EP0419591B1 - Control device for stopping an internal combustion engine - Google Patents

Control device for stopping an internal combustion engine Download PDF

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Publication number
EP0419591B1
EP0419591B1 EP90902615A EP90902615A EP0419591B1 EP 0419591 B1 EP0419591 B1 EP 0419591B1 EP 90902615 A EP90902615 A EP 90902615A EP 90902615 A EP90902615 A EP 90902615A EP 0419591 B1 EP0419591 B1 EP 0419591B1
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EP
European Patent Office
Prior art keywords
feed
suction
fuel
pump
valve
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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
EP90902615A
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German (de)
French (fr)
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EP0419591A1 (en
Inventor
Klaus Krieger
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Robert Bosch GmbH
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Robert Bosch GmbH
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/30—Controlling fuel injection
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S123/00—Internal-combustion engines
    • Y10S123/02—Accumulated fuel return to tank or engine-induction system
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S123/00—Internal-combustion engines
    • Y10S123/11—Antidieseling

Definitions

  • the invention is based on a control device for stopping an internal combustion engine, in particular a diesel internal combustion engine, according to the generic preamble of the main claim.
  • a control device of the generic type in which an electrically driven feed pump with pole-changing electric motor and reversible delivery device is used to shut down the internal combustion engine in a solution variant according to FIG Fuel injection pump is connected to the suction side of the feed pump and the pressure side of the feed pump to the fuel tank.
  • a second, electrically driven feed pump in addition to a feed pump that only serves to supply the suction space of the fuel injection pump, a second, electrically driven feed pump is fitted, which only functions when the internal combustion engine is switched off. They are controlled and operated electrically by an electronic control unit that interacts with an electro-hydraulic injection pump controller.
  • This system is complex and costly and increases the risk of failure with the degree of complexity and interdependency.
  • a sufficiently rapid emergency shutdown of the internal combustion engine, in particular a diesel internal combustion engine, is ensured by the control device designed according to the invention with the characterizing features of the main claim.
  • the mechanical and thus permanently driven suction feed pump which is only intended for the extraction of the suction chamber of the fuel injection pump, guarantees that the suction chamber of the fuel injection pump is emptied as quickly as possible when the internal combustion engine is switched off. Since the pre-feed pump, which supplies the suction chamber of the internal combustion engine with fuel when the internal combustion engine is operating, is mechanically driven, there is no need for a control unit which controls both feed pumps and the drive of both feed pumps can be carried out easily via the camshaft, which is already present on the injection pump side.
  • control valve which according to claim 2 has a valve housing attached directly to the suction chamber of the fuel injection pump and in which, in accordance with the characterizing features of claim 3, there is a valve member which is cylindrical in its basic form, is simple, insensitive to dirt and compact and thus can also be advantageously integrated into the regulator cover of the fuel injection pump.
  • an inexpensive control of the control valve, for. B. realizes a so-called key stop and automatically switches off the associated internal combustion engine if the power supply is interrupted.
  • FIG. 1 shows a partial cross section through the first exemplary embodiment of a fuel injection pump designed according to the invention with cross-flushed suction chamber
  • FIG. 2 shows a partial cross section through the second exemplary embodiment of a fuel injection pump designed according to the invention with normally flushed suction chamber.
  • FIGS. 1 and 2 The two exemplary embodiments, shown schematically in FIGS. 1 and 2, of a fuel injection pump 10 designed as a multi-cylinder in-line injection pump for diesel internal combustion engines are shown with an attached control valve 12 as part of a control device 14.
  • the basic arrangement of the elements of such Fuel injection pump 10 is known per se, the configuration of the fuel injection pump 10 with a suction chamber 16 which is flushed in the first exemplary embodiment, as shown in FIG. 1, is described in detail, for example, in DE-A-3 304 335.
  • the control device 14, which essentially consists of the control valve 12, a prefeed pump 18 and a suction feed pump 20, supplies fuel to the fuel injection pump 10 during a delivery position. In contrast, fuel is withdrawn from the fuel injection pump 10 during a switch-off position of the control device 14.
  • the mechanically driven pre-feed pump 18 is a piston feed pump known per se, equipped with a suction and a pressure valve, which in practice is attached to the fuel injection pump 10 at camshaft height.
  • the prefeed pump 18 is connected on its suction side to a suction line 24 connected to a tank 22. Downstream of the pre-feed pump 18 there is a supply line 30, which receives a fuel filter 26 and a fuel accumulator 28, and which opens into a first port 32 of the control valve 12.
  • the first connection 32 corresponds to a second connection 34, to which an inlet channel 36 of the fuel injection pump 10 is connected.
  • a second connection 34 to which an inlet channel 36 of the fuel injection pump 10 is connected.
  • inlet openings 46 which open into partial suction spaces 48 designed as annular grooves, which in turn each on the other side have a return opening 52 connected to a return channel 50.
  • Each return opening 52 has a flow cross-section which is substantially smaller in relation to the cross-section of the return duct 50 and the flow cross-section of each throttle 44 in the inlet openings 46 is smaller than the flow cross-section of the associated return opening 52.
  • An overflow line 56 having a pressure-maintaining valve 54 and opening into the tank 22 connects to the return channel 50.
  • the end of the return channel 50 facing away from the overflow line 56 is connected to a third connection 58 of the control valve 12.
  • the third connection 58 corresponds to a fourth connection 60 serving as a delivery connection, to which the suction feed pump 20 is connected via a suction line 62 and which is connected downstream to the tank 22 via a tank return line 66.
  • the control valve 12 is designed as a solenoid valve and has a valve member 68, which can be brought into a conveying position and a switch-off position in a sealing manner in the inner cylindrical shape of a hollow hollow cylindrical valve housing 70 in the axial direction.
  • the valve member 68 forms, on the one hand, an incompletely closed end face 72 facing the first connection 32 and the second connection 34 and, on the other hand, a second end face 78 which is opposite the first end surface 72 and cooperates with the third connection 58 and the fourth connection 60 and which is completely is closed and which carries a hollow cylindrical wall 74 which in the area of the fourth connection 60 has a throttle duct 76 formed by a narrow bore.
  • a return spring 80 which acts on the first end face 72 and is supported in the valve housing 70, holds the valve member 68 in the delivery position, as shown in FIG. 1.
  • the control member 68 is brought into one end position by the force of the return spring 80, in which there is a hydraulic connection between the first connection 32 and the second connection 34 and the third connection 58 from the fourth connection 60 the intermediate valve member 68 is hydraulically separated.
  • the pre-feed pump 18 delivered fuel corresponding to the position of the control edge of the first end face 72 via the first connection 32 and the second connection 34 to the inlet channel 36, from which the fuel flows to the partial suction chambers 48 of the pump cylinders 42 via the throttles 44 and the inlet openings 46. Excess fuel can flow out to the tank 22 via the return openings 52, the return channel 50 and the pressure holding valve 54.
  • the fuel delivered by the pre-feed pump 18 passes via the first connection 32, the perforated first end face 72 to the throttle duct 76 and through it to the fourth connection 60 and from here further via the suction line 62, the suction feed pump 20 and the tank return line 66 to the tank 22 back.
  • This fuel flow is restricted by the flow cross section of the throttle channel 76 so that, on the one hand, there is a minimum flow for self-lubrication of the mechanical, permanently driven suction feed pump 20, and on the other hand the filling of the pump cylinders 42 in the main flow is not yet weakened in a functionally impairing manner.
  • the internal combustion engine is deprived of the fuel required for the injection, on the one hand no longer supplying fuel to the suction space 16 of the associated fuel injection pump 10, and on the other hand the fuel located in the suction space 16 of the fuel injection pump 10 is extracted.
  • the valve member 68 is brought into the other end position against the force of the return spring 80, in which the connection between the first connection 32 and the second connection 34 is blocked by the control edge of the first end face 72 and by the position the control edge of the second end face 78, the third connection 58 is hydraulically connected to the fourth connection 60.
  • the fuel supplied by the pre-feed pump 18 thus does not reach the partial suction chambers 48 or the throttle duct 76 fourth connection 60, since the throttle channel 76 has been displaced by the axial displacement of the control member 68 into the other end position from the pull-in area of the fourth connection 60. Nevertheless, the suction feed pump 20 receives the fuel from the suction chamber 60 of the fuel injection pump and delivers it back via the tank 22 when the suction chamber 16 is emptied. There is no risk of overloading the pre-feed pump 18 and the dry running of the suction feed pump 20 because of the fuel injection pump 10 coming to a standstill and the lack of drive for the pre-feed pump 18 and the suction feed pump 20.
  • control valve 12 need not be a separate structural unit, but can form a structural association with the fuel injection pump 10 in such a way that the second connection 34 coincides with the inlet channel 36 and the third connection 58 with the return channel 50, whereby these two plague connections reduce the number of free connections to the minimum of two for connecting the pre-feed pump 18 and the suction feed pump 20, thereby improving operational reliability.
  • the throttle duct 76 it is possible to form the throttle duct 76 by a flat annular groove provided in the same area in the lateral surface of the valve member 68, so that the fuel required for the self-lubrication of the suction feed pump 20 can flow out of the return duct 50 in the delivery position.
  • the operation of the delivery valve 12 can also take place in such a way that in the delivery position the control valve 12 receives operating voltage and the control member 68 is held against the force of the return spring 80, while in the absence of the operating voltage the return spring 80 brings the valve member 68 into the switch-off position.
  • the fuel injection pump 110 is shown with a suction space 116 which is common to all pump cylinders 142 and also takes up the control fuel quantity, parts which correspond to the first exemplary embodiment being used by 100 larger reference numerals, so that this means that to avoid repetition, reference is made to the description of the first exemplary embodiment.
  • the second connection 34, the inlet channel 36, the throttle 44, and the partial suction spaces are omitted 48, the inlet channel 50, the return openings 52 and the third connection 58.
  • the suction space 116 has a central opening 182 at the mounting point of the control valve 112, which allows the fuel exchange through the attached valve housing 170, which is also open in this area.
  • the valve body 170 which is also of a hollow cylindrical design in its inner form, has a longitudinal groove 184 in the region of the valve member 168, which is designed and positioned in such a way that, in the delivery position of the control valve 112, fuel from the pre-feed pump 118 to the suction chamber 116, but not via the longitudinal groove 184 arrives at the fourth connection 160.
  • the fourth connection 160 in turn receives fuel in a bypass flow via the throttle duct 176, which is inserted in the second end face 178 in this second exemplary embodiment.
  • the functional sequence of the second exemplary embodiment differs from that of the first exemplary embodiment in that, in order to reach the conveying position shown in FIG. 2, the force of the return spring 180 must be overpressed by the magnetically excited actuating forces of the control valve 112.
  • the suction chamber 116 of the fuel injection pump 110 is by means of the pre-delivery pump 118 through the Position of the control edge formed by the first end face 172 kept open first connection 132 and the opening 182 supplied with fuel.
  • the control valve 112 is disconnected from the power supply, the control member 168, due to the actuating force of the return spring 180, moves into the other end position, which represents the switch-off position, which is assumed by the first end face 172 approaching a stop 186, thereby firstly causing the first Connection 132 is closed by the control edge of the first end face 172 and, on the other hand, the connection from the fourth connection 160 to the longitudinal groove 184 is opened by the control edge of the second end face 178.
  • the suction feed pump 120 can reach through hydraulically to the suction chamber 116 and thus drain the suction chamber 116 into the tank 122.
  • valve member 168 of the control valve 112 can also be held in the delivery position shown in FIG. 2 by the action of the return spring 180 and can be brought into the switched-off position by the magnetically excited actuating force of the control valve 112.
  • the control device 14; 114 in accordance with FIG. 1 and FIG. 2 ensures that the internal combustion engine is stopped safely and sufficiently quickly by means of simply designed and inexpensive parts. Any engine damage due to overspeed and excess fuel as well as accidents due to impossible "gas removal” are prevented by the use of an uncomplicated control valve 12; 112 and two mechanically driven feed pumps 18; 20 or 118; 120, which can both be combined in a common pump housing and can be provided with a common drive, reliably prevented.

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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)
  • High-Pressure Fuel Injection Pump Control (AREA)

Abstract

The control device of the invention is designed to enable a diesel engine to be brought rapidly to a halt by evacuating the suction chamber (16) of the fuel-injection pump (10) which supplies the engine with fuel. To this end, the control device (14) has two mechanically and hence permanently driven feed pumps (18; 20) which operate in conjuntion with a control valve (12) which is easy and inexpensive to manufacture and which has a valve element (68) which is basically hollow-cylindrical in shape and whose two end faces (72; 78) form control edges. By virtue of its design, the valve (12) is insensitive to dirt and can be built small; it can thus be accommodated in the cover of the fuel-injection pump (10) governer. This device is particularly suitable for diesel engines with high-pressure fuel-injection systems, providing additional relability.

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Steuereinrichtung zum Stillsetzen einer Brennkraftmaschine, insbesondere einer Dieselbrennkraftmaschine nach dem gattungsbildenden Oberbegriff des Hauptanspruchs.The invention is based on a control device for stopping an internal combustion engine, in particular a diesel internal combustion engine, according to the generic preamble of the main claim.

Durch die DE-A-3 304 335 ist eine Steuereinrichtung der gattungsgemäßen Bauart bekannt, bei der zum Stillsetzen der Brennkraftmaschine in einer Lösungsvariante gemäß Figur 2 eine elektrisch angetriebene Förderpumpe mit polumschaltbarem Elektromotor und umkehrbarer Fördereinrichtung eingesetzt wird, wobei im Abstellfall der Brennkraftmaschine der Saugraum der Kraftstoffeinspritzpumpe mit der Saugseite der Förderpumpe und die Druckseite der Förderpumpe mit dem Kraftstofftank verbunden wird.From DE-A-3 304 335 a control device of the generic type is known, in which an electrically driven feed pump with pole-changing electric motor and reversible delivery device is used to shut down the internal combustion engine in a solution variant according to FIG Fuel injection pump is connected to the suction side of the feed pump and the pressure side of the feed pump to the fuel tank.

Dadurch wird dem Saugraum der Kraftstoffeinspritzpumpe im Abstellfall schlagartig Kraftstoff entzogen, so daß die Kraftstoffeinspritzpumpe keinen Kraftstoff mehr fördern kann und die zugehörige Brennkraftmaschine stehenbleibt.As a result, fuel is suddenly withdrawn from the suction space of the fuel injection pump when it is switched off, so that the fuel injection pump can no longer deliver fuel and the associated internal combustion engine stops.

Es hat sich gezeigt, daß bei dieser bekannten Steuereinrichtung die Saugwirkung der im Strömungsteil bipolar ausgelegten, d. h. in beiden Drehrichtungen arbeitende und damit vom prinzipiellen Ansatz her nicht optimal abstimmbaren Förderpumpe nicht immer ausreicht, möglichst schnell und schlagartig einen genügend hohen Unterdruck im Saugraum der Einspritzpumpe zu erzeugen. Dadurch ist ein einwandfreies Abstellen der Brennkraftmaschine nicht gewährleistet, so daß die Gefahr von Motorschäden aufgrund von Überdrehzahl und Kraftstoffübermenge sowie vor Unfällen durch nicht mögliche "Gaswegnahme" nicht hinreichend zuverlässig vermieden ist.It has been shown that in this known control device, the suction effect of the bipolar in the flow part, ie. H. Delivery pump operating in both directions of rotation and therefore not optimally tunable in principle is not always sufficient to generate a sufficiently high vacuum in the suction space of the injection pump as quickly and suddenly as possible. This does not ensure that the internal combustion engine is switched off properly, so that the risk of engine damage due to overspeed and excess fuel and from accidents due to impossible "gas removal" is not sufficiently reliably avoided.

Als weiterer Nachteil dieser Lösung kommt hinzu, daß periphere Saug- und Druckleitungen der mit in zwei Förderrichtungen arbeitenden Förderpumpe hydraulisch entkoppelt werden müssen, was zusätzliche Bauelemente, z. B. zusätzliche Rückschlagventile, erfordert. Dies ist bauraum- und kostenaufwendig und stellt ein ungewolltes Sicherheitsrisiko in dem Sinne dar, daß bei unzureichender Funktion oder gar Ausfall eines dieser zusätzlichen Bauelemente das Gesamtsystem ausfallen kann. Außerdem ist der Gesamtaufwand bei der Verwendung von umpolbaren Elektrokraftstoffpumpen an Dieselmotoren wegen der zusätzlichen Stromversorgung und der erforderlichen Steuerschaltung beträchtlich.Another disadvantage of this solution is that peripheral suction and pressure lines of the feed pump working in two delivery directions must be hydraulically decoupled, which additional components such. B. additional check valves required. This is space-consuming and costly and represents an undesired security risk in the sense that the entire system can fail if one of these additional components malfunctions or even fails. In addition, the total effort when using reversible electric fuel pumps on diesel engines is considerable because of the additional power supply and the necessary control circuit.

Bei einer weiteren Lösungsvariante (Figur 1 der eingangs zitierten DE-OS 33 04 355) ist neben einer nur der Zuförderung zum Saugraum der Kraftstoffeinspritzpumpe dienende Förderpumpe eine zweite, elektrisch angetriebene Förderpumpe angebracht, die nur im Abstellfall der Brennkraftmaschine in Funktion tritt. Ihre Ansteuerung und der Betrieb erfolgt elektrisch über ein elektronisches Steuergerät, das mit einem elektrohydraulischen Einspritzpumpenregler zusammenwirkt. Dieses System ist aufwendig und kostenintensiv und steigert mit dem Grad der Komplexität und der gegenseitigen Abhängigkeit das Versagensrisiko.In a further solution variant (FIG. 1 of DE-OS 33 04 355 cited at the beginning), in addition to a feed pump that only serves to supply the suction space of the fuel injection pump, a second, electrically driven feed pump is fitted, which only functions when the internal combustion engine is switched off. They are controlled and operated electrically by an electronic control unit that interacts with an electro-hydraulic injection pump controller. This system is complex and costly and increases the risk of failure with the degree of complexity and interdependency.

Vorteile der ErfindungAdvantages of the invention

Durch die erfindungsgemäß mit den kennzeichnenden Merkmalen des Hauptanspruchs ausgestaltete Steuereinrichtung ist eine ausreichend schnelle Notabstellung der Brennkraftmaschine, insbesondere Diesel-brennkraftmaschine, gewährleistet. Die nur für die Absaugung des Saugraums der Kraftstoffeinspritzpumpe bestimmte, mechanisch und damit permanent angetriebene Absaugförderpumpe, garantiert ein schnellstmögliches Leersaugen des Saugraums der Kraftstoffeinspritzpumpe im Abstellfall der Brennkraftmaschine. Da auch die Vorförderpumpe, die im Betriebsfall der Brennkraftmaschine den Saugraum der Brennkraftmaschine mit Kraftstoff versorgt, mechanisch angetrieben wird, erübrigt sich ein beide Förderpumpen ansteuerndes Steuergerät und der Antrieb beider Förderpumpen kann problemlos über die schon einspritzpumpenseitig ohnehin vorhandene Nockenwelle vorgenommen werden.A sufficiently rapid emergency shutdown of the internal combustion engine, in particular a diesel internal combustion engine, is ensured by the control device designed according to the invention with the characterizing features of the main claim. The mechanical and thus permanently driven suction feed pump, which is only intended for the extraction of the suction chamber of the fuel injection pump, guarantees that the suction chamber of the fuel injection pump is emptied as quickly as possible when the internal combustion engine is switched off. Since the pre-feed pump, which supplies the suction chamber of the internal combustion engine with fuel when the internal combustion engine is operating, is mechanically driven, there is no need for a control unit which controls both feed pumps and the drive of both feed pumps can be carried out easily via the camshaft, which is already present on the injection pump side.

Des weiteren wird für die jeweilige im Normalbetrieb und im Abstellfall erforderliche Ansteuerung beider Förderpumpen nur ein einfaches 2-Stellungs-Wegeventil benötigt. Somit stellt sich eine Steuereinrichtung dar, die nur wenige Bauelemente benötigt, die einfach, kostengünstig und funktionssicher gestaltet sind.Furthermore, only a simple 2-position directional control valve is required for the control of both feed pumps required in normal operation and in the event of a shutdown. This represents a control device which requires only a few components, which are simple, inexpensive and functionally reliable.

Durch die in den Unteransprüchen aufgeführten Merkmale sind vorteilhafte Weiterbildungen und Verbesserungen der im Hauptanspruch angegebenen Steuereinrichtung erreichbar. So ist die Bauweise des Steuerventils, das gemäß Anspruch 2 ein direkt im Zulauf zum Saugraum der Kraftstoffeinspritzpumpe angebrachtes Ventilgehäuse aufweist und in dem entsprechend den kennzeichnenden Merkmalen des Anspruchs 3 ein Ventilglied vorhanden ist, das in seiner Grundform zylindrisch ausgebildet ist, einfach, schmutzunempfindlich und kompakt und somit in vorteilhafter Weise auch in den Reglerdeckel der Kraftstoffeinspritzpumpe integrierbar.Advantageous further developments and improvements of the control device specified in the main claim can be achieved by the features listed in the subclaims. Thus, the construction of the control valve, which according to claim 2 has a valve housing attached directly to the suction chamber of the fuel injection pump and in which, in accordance with the characterizing features of claim 3, there is a valve member which is cylindrical in its basic form, is simple, insensitive to dirt and compact and thus can also be advantageously integrated into the regulator cover of the fuel injection pump.

Außerdem wird durch die kennzeichnenden Merkmale der Ansprüche 4 und 5 bei den Ausführungen der Förderpumpen weitere Vereinfachungen erreicht, insbesondere bei der Zusammenlegung beider Förderpumpen in ein gemeinsames Gehäuse und deren gemeinsamer Antrieb mittels der vorhandenen Nockenwelle der Kraftstoffeinspritzpumpe.In addition, the characterizing features of claims 4 and 5 further simplify the designs of the feed pumps, in particular when the two feed pumps are combined in a common housing and their common drive by means of the existing camshaft of the fuel injection pump.

Gemäß den Merkmalen des Anspruchs 6 wird eine kostengünstige Ansteuerung des Steuerventils, z. B. ein sogenannter Schlüsselstopp verwirklicht und bei einer Unterbrechung der Stromversorgung die zugehörige Brennkraftmaschine automatisch abgestellt.According to the features of claim 6, an inexpensive control of the control valve, for. B. realizes a so-called key stop and automatically switches off the associated internal combustion engine if the power supply is interrupted.

Gemäß den Merkmalen des Anspruchs 7 ist im Normalbetrieb keine Stromversorgung des Steuerventils erforderlich, so daß, wie auch schon durch den Einsatz der mechanisch angetriebenen Förderpumpen, auch beim Steuerventil kein Stromverbrauch erfolgt.According to the features of claim 7, no power supply to the control valve is required in normal operation, so that, as also by the use of the mechanically driven feed pumps, there is also no power consumption in the control valve.

Zeichnungdrawing

Zwei Ausführungsbeispiele sind in der Zeichnung dargestellt und werden nachfolgend näher erläutert. Es zeigen Figur 1 einen partiellen Querschnitt durch das erste Ausführungsbeispiel einer erfindungsgemäß ausgestalteten Kraftstoffeinspritzpumpe mit quergespültem Saugraum und Figur 2 einen partiellen Querschnitt durch das zweite Ausführungsbeispiel einer erfindungsgemäß ausgestalteten Kraftstoffeinspritzpumpe mit normalgespültem Saugraum.Two exemplary embodiments are shown in the drawing and are explained in more detail below. FIG. 1 shows a partial cross section through the first exemplary embodiment of a fuel injection pump designed according to the invention with cross-flushed suction chamber, and FIG. 2 shows a partial cross section through the second exemplary embodiment of a fuel injection pump designed according to the invention with normally flushed suction chamber.

Beschreibung der AusführungsbeispieleDescription of the embodiments

Die in Figur 1 und 2 schematisch dargestellten beiden Ausführungsbeispiele einer als Mehrzylinder-Reiheneinspritzpumpe ausgebildeten Kraftstoffeinspritzpumpe 10 für Dieselbrennkraftmaschinen ist mit einem angebauten Steuerventil 12 als Teil einer Steuereinrichtung 14 gezeigt. Die grundsätzliche Anordnung der Elemente einer solchen Kraftstoffeinspritzpumpe 10 ist an sich bekannt, wobei die Ausgestaltung der Kraftstoffeinspritzpumpe 10 mit einem, wie in Figur 1 bei dem im ersten Ausführungsbeispiel vorliegenden quergespülten Saugraum 16 beispielsweise in der DE-A-3 304 335 detailliert beschrieben ist. Die Steuereinrichtung 14, die im wesentlichen aus dem Steuerventil 12, einer Vorförderpumpe 18 und einer Absaugförderpumpe 20 besteht, liefert während einer Förderstellung der Kraftstoffeinspritzpumpe 10 Kraftstoff zu. Hingegen wird während einer Abschaltstellung der Steuereinrichtung 14 der Kraftstoffeinspritzpumpe 10 Kraftstoff entzogen. Die mechanisch angetriebene Vorförderpumpe 18 ist eine an sich bekannte, mit einem Saug- und einem Druckventil ausgestattete Kolbenförderpumpe, die in der Praxis in Nockenwellenhöhe an der Kraftstoffeinspritzpumpe 10 angebaut ist. Die Vorförderpumpe 18 ist auf ihrer Saugseite an eine mit einem Tank 22 verbundene Saugleitung 24 angeschlossen. Stromabwärts der Vorförderpumpe 18 schließt sich an deren Druckseite eine einen Kraftstoffilter 26 und eine einen Kraftstoffspeicher 28 aufnehmende Versorgungsleitung 30 an, die in einen ersten Anschluff 32 des Steuerventils 12 mündet.The two exemplary embodiments, shown schematically in FIGS. 1 and 2, of a fuel injection pump 10 designed as a multi-cylinder in-line injection pump for diesel internal combustion engines are shown with an attached control valve 12 as part of a control device 14. The basic arrangement of the elements of such Fuel injection pump 10 is known per se, the configuration of the fuel injection pump 10 with a suction chamber 16 which is flushed in the first exemplary embodiment, as shown in FIG. 1, is described in detail, for example, in DE-A-3 304 335. The control device 14, which essentially consists of the control valve 12, a prefeed pump 18 and a suction feed pump 20, supplies fuel to the fuel injection pump 10 during a delivery position. In contrast, fuel is withdrawn from the fuel injection pump 10 during a switch-off position of the control device 14. The mechanically driven pre-feed pump 18 is a piston feed pump known per se, equipped with a suction and a pressure valve, which in practice is attached to the fuel injection pump 10 at camshaft height. The prefeed pump 18 is connected on its suction side to a suction line 24 connected to a tank 22. Downstream of the pre-feed pump 18 there is a supply line 30, which receives a fuel filter 26 and a fuel accumulator 28, and which opens into a first port 32 of the control valve 12.

Bei dem ersten Ausführungsbeispiel nach Figur 1 korrespondiert mit dem ersten Anschluß 32 ein zweiter Anschluß 34, an welchen ein Zulaufkanal 36 der Kraftstoffeinspritzpumpe 10 angeschlossen ist. Von diesem zweigen, entsprechend der Anzahl der in einem Gehäuse 38 der Kraftstoffeinspritzpumpe 10 in Reihe angeordnete Aufnahmebohrungen 40 für die Pumpenzylinder 42 mit je einer Drossel 44 versehene Zulauföffnungen 46 ab, die in als Ringnuten ausgeführte Teilsaugräume 48 münden, die auf der anderen Seite wiederum je eine mit einem Rücklaufkanal 50 verbundene Rücklauföffnungen 52 aufweisen.In the first exemplary embodiment according to FIG. 1, the first connection 32 corresponds to a second connection 34, to which an inlet channel 36 of the fuel injection pump 10 is connected. From this branch, corresponding to the number of receiving bores 40 arranged in series in a housing 38 of the fuel injection pump 10 for the pump cylinders 42, each provided with a throttle 44, inlet openings 46, which open into partial suction spaces 48 designed as annular grooves, which in turn each on the other side have a return opening 52 connected to a return channel 50.

Jede Rücklauföffnung 52 hat einen in bezug auf den Querschnitt des Rücklaufkanals 50 wesentlich geringeren Durchströmquerschnitt und der Durchströmquerschnitt jeder Drossel 44 in den Zulauföffnungen 46 ist geringer als der Durchströmquerschnitt der zugehörigen Rücklauföffnung 52. An den Rücklaufkanal 50 schließt sich eine ein Druckhalteventil 54 aufweisende und in den Tank 22 mündende Überströmleitung 56 an. Das der Überströmleitung 56 abgewandte Ende des Rücklaufkanals 50 ist mit einem dritten Anschluß 58 des Steuerventils 12 verbunden. Mit dem dritten Anschluß 58 korrespondiert ein als Förderanschluß dienender vierter Anschluß 60, dem über eine Absaugleitung 62 die Absaugförderpumpe 20 angeschlossen ist, die stromabwärts über eine Tankrücklaufleitung 66 mit dem Tank 22 in Verbindung steht. Das Steuerventil 12 ist als Magnetventil ausgeführt und weist ein Ventilglied 68 auf, das innerhalb eines in seiner inneren Rundform hohlzylindrisch ausgebildeten Ventilgehäuse 70 dichtend in axialer Richtung gleitverschieblich in eine Förderstellung und in einen Abschaltstellung gebracht werden kann. Das Ventilglied 68 bildet einerseits eine, dem ersten Anschluß 32 und dem zweiten Anschluß 34 zugewandte, nicht vollständig geschlossene Stirnfläche 72 und andererseits eine, der ersten Stirnfläche 72 gegenüberliegende, mit dem dritten Anschluß 58 und dem vierten Anschluß 60 zusammenarbeitende zweite Stirnfläche 78, die vollständig geschlossen ist und die eine hohlzylinderförmige Wand 74 trägt, die im Bereich des vierten Anschlusses 60 einen, von einer engen Bohrung gebildeten Drosselkanal 76 aufweist. Eine an der ersten Stirnfläche 72 angreifende, sich im Ventilgehäuse 70 abstützende Rückstellfeder 80 hält, entsprechend der Darstellung nach Figur 1, das Ventilglied 68 in der Förderstellung.Each return opening 52 has a flow cross-section which is substantially smaller in relation to the cross-section of the return duct 50 and the flow cross-section of each throttle 44 in the inlet openings 46 is smaller than the flow cross-section of the associated return opening 52. An overflow line 56 having a pressure-maintaining valve 54 and opening into the tank 22 connects to the return channel 50. The end of the return channel 50 facing away from the overflow line 56 is connected to a third connection 58 of the control valve 12. The third connection 58 corresponds to a fourth connection 60 serving as a delivery connection, to which the suction feed pump 20 is connected via a suction line 62 and which is connected downstream to the tank 22 via a tank return line 66. The control valve 12 is designed as a solenoid valve and has a valve member 68, which can be brought into a conveying position and a switch-off position in a sealing manner in the inner cylindrical shape of a hollow hollow cylindrical valve housing 70 in the axial direction. The valve member 68 forms, on the one hand, an incompletely closed end face 72 facing the first connection 32 and the second connection 34 and, on the other hand, a second end face 78 which is opposite the first end surface 72 and cooperates with the third connection 58 and the fourth connection 60 and which is completely is closed and which carries a hollow cylindrical wall 74 which in the area of the fourth connection 60 has a throttle duct 76 formed by a narrow bore. A return spring 80, which acts on the first end face 72 and is supported in the valve housing 70, holds the valve member 68 in the delivery position, as shown in FIG. 1.

Die beschriebene Anordnungsdarstellung ergibt den folgenden Funktions- und Wirkungsalauf. Ausgehend von der Förderstellung des Steuerventils 12 ist dessen Steuerglied 68 durch die Kraft der Rückstellfeder 80 in die eine Endlage gebracht, in der zwischen dem ersten Anschluß 32 und dem zweiten Anschluß 34 eine hydraulische Verbindung besteht und der dritte Anschluß 58 von dem vierten Anschluß 60 durch das dazwischenliegende Ventilglied 68 hydraulisch getrennt ist. In dieser Betriebsstellung gelangt der von der Vorförderpumpe 18 geförderte Kraftstoff entsprechend der Lage der Steuerkante der ersten Stirnfläche 72 über den ersten Anschluß 32 und den zweiten Anschluß 34 zum Zulaufkanal 36, von dem aus der Kraftstoff den Teilsaugräumen 48 der Pumpenzylinder 42 über die Drosseln 44 und die Zulauföffnungen 46 zufließt. Überschüssiger Kraftstoff kann über die Rücklauföffnungen 52, dem Rücklaufkanal 50 und dem Druckhalteventil 54 zum Tank 22 hin abfließen. Zum anderen gelangt der von der Vorförderpumpe 18 geförderte Kraftstoff über den ersten Anschluß 32, die durchbrochene erste Stirnfläche 72 zu dem Drosselkanal 76 und durch ihn zum vierten Anschluß 60 und von hier weiter über die Absaugleitung 62, die Absaugförderpumpe 20 und die Tankrücklaufleitung 66 zum Tank 22 zurück. Dieser Kraftstoffstrom ist durch den Strömungsquerschnitt des Drosselkanals 76 so eingeschränkt, daß einerseits ein Mindestdurchlauf zur Selbstschmierung der mechanischen, permanent angetriebenen Absaugförderpumpe 20 erfolgt, andererseits die im Hauptstrom erfolgende Füllung der Pumpenzylinder 42 noch nicht funktionsbeeinträchtigend geschwächt wird.The arrangement diagram described results in the following functional and functional run. Starting from the delivery position of the control valve 12, the control member 68 is brought into one end position by the force of the return spring 80, in which there is a hydraulic connection between the first connection 32 and the second connection 34 and the third connection 58 from the fourth connection 60 the intermediate valve member 68 is hydraulically separated. In this operating position it comes from the pre-feed pump 18 delivered fuel corresponding to the position of the control edge of the first end face 72 via the first connection 32 and the second connection 34 to the inlet channel 36, from which the fuel flows to the partial suction chambers 48 of the pump cylinders 42 via the throttles 44 and the inlet openings 46. Excess fuel can flow out to the tank 22 via the return openings 52, the return channel 50 and the pressure holding valve 54. On the other hand, the fuel delivered by the pre-feed pump 18 passes via the first connection 32, the perforated first end face 72 to the throttle duct 76 and through it to the fourth connection 60 and from here further via the suction line 62, the suction feed pump 20 and the tank return line 66 to the tank 22 back. This fuel flow is restricted by the flow cross section of the throttle channel 76 so that, on the one hand, there is a minimum flow for self-lubrication of the mechanical, permanently driven suction feed pump 20, and on the other hand the filling of the pump cylinders 42 in the main flow is not yet weakened in a functionally impairing manner.

Zum Stillsetzen der Brennstoffkraftmaschine bei einer Notabschaltung wird der Brennkraftmaschine der für die Einspritzung benötigte Kraftstoff entzogen, indem dem Saugraum 16 der zugehörigen Kraftstoffeinspritzpumpe 10 zum einen kein Kraftstoff mehr zuliefert, zum anderen der im Saugraum 16 der Kraftstoffeinspritzpumpe 10 befindliche Kraftstoff abgesaugt wird. Dazu wird durch magnetisch angeregte Stellkräfte des Steuerventils 12 das Ventilglied 68 entgegen der Kraft der Rückstellfeder 80 in die andere Endlage gebracht, in der durch die Steuerkante der ersten Stirnfläche 72 die Verbindung zwischen dem ersten Anschluß 32 und dem zweiten Anschluß 34 gesperrt und durch die Lage der Steuerkante der zweiten Stirnfläche 78 der dritte Anschluß 58 mit dem vierten Anschluß 60 hydraulisch verbunden wird.To stop the fuel engine in the event of an emergency shutdown, the internal combustion engine is deprived of the fuel required for the injection, on the one hand no longer supplying fuel to the suction space 16 of the associated fuel injection pump 10, and on the other hand the fuel located in the suction space 16 of the fuel injection pump 10 is extracted. For this purpose, by means of magnetically excited actuating forces of the control valve 12, the valve member 68 is brought into the other end position against the force of the return spring 80, in which the connection between the first connection 32 and the second connection 34 is blocked by the control edge of the first end face 72 and by the position the control edge of the second end face 78, the third connection 58 is hydraulically connected to the fourth connection 60.

Damit gelangt der von der Vorförderpumpe 18 gelieferte Kraftstoff weder zu den Teilsaugräumen 48 noch über den Drosselkanal 76 zum vierten Anschluß 60, da der Drosselkanal 76 durch die axiale Verlagerung des Steuerglieds 68 in die andere Endlage aus dem Einzugsbereich des vierten Anschlusses 60 verschoben wurde. Gleichwohl erhält die Absaugförderpumpe 20 den Kraftstoff aus dem Saugraum 60 der Kraftstoffeinspritzpumpe und fördert diesen bei Entleerung des Saugraums 16 über den Tank 22 zurück. Eine Gefahr der Überlastung der Vorförderpumpe 18 sowie des Trockenlaufes der Absaugförderpumpe 20 besteht wegen der zum Stillstand kommenden Kraftstoffeinspritzpumpe 10 und des entfallenden Antriebs für die Vorförderpumpe 18 und die Absaugförderpumpe 20 nicht.The fuel supplied by the pre-feed pump 18 thus does not reach the partial suction chambers 48 or the throttle duct 76 fourth connection 60, since the throttle channel 76 has been displaced by the axial displacement of the control member 68 into the other end position from the pull-in area of the fourth connection 60. Nevertheless, the suction feed pump 20 receives the fuel from the suction chamber 60 of the fuel injection pump and delivers it back via the tank 22 when the suction chamber 16 is emptied. There is no risk of overloading the pre-feed pump 18 and the dry running of the suction feed pump 20 because of the fuel injection pump 10 coming to a standstill and the lack of drive for the pre-feed pump 18 and the suction feed pump 20.

Wie in Figur 1 gezeigt, braucht das Steuerventil 12 keine separate Baueinheit zu sein, sondern kann mit der Kraftstoffeinspritzpumpe 10 einen baulichen Verband bilden in der Weise, daß der zweite Anschluß 34 mit dem Zulaufkanal 36 und der dritte Anschluß 58 mit dem Rücklaufkanal 50 zusammenfallen, wobei durch diese beiden Pestanschlüsse die Zahl der freien Anschlüsse auf das Mindestmaß von zwei zum Anschluß der Vorförderpumpe 18 bzw. der Absaugförderpumpe 20 vermindert und damit eine verbesserte Betriebssicherheit erreicht wird. Des weiteren ist es möglich, den Drosselkanal 76 durch eine im gleichen Bereich in der Mantelfläche des Ventilgliedes 68 angebrachte flache Ringnut auszubilden, so daß in der Förderstellung der für die Selbstschmierung der Absaugförderpumpe 20 benötigte Kraftstoff aus dem Rücklaufkanal 50 zuströmen kann.As shown in FIG. 1, the control valve 12 need not be a separate structural unit, but can form a structural association with the fuel injection pump 10 in such a way that the second connection 34 coincides with the inlet channel 36 and the third connection 58 with the return channel 50, whereby these two plague connections reduce the number of free connections to the minimum of two for connecting the pre-feed pump 18 and the suction feed pump 20, thereby improving operational reliability. Furthermore, it is possible to form the throttle duct 76 by a flat annular groove provided in the same area in the lateral surface of the valve member 68, so that the fuel required for the self-lubrication of the suction feed pump 20 can flow out of the return duct 50 in the delivery position.

In abgewandelter Weise kann der Betrieb des Förderventils 12 auch so erfolgen, daß in der Förderstellung das Steuerventil 12 Betriebsspannung erhält und das Steuerglied 68 entgegen der Kraft der Rückstellfeder 80 gehalten wird, während bei fehlender Betriebsspannung die Rückstellfeder 80 das Ventilglied 68 in die Abschaltstellung bringt.In a modified manner, the operation of the delivery valve 12 can also take place in such a way that in the delivery position the control valve 12 receives operating voltage and the control member 68 is held against the force of the return spring 80, while in the absence of the operating voltage the return spring 80 brings the valve member 68 into the switch-off position.

In einem zweiten Ausführungsbeispiel der Steuereinrichtung 114 nach Figur 2 ist die Kraftstoffeinspritzpumpe 110 mit einem für alle Pumpenzylinder 142 gemeinsamen, auch die Absteuerkraftstoffmenge aufnehmenden Saugraum 116 gezeigt, wobei für Teile, die dem ersten Ausführungsbeispiel entsprechen, um 100 größere Bezugszeichen verwendet sind, so daß dadurch zur Vermeidung von Wiederholungen auf die Beschreibung des ersten Ausführungsbeispiels Bezug genommen ist.In a second exemplary embodiment of the control device 114 according to FIG. 2, the fuel injection pump 110 is shown with a suction space 116 which is common to all pump cylinders 142 and also takes up the control fuel quantity, parts which correspond to the first exemplary embodiment being used by 100 larger reference numerals, so that this means that to avoid repetition, reference is made to the description of the first exemplary embodiment.

Beim zweiten Ausführungsbeispiel, in dem die Bewegungsrichtung des Ventilglieds 168 längs zu den in Reihe angeordneten Pumpenzylindern 142 verläuft und damit gegenüber der Bewegungsrichtung des Ventilglieds 168 um 90 Grad gedreht ist, entfallen der zweite Anschluß 34, der Zulaufkanal 36, die Drossel 44, die Teilsaugräume 48, der Zulaufkanal 50, die Rücklauföffnungen 52 und der dritte Anschluß 58. Statt dessen weist der Saugraum 116 an der Anbaustelle des Steuerventils 112 einen zentralen Durchbruch 182 auf, der den Kraftstoffaustausch durch das angebaute, in diesem Bereich ebenfalls offen gestaltete Ventilgehäuse 170 gestattet. Das in seiner inneren Grundform gleichfalls hohlzylindrisch ausgebildete Ventilgehäuse 170 weist im Bereich des Ventilglieds 168 eine Längsnut 184 auf, die so gestaltet und positioniert ist, daß in der Förderstellung des Steuerventils 112 zwar Kraftstoff von der Vorförderpumpe 118 zum Saugraum 116, nicht jedoch über die Längsnut 184 zum vierten Anschluß 160 gelangt. Der vierte Anschluß 160 erhält wiederum in einem Bypaßstrom Kraftstoff über den Drosselkanal 176, der bei diesem zweiten Ausführungsbeispiel in der zweiten Stirnfläche 178 eingefügt ist.In the second exemplary embodiment, in which the direction of movement of the valve member 168 extends longitudinally to the pump cylinders 142 arranged in series and is thus rotated by 90 degrees with respect to the direction of movement of the valve member 168, the second connection 34, the inlet channel 36, the throttle 44, and the partial suction spaces are omitted 48, the inlet channel 50, the return openings 52 and the third connection 58. Instead, the suction space 116 has a central opening 182 at the mounting point of the control valve 112, which allows the fuel exchange through the attached valve housing 170, which is also open in this area. The valve body 170, which is also of a hollow cylindrical design in its inner form, has a longitudinal groove 184 in the region of the valve member 168, which is designed and positioned in such a way that, in the delivery position of the control valve 112, fuel from the pre-feed pump 118 to the suction chamber 116, but not via the longitudinal groove 184 arrives at the fourth connection 160. The fourth connection 160 in turn receives fuel in a bypass flow via the throttle duct 176, which is inserted in the second end face 178 in this second exemplary embodiment.

Im Gegensatz zum Wirkungsablauf unterscheidet sich der Funktionsablauf des zweiten Ausführungsbeispiels von jenem des ersten Ausführungsbeispiels dadurch, daß zum Erreichen der in Figur 2 gezeigten Förderstellung die Kraft der Rückstellfeder 180 durch die magnetisch angeregten Stellkräfte des Steuerventils 112 überdrückt werden müssen. In dieser Förderstellung wird der Saugraum 116 der Kraftstoffeinspritzpumpe 110 mittels der Vorförderpumpe 118 über den durch die Lage der von der ersten Stirnfläche 172 gebildeten Steuerkante offen gehaltenen ersten Anschluß 132 und den Durchbruch 182 mit Kraftstoff versorgt.In contrast to the sequence of effects, the functional sequence of the second exemplary embodiment differs from that of the first exemplary embodiment in that, in order to reach the conveying position shown in FIG. 2, the force of the return spring 180 must be overpressed by the magnetically excited actuating forces of the control valve 112. In this delivery position, the suction chamber 116 of the fuel injection pump 110 is by means of the pre-delivery pump 118 through the Position of the control edge formed by the first end face 172 kept open first connection 132 and the opening 182 supplied with fuel.

Zum Stillsetzen der Brennkraftmaschine wird das Steuerventil 112 stromlos geschaltet, das Steuerglied 168 gerät durch die Stellkraft der Rückstellfeder 180 in die, die Abschaltstellung repräsentierende andere Endlage, die durch das Anlaufen der ersten Stirnfläche 172 an einen Anschlag 186 eingenommen wird, wodurch zum einen der erste Anschluß 132 durch die Steuerkante der ersten Stirnfläche 172 verschlossen und zum anderen die Verbindung vom vierten Anschluß 160 zur Längsnut 184 durch die Steuerkante der zweiten Stirnfläche 178 aufgesteuert wird. Da mittels des Anschlages 186 auch in der Abschaltstellung des Steuerventils 112 die hydraulische Verbindung zwischen der Längsnut 184 und dem Saugraum 116 nicht verschlossen wird, kann die Absaugförderpumpe 120 hydraulisch zum Saugraum 116 durchgreifen und somit eine Entleerung des Saugraumes 116 in den Tank 122 vornehmen.To stop the internal combustion engine, the control valve 112 is disconnected from the power supply, the control member 168, due to the actuating force of the return spring 180, moves into the other end position, which represents the switch-off position, which is assumed by the first end face 172 approaching a stop 186, thereby firstly causing the first Connection 132 is closed by the control edge of the first end face 172 and, on the other hand, the connection from the fourth connection 160 to the longitudinal groove 184 is opened by the control edge of the second end face 178. Since the hydraulic connection between the longitudinal groove 184 and the suction chamber 116 is not closed by means of the stop 186 even when the control valve 112 is switched off, the suction feed pump 120 can reach through hydraulically to the suction chamber 116 and thus drain the suction chamber 116 into the tank 122.

In Abwandlung des zweiten Ausführungsbeispiels kann das Ventilglied 168 des Steuerventils 112 auch in der in Figur 2 gezeigten Förderstellung durch die Wirkung der Rückstellfeder 180 gehalten sein und in der Abschaltstellung durch die magnetish angeregte Stellkraft des Steuerventils 112 gebracht werden.In a modification of the second exemplary embodiment, the valve member 168 of the control valve 112 can also be held in the delivery position shown in FIG. 2 by the action of the return spring 180 and can be brought into the switched-off position by the magnetically excited actuating force of the control valve 112.

Die beschriebene Steuereinrichtung 14; 114 gemaß Figur 1 und Figur 2 gewährleistet ein sicheres und ausreichend schnelles Stillsetzen der Brennkraftmaschine mittels einfach gestalteten und kostengünstig herzustellenden Teilen. Eventuelle Motorschäden aufgrund von Überdrehzahl und Kraftstoffübermenge sowie Unfälle durch nicht mögliche "Gaswegnahme" werden durch die Verwendung eines unkompliziert ausgebildeten Steuerventils 12; 112 und zweier mechanisch angetriebener Förderpumpen 18; 20 bzw. 118; 120, die sowohl in einem gemeinsamen Pumpengehäuse zusammengefaßt als auch mit einem gemeinsamen Antrieb versehen sein können, sicher verhindert.The control device 14; 114 in accordance with FIG. 1 and FIG. 2 ensures that the internal combustion engine is stopped safely and sufficiently quickly by means of simply designed and inexpensive parts. Any engine damage due to overspeed and excess fuel as well as accidents due to impossible "gas removal" are prevented by the use of an uncomplicated control valve 12; 112 and two mechanically driven feed pumps 18; 20 or 118; 120, which can both be combined in a common pump housing and can be provided with a common drive, reliably prevented.

Claims (7)

  1. Control device for stopping an internal-combustion engine, especially a diesel internal-combustion engine, with an electromagnetic control valve (12; 112) which precedes a suction space (16; 116) of a fuel-injection pump (10; 110) and which is designed as a two-position directional valve with a feed position and a disconnected position, is inserted with its valve housing (70; 170) into a supply line (30; 130) leading to the suction space (16; 116) and, in the feed position, connects the delivery side of a mechanically driven feed forepump (18; 118), conveying from a tank (22; 122), to the suction space (16; 116) of the fuel-injection pump (10; 110), and with an additional suction feed pump (20; 120) which, when the control valve (12; 112) is in the disconnected position and shuts off the fuel feed from the feed forepump (18; 118) to the suction space (16; 116), sucks fuel from the suction space (16; 116) and conveys it to the tank (22; 122), characterized in that the additional suction feed pump (20; 120) is a mechanically driven fuel-feed pump, and in that the control valve (12; 112), in the feed position, in addition to making the connection from the tank (22; 122) to the suction space (16; 116), also keeps open a line connection via a throttle channel (76; 176) from the suction space (16; 116) to the suction side of the suction feed pump (20; 120) and, in the disconnected position, not only shuts off the inflow from the delivery side of the feed forepump (18; 118) to the suction space (16; 116) of the fuel-injection pump (10; 110), but at the same time also connects the suction side of the suction feed pump (20; 120) to the suction space (16; 116) of the fuel-injection pump (10; 110).
  2. Control device (14; 114) according to Claim 1, characterized in that the control valve (12; 112) is designed as a 4/2-way directional valve, the valve housing (70; 170) of which is mounted directly at the inflow to the suction space (16; 116) of the fuel-injection pump (10; 110).
  3. Control device (14; 114) according to Claim 1 or 2, characterized in that the control valve (12; 112) has a valve member (68) which is of cylindrical basic form and which forms control edges with its end faces (72; 78).
  4. Control device (14; 114) according to one of the preceding claims, characterized in that the feed forepump (18; 118) and the suction feed pump (20; 120) are two piston feed pumps of the same design which are driven mechanically by the camshaft of the fuel-injection pump and which are driven permanently when the internal-combustion engine is running.
  5. Control device (14; 114) according to one of Claims 1 to 3, characterized in that the feed forepump (18; 118) and the suction feed pump (20; 120) are designed as a double feed pump with a common pump housing or a common drive.
  6. Control device (114) according to one of the preceding claims, characterized in that the control member (168) of the control valve (112), in its feed position, is activated by a current supply via a starter switch required for operating a diesel internal-combustion engine and is displaced counter to the force of a restoring spring (180), thereby allowing the feed mode, and, with the starter switch switched off, returns automatically into the disconnected position allowing the suction mode.
  7. Control device (14) according to one of Claims 1 to 5, characterized in that the valve member (68) of the control valve (12), in its feed position, is maintained in its initial position by the force of a restoring spring (80) and consequently allows the feed mode, and in that, to stop the internal-combustion engine in an emergency, the control valve (12) is activated by a current supply and its valve member (68) is thereby brought into the disconnected position counter to the force of the restoring spring (80).
EP90902615A 1989-04-08 1990-02-09 Control device for stopping an internal combustion engine Expired - Lifetime EP0419591B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3911559A DE3911559A1 (en) 1989-04-08 1989-04-08 CONTROL DEVICE FOR STOPPING AN INTERNAL COMBUSTION ENGINE
DE3911559 1989-04-08

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EP0419591A1 EP0419591A1 (en) 1991-04-03
EP0419591B1 true EP0419591B1 (en) 1992-12-02

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EP (1) EP0419591B1 (en)
JP (1) JPH03505360A (en)
KR (1) KR920700345A (en)
DE (2) DE3911559A1 (en)
WO (1) WO1990012207A1 (en)

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EP0419591A1 (en) 1991-04-03
JPH03505360A (en) 1991-11-21
DE59000541D1 (en) 1993-01-14
DE3911559A1 (en) 1990-10-11
KR920700345A (en) 1992-02-19
US5076227A (en) 1991-12-31
WO1990012207A1 (en) 1990-10-18

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