und wirtschaftliche Vorteile durch reduzierten Material- und Montageaufwand erzielt.The design of the control device according to the invention as a structural unit integrated in the feed pump 10, 110 improves the functional and operational safety of the injection system for the internal combustion engine and achieves economic advantages through reduced material and assembly costs.

Claims (5)

  1. Control device for stopping a diesel internal combustion engine having a feed pump (10) which, in normal operation, induces fuel from a tank (27) via a suction conduit (26) and, during the delivery stroke, delivers it via a pressure conduit (32) to a suction space (33) of a fuel injection pump (9), the pump housing (12) of which feed pump (10) has at least one suction valve (25) and one pressure valve (28) in a working space (22), having a switching element (34) influencing the effective delivery direction of the feed pump (10), which switching element (34) can be switched from a normal operating position which does not influence the fuel delivery of the feed pump (10) from the suction conduit (26) to the pressure conduit (32) into a stop position in which a reversed operation occurs in which the feed pump (10) induces the fuel from the suction space (33) of the fuel injection pump (9) and delivers it to the tank (27), characterised in that the switching element (34) is integrated into the feed pump (10) and is connected to the at least two valves (25, 28) by a coupling element (60) which can be displaced by means of a setting element (62) into the stop position in which the valves (25, 28) reach a position in which the valve springs (50, 80) of the suction valve (25) and of the pressure valve (28) are ineffective and an additional valve spring (52, 82) comes respectively into engagement, the force effect of these additional valve springs (52, 82) causing the suction valve (25) to operate as a pressure valve and the pressure valve (28) to operate as a suction valve so that the feed pump (10) induces fuel from the pressure conduit (32) and delivers it to the suction conduit (26).
  2. Control device according to Claim 1, characterised in that each of the two valves (25, 28) has a valve seat carrier (35, 65) which permits displacement within the working space (22) of the feed pump (10) while sealing at its outer contour, the first valve seat carrier (35) limiting the working space (22) in the direction of the tank (27) and the second valve seat carrier (65) limiting the working space (22) in the direction of the suction space (33) of the fuel injection pump (9), and that there is an inner space (36, 66) with two mutually opposite valve seats (43, 45; 73, 75) in each of the valve seat carriers (35, 65), a double-acting valve closing element (38, 68) coming alternatively into contact with the sealing surfaces of the valve seats (43, 45; 73, 75) (Figures 1 and 2).
  3. Control device according to Claim 1, characterised in that each of the two valves (125, 128) has two spring abutments (151, 153; 181, 183) accepting one end each of the valve springs (150, 180) and the additional valve springs (152, 182) and one fixed location valve seat carrier (135, 165) each situated between the spring abutments (151, 153; 181, 183), both of which valve seat carriers (135, 165) contain, in one inner space (36, 66) each, two mutually opposite valve seats (43, 45; 73, 75) on whose sealing surfaces, the closing surfaces (42, 44; 72, 74) of one valve closing element (138, 168) each come alternately into contact and in fact, under the action of the valve springs (150, 180) when the coupling element (160) is in the normal operating position or, after switching of the coupling element (160) by the setting element, into its stop position under the action of the additional valve springs (152, 182) (Figure 3).
  4. Control device according to Claim 1 or 2, characterised in that the valve closing elements (38, 68) of the suction valve (25) and of the pressure valve (28) are similarly constructed with, in each case, a basic body (40, 70) containing two opposite closing surfaces (42, 44; 72, 74), which basic body (40, 70) is provided on at least one side with a guide element (46, 76) extending along the longitudinal axis of the valve (25, 28), penetrating the valve springs (50, 80) and the additional valve springs (52, 82) with movement clearance and guided in the pump housing (12).
  5. Control device according to Claim 4, characterised in that the basic body (40, 70) of the valve closing element (38, 68) has two preferably flat closing surfaces (42, 44; 72, 74) and each of the valve seats (43, 45; 73, 75) is provided with an annular seating surfaces (sic) located symmetrically with respect to the longitudinal axis, matched to the associated closing surface (42, 44; 72, 74) and permitting form closure.
EP90104259A 1989-04-13 1990-03-06 Control device for shutting down a diesel internal combustion engine Expired - Lifetime EP0392187B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3912145 1989-04-13
DE3912145A DE3912145A1 (en) 1989-04-13 1989-04-13 CONTROL DEVICE FOR STOPPING A DIESEL INTERNAL COMBUSTION ENGINE

Publications (2)

Publication Number Publication Date
EP0392187A1 EP0392187A1 (en) 1990-10-17
EP0392187B1 true EP0392187B1 (en) 1992-10-28

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Application Number Title Priority Date Filing Date
EP90104259A Expired - Lifetime EP0392187B1 (en) 1989-04-13 1990-03-06 Control device for shutting down a diesel internal combustion engine

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EP (1) EP0392187B1 (en)
JP (1) JPH02298659A (en)
DE (2) DE3912145A1 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4136626C1 (en) * 1991-11-07 1992-10-08 Mercedes-Benz Aktiengesellschaft, 7000 Stuttgart, De
EP1094216A3 (en) * 1999-10-21 2002-05-02 Miguel Roy Jimenez A system for reducing fuel consumption in combustion engines
DE102007052665A1 (en) * 2007-11-05 2009-05-07 Robert Bosch Gmbh Fuel overflow valve for a fuel injector and fuel injector with fuel spill valve

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5688954A (en) * 1979-12-21 1981-07-18 Nippon Denso Co Ltd Engine stopping apparatus
DE3014712A1 (en) * 1980-04-17 1981-10-22 Robert Bosch Gmbh, 7000 Stuttgart CONTROL DEVICE FOR STOPPING A DIESEL INTERNAL COMBUSTION ENGINE

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JPH02298659A (en) 1990-12-11
DE3912145A1 (en) 1990-10-18
EP0392187A1 (en) 1990-10-17
DE59000387D1 (en) 1992-12-03

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