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EP0303624B1 - Fuel injection device for internal combustion engines - Google Patents

Fuel injection device for internal combustion engines Download PDF

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Publication number
EP0303624B1
EP0303624B1 EP87904028A EP87904028A EP0303624B1 EP 0303624 B1 EP0303624 B1 EP 0303624B1 EP 87904028 A EP87904028 A EP 87904028A EP 87904028 A EP87904028 A EP 87904028A EP 0303624 B1 EP0303624 B1 EP 0303624B1
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EP
European Patent Office
Prior art keywords
valve
spring
fuel
chamber
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
EP87904028A
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German (de)
French (fr)
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EP0303624A1 (en
Inventor
Manfred KRÄMER
Erhard Sitter
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP0303624A1 publication Critical patent/EP0303624A1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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 fuel injection device for internal combustion engines, in particular for diesel engines, of the type specified in the preamble of claim 1.
  • the shutdown device serves to terminate the fuel injection as suddenly as possible in the event of faults or errors.
  • the shutdown device has a shut-off valve designed as a poppet valve and a suction pump, which are combined to form a structural unit.
  • the suction pump consists of a piston displaceably guided in a storage space and a compression spring acting on the piston.
  • the piston is normally held in an extended position by means of a mechanical locking device with the compression spring tensioned, in which the storage volume of the storage space is almost zero.
  • the poppet valve is held in the open position by the piston via a valve tappet against the force of a valve closing spring.
  • the fuel delivered by the feed pump enters the space delimited by the piston, in which the piston compression spring is arranged, and flows from here into the suction space.
  • the locking device is released.
  • the piston is moved by the piston compression spring and increasingly frees up the storage space. This creates a negative pressure in the line between the shutdown device and the suction chamber, which prevents fuel from getting further into the suction chamber of the injection pump.
  • the poppet valve is also released by the piston sliding back in the storage space, which passes into its closed position under the action of its valve closing spring.
  • the feed pump is shut off from the suction chamber and feeds back into the fuel tank via an overflow valve.
  • the fuel injection device according to the invention with the characterizing features of claim 1 has the advantage of creating a quick shutdown device with commercially available components, such as spring accumulators, simple hydraulic valves and solenoid valves, which is structurally simple and inexpensive to manufacture.
  • the suction chamber pressure is reduced to a defined pressure of e.g. 1 bar overpressure set.
  • the delivery pressure exceeding the suction chamber pressure, here e.g. 2 bar overpressure tensions the spring accumulator so that its spring chamber has the smallest possible volume.
  • the bypass is opened, as a result of which the excess pressure generated by the delivery pressure in the storage chamber of the spring accumulator breaks down.
  • the spring accumulator relaxes, and the increasing spring chamber volume causes the pressure in the suction chamber to be reduced to less than 0.2 bar absolute, as a result of which the delivery of fuel to the injection nozzles is suddenly interrupted.
  • the internal combustion engine no longer receives fuel and switches off immediately.
  • This configuration of the electromagnetic switching valve means that the greatest valve actuation force, here the closing force of the valve, is to be applied when the magnet armature is tightened. For this, lower forces are required than if the greatest valve force had to be applied against the force of a closing spring when the magnet armature was extended.
  • the electromagnet of the switching valve in particular its winding space, can be dimensioned smaller, and the switching valve can thus be kept small in volume.
  • the switching valve opens in the event of an unwanted power cut, thereby stopping fuel injection.
  • An advantageous embodiment of the invention also results from claim 10. This measure saves an additional fuel line from the switching valve to the fuel tank. Their function is taken over by the return line, which is already present. Due to the connection of the spring chamber of the spring accumulator to the outflow-side region of the suction chamber, the required pressure reduction in the suction chamber takes place quickly enough even in those fuel injection pumps in which flow-limiting or flow-guiding means are provided in the inflow-side region of the suction chamber and can delay the shutdown.
  • the fuel injection device for a diesel engine which is known per se and is shown in FIG. 1 as an example of an internal combustion engine, has a fuel injection pump 10 which is only indicated schematically.
  • the fuel injection pump 10 sucks fuel from a suction chamber 11 of the fuel injection pump 10 with a pump element (not shown), compresses it to injection pressure and distributes the amount of fuel under injection pressure to injection nozzles that are assigned to the individual cylinders of the diesel engine.
  • FIG. 1 shows only a single injection nozzle 43 for an engine cylinder.
  • the suction chamber 11 is filled with fuel by a fuel delivery pump 12 from a fuel tank 13.
  • the feed pump 12 is connected to the fuel tank 13 via a suction port 14 with a fuel filter 44 and via a feed line 15 to a further fuel filter 45 at the inlet of the suction chamber 11.
  • the outlet of the suction chamber 11 is connected to the fuel tank 13 again via a return line 16.
  • An inlet valve 17 is arranged in the delivery line 15 and an overflow valve 18 is arranged in the return line 16, each with a defined opening pressure of 1 bar overpressure here.
  • the flow direction of the feed valve 17 is directed from the feed pump 12 to the suction chamber 11, while the flow direction of the overflow valve 18 is directed from the suction chamber 11 to the fuel tank 13.
  • the two valves 17, 18 designed here as simple non-return valves ensure that fuel delivery from the fuel tank 13 to the suction chamber 11 only begins at a defined delivery pressure of greater than 2 bar and that the excess pressure in the suction chamber 11 is kept constant at 1 bar.
  • the two valves 17, 18 are part of a shutdown device 19 for fuel injection in the event of an emergency or malfunction.
  • the shutdown device 19 also has a spring accumulator 20 which is arranged between the feed pump 12 and the suction chamber 11, that is to say parallel to the inlet valve 17 and is divided in a known manner into a storage chamber 22 and a spring chamber 23 by a membrane 21.
  • a compression spring 24 which is supported on the one hand on the membrane 21 and on the other hand on the housing side, and a stop 25 for limiting the displacement movement of the membrane 21.
  • the spring chamber 23 is connected to the inlet of the suction chamber 11 or to the outlet valve 17 and the storage chamber 22 is connected to the outlet of the feed pump 12 or the inlet of the inlet valve 17.
  • the compression spring 24 is set so that when the spring chamber 23 is depressurized, a pressure in the storage chamber 22 of 0.8 bar overpressure is sufficient to compress the compression spring 24 to such an extent that the membrane 21 bears against the stop 25. In this position of the membrane 21, the spring 20 is tensioned.
  • a switching valve 27 which is arranged in a bypass 26, which connects the outlet of the feed pump 12 to the fuel tank 13.
  • the switching valve 27 designed as a 2/2-way solenoid valve normally closes, i.e. with the diesel engine running, the bypass 26 and gives this in the event of a shutdown, i.e. with an appealing switch-off device 19, free.
  • the switching valve 27 has a valve member 28 which cooperates with a valve seat 30 surrounding a valve inlet opening 29.
  • the valve member 28 is fixedly connected to a magnet armature 31 of an electromagnet 32 and is held in the valve open position by a valve opening spring 33 when the electromagnet 32 is not energized.
  • the electromagnet 32 is switched by an electronic control unit 42 which is electrically connected to an electrical signal box 46 flanged to the fuel injection pump 10 and carries out further control functions which are not important here.
  • the mode of operation of the shutdown device 19 described is as follows:
  • the electromagnet 32 of the switching valve 27 When the diesel engine is started, the electromagnet 32 of the switching valve 27 is energized. The magnet armature 31 is attracted and the valve member 28 is pressed onto the valve seat 30 by compressing the valve opening spring 33. The switching valve 27 shuts off the bypass 26. Since there is still no pressure on the delivery side of the delivery pump 12, the magnetic force required to close the valve is relatively low. With the onset of fuel delivery by the feed pump 12, the greatest electromagnetic force must then be applied to keep the switching valve 27 closed when the magnet armature 31 is tightened.
  • the feed pressure reaches the clamping pressure of the spring spring set by the pressure spring 24 to about 0.8 bar overpressure chers 20 exceeds, the spring accumulator 20 is tensioned by moving the membrane 21 against the force of the compression spring 24.
  • the inlet valve 17 opens and fuel flows via the delivery line 15 into the suction chamber 11 of the fuel injection pump 10. If the pressure in the suction chamber 11 exceeds 1 bar overpressure, the overflow valve 18 opens and excess fuel flows via the return line 16 back into the fuel tank 13.
  • the pressure in the suction chamber 11 is thus kept constant at 1 bar overpressure and loads the spring chamber 24 of the spring accumulator 20.
  • the feed pump 12 now delivers with an overpressure of 2 bar.
  • the fuel injection pump 10 now supplies the injection nozzles 43 of the cylinders of the diesel engine with fuel under injection pressure.
  • An electronic control unit 42 detects a malfunction that occurs in the diesel engine and necessitates switching off the diesel engine. This switches off the excitation voltage on the electromagnet 32 of the switching valve 27.
  • the valve opening spring 33 lifts the valve member 28 from the valve seat 30.
  • the switching valve 27 opens.
  • the pressure on the output side of the feed pump 12 is reduced via the open switching valve 27, as a result of which the flow through the suction chamber is interrupted, the inlet valve 17 and the return flow valve 18 close and the suction chamber 11 is shut off.
  • the volume of the spring chamber 23 increases and fills with a fuel volume sucked out of the suction chamber 11.
  • the pressure in the suction chamber 11 is thus reduced to less than 0.2 bar absolute.
  • the pump element of the injection pump 10 can no longer be sufficiently filled with fuel, so that no more fuel is delivered to the injection nozzles.
  • the diesel engine is no longer fueled and stops immediately.
  • the fuel injection device shown in FIG. 2 differs from that in FIG. 1 only in the combination of different assemblies of the shutdown device 19 into structural units. The same components are therefore provided with the same reference numerals.
  • the overflow valve 18 located in the return line 16 is combined with the switching valve 27 to form a structural unit 34.
  • the input of the switching valve 27 is still connected to the output of the feed pump 12, while the output of the switching valve 27 is connected directly to the output of the overflow valve 18. This measure eliminates the separate bypass section from the outlet of the switching valve 27 to the fuel tank 13. The fuel return from the outlet of the switching valve 27 takes place via the return line 16.
  • the inlet valve 17 located in the delivery line 15 is integrated in the spring accumulator 20, that is to say it is combined to form a second structural unit 35.
  • the diaphragm 21, which still divides the spring accumulator 20 into the pressure chamber 22 and the spring chamber 23, has a flow opening 36 and a valve seat 37 surrounding it, with which the valve member 38 of the inlet valve 17 cooperates.
  • the inlet valve 17 is fastened to the membrane 21 with a housing web 39, and the valve closing spring 40 is supported on the one hand on the housing web 39 and on the other hand on the valve member 38.
  • the housing web 39 also forms a stop 41 corresponding in function to the stop 25 in FIG. 1, which comes to rest against the force of the compression spring 24 against the bottom of the spring chamber 23 after a displacement path of the membrane 21.
  • the overflow valve 18 and the inlet valve 17 are designed as a simple check valve.
  • the fuel injection device shown schematically in FIG. 3 differs from that in FIG. 2 only by a different design of the inlet valve 17 ', which is also integrated in the spring accumulator 20, that is to say it is combined with the spring accumulator 20 to form the structural unit 35.
  • the same components are therefore provided with the same reference numerals.
  • the inlet valve 17 ' which also acts here as a one-way valve, is designed here as a slide valve, consisting of a control slide 51 and a guide sleeve 52 which accommodates the control slide 51 in an axially displaceable manner.
  • the inlet valve 17 ' is arranged in the spring chamber 23 of the spring accumulator 20, the guide sleeve 52 being fastened to the bottom of the spring chamber 23 and the control slide 51 to the membrane 21.
  • the compression spring 24 is in turn supported in the same way on the bottom of the spring chamber 23 and on the membrane 21.
  • the end face of the guide sleeve 52 facing the membrane 21 forms a stop 53 comparable to the stop 41 in FIG. 2 or the stop 25 in FIG. 1.
  • the guide sleeve 52 has two diametrically opposite radial bores 54, 55, which are provided with an annular control groove 56 cooperate on the circumference of the control slide 51.
  • the control groove 56 is connected via a transverse bore 57 to an axial channel 58 designed as a blind hole.
  • the axial channel 58 opens at the end face of the control slide 51 fastened to the membrane 21, specifically there coaxially with a flow opening 59 in the membrane 21.
  • the control groove 56 on the control slide 51 and the radial bores 54, 55 in the guide sleeve 52 are spatially arranged in relation to one another that they first come into contact with each other when the diaphragm 21 abuts the stop 53 and then fuel can flow into the spring chamber 23 from the storage space 22 via the axial channel 58, the transverse bore 57, the control groove 56 and the radial bores 54, 55. In all other positions of the membrane 21 and thus of the control slide 51, the control groove 56 is covered in a liquid-tight manner by the inner wall of the guide sleeve 52.
  • this fuel injection device largely corresponds to the two fuel injection devices described above, with the following difference: after the diesel engine is started and the bypass 26 is shut off by the switching valve 27, the fuel flowing into the storage chamber 22 displaces the diaphragm 21 against the force of the return spring 24 up to the stop 53 on the guide sleeve 52. In this position, the control groove 56 is in the region of the radial bores 54, 55 and the flow from the feed pump 12 to the suction chamber 11 is given. The pressure prevailing in the suction chamber 11 is determined exclusively by the overflow valve 18 and can be set as desired.
  • the storage chamber 22 is connected to the released bypass 26. As a result, the pressure in the storage chamber 22 is suddenly reduced.
  • the compression spring 24 pushes back the diaphragm 21 and thus the control slide 51 fastened to the diaphragm 21, as a result of which the control groove 56 is closed again by the guide sleeve 52 and the spring chamber 23 is again hermetically separated from the storage chamber 22.
  • the increasing spring chamber volume ensures the necessary pressure reduction in the suction chamber 11 to the absolute pressure of 0.2 bar.
  • the fuel injection device shown in FIG. 4 differs from that in FIG. 1 essentially only by a differently designed connection of the spring chamber 23 of the spring accumulator 20 to the suction chamber 11 '.
  • the respective mounting position of the inlet valve 17 and the fuel filter 45 was changed.
  • the same components are therefore also given the same designation here, and the differently designed suction chamber is given the reference number 11 '.
  • the spring chamber 23 of the spring accumulator 20 has no connection to the delivery line 15 in FIG. but is connected via a suction line 61 to the downstream area 11a 'of the suction space 11', the suction line 61 being connected to a section 16a of the return line 16 located upstream of the overflow valve 18.
  • both the overflow valve 18 and the spring chamber 23 are to be mounted as close as possible to the suction space 11 'in order to keep the space to be partially evacuated as small as possible, which is beneficial for a quick shutdown.
  • the inlet valve 17 has also been drawn closer to an upstream region 11b 'of the suction chamber 11'.
  • the fuel filter 45 is, as is usual in injection systems, connected directly behind the feed pump 12, so that its fuel volume cannot delay the shutdown.
  • the separation of the suction chamber 11 'into an outflow-side region 11a' and into an inflow-side region 11b ', indicated by a broken line, is intended to indicate that this is a fuel injection pump, the suction chamber 11' of which is intended for a specific flow through the The inlet side to the downstream side is divided and has flow restricting restrictors on the inflow side.
  • a fuel injection pump is e.g. known from Figure 6 of DE-A-35 09 536 and therefore not the subject of the present invention.
  • the mode of operation of the fourth exemplary embodiment described above essentially corresponds to that of the first exemplary embodiment described for FIG. Only the spring chamber 23 of the spring accumulator 20, which enlarges during the shutdown process, is connected by means of the suction line 61 and here the section 16a of the return line 16, upstream of the overflow valve 18, to the outflow-side region 11a 'of the suction chamber 11'. Since this connection has also been made in this exemplary embodiment between the inlet valve 17 and the overflow valve 18, here too, as in the examples described above, with the switching valve 27 open and the volume of the spring chamber 23 increasing, the suction chamber 11 'is placed under negative pressure, so that the injection pump 10 can no longer deliver and the associated internal combustion engine "dies", ie stop.
  • the shutdown device implemented in each of the exemplary embodiments leads to very rapid shutdown when the fuel feed pump 12 is driven by an electric motor and the feed pump also stops in the event of a shutdown.
  • the described embodiments are also in the presence of a mechanical, for. B. fuel pump driven by the camshaft of the injection pump 10 can advantageously be used since the delivery line 15 is short-circuited by the switching valve 27, the delivery into the suction chamber 11, 11 'thus stops and the increasing volume of the spring chamber 23 for the vacuum required for switching off Suction chamber ensures that quick parking is also possible here.
  • the invention naturally also includes combinations of the device described in the four exemplary embodiments.
  • the spring chamber 23 can both the input as well as to the output of the suction chamber 11, 11 'are connected if this is necessary with corresponding large pumps.
  • a central connection to the suction space is also conceivable if a corresponding connection is provided and this measure leads to faster shutdown.

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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)

Abstract

In a fuel injection device for internal combustion engines, in particular for diesel engines, comprising a fuel injection pump (10), a fuel delivery pump (12) and a fuel injection shut-off system (19) in the event of a fault, said system consists, in order to provide high speed operation of the shut-off system (19), of a chargeable spring (20) which can be loaded by means of the delivery pressure of the delivery pump (12) and of an electromagnetically operator control valve (27). The chargeable spring (20) is linked, via its storage chamber (22) to the outlet of the delivery pump and via its spring chamber (23) to the inlet of the intake chamber (11) of the injection pump (10). The control valve (27) connected to the outlet of the delivery pump (12) is normally closed and, in order to shut off the fuel injection, opens up a by-pass (26) leading to a fuel container (13). A feed valve (17) and a spill valve (17, 18) located upstream and downstream of the intake chamber (11) ensure its closure in the event of a fault and the setting of a constant pressure in said chamber during normal operation.

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen, insbesondere für Dieselmotoren, der im Oberbegriff des Anspruchs 1 angegebenen Gattung.The invention relates to a fuel injection device for internal combustion engines, in particular for diesel engines, of the type specified in the preamble of claim 1.

Bei solchen Kraftstoffeinspritzvorrichtungen dient die Abschaltvorrichtung dazu, bei Auftreten von Störungen oder Fehlern die Kraftstoffeinspritzung möglichst schlagartig zu beenden. Hierzu ist es erforderlich, nicht nur die Förderleistung der Förderpumpe zum Saugraum der Kraftstoffeinspritzpumpe zu unterbinden, sondern auch zu verhindern, daß aus dem Saugraum weiterhin Kraftstoff zu den Einspritzdüsen gefördert wird. Letzeres ist dann nicht mehr der Fall, wenn der Saugraumdruck unter 0,2 bar absolut abfällt, da dann das Pumpenelement der Kraftstoffeinspritzpumpe nicht mehr ausreichend mit Kraftstoff gefüllt wird.In such fuel injection devices, the shutdown device serves to terminate the fuel injection as suddenly as possible in the event of faults or errors. For this purpose, it is necessary not only to prevent the delivery capacity of the feed pump to the suction chamber of the fuel injection pump, but also to prevent fuel from continuing to be conveyed from the suction chamber to the injection nozzles. The latter is no longer the case if the suction chamber pressure drops below 0.2 bar absolute, since then the pump element of the fuel injection pump is no longer adequately filled with fuel.

Bei einer bekannten Kraftstoffeinspritzvorrichtung der eingangs genannten Art (DE-A-21 45 983) weist hierzu die Abschaltvorrichtung ein als Tellerventil ausgebildetes Absperrventil und eine Saugpumpe auf, die zu einer Baueinheit zusammengefaßt sind. Die Saugpumpe besteht aus einem in einem Speicherraum verschiebbar geführten Kolben und einer den Kolben beaufschlagenden Druckfeder. Der Kolben wird im Normalfall mittels einer mechanischen Arretiervorrichtung bei gespannter Druckfeder in einer Ausschiebestellung gehalten, in welcher das Speichervolumen des Speicherraums nahezu Null ist. In dieser Stellung wird das Tellerventil von dem Kolben über einen Ventilstößel entgegen der Kraft einer Ventilschließfeder in Offenstellung gehalten. Der von der Förderpumpe geförderte Kraftstoff gelangt bei offenem Tellerventil in den von dem Kolben begrenzten Raum, in welchem die Kolben-Druckfeder angeordnet ist, und strömt von hier aus in den Saugraum ein. Im Abschaltfall wird die Arretiervorrichtung gelöst. Der Kolben wird von der Kolben-Druckfeder verschoben und gibt den Speicherraum zunehmend frei. Dadurch entsteht in der Leitung zwischen Abschaltvorrichtung und Saugraum ein Unterdruck, durch den verhindert wird, daß Kraftstoff weiter in den Saugraum der Einspritzpumpe gelangen kann. Durch den im Speicherraum zurückgleitenden Kolben wird auch das Tellerventil freigegeben, das unter der Wirkung seiner Ventilschließfeder in seine Schließstellung übergeht. Die Förderpumpe ist vom Saugraum abgesperrt und fördert über ein Überströmventil in den Kraftstoffbehälter zurück.In a known fuel injection device of the type mentioned at the beginning (DE-A-21 45 983), the shutdown device has a shut-off valve designed as a poppet valve and a suction pump, which are combined to form a structural unit. The suction pump consists of a piston displaceably guided in a storage space and a compression spring acting on the piston. The piston is normally held in an extended position by means of a mechanical locking device with the compression spring tensioned, in which the storage volume of the storage space is almost zero. In this position, the poppet valve is held in the open position by the piston via a valve tappet against the force of a valve closing spring. When the poppet valve is open, the fuel delivered by the feed pump enters the space delimited by the piston, in which the piston compression spring is arranged, and flows from here into the suction space. In the event of a shutdown, the locking device is released. The piston is moved by the piston compression spring and increasingly frees up the storage space. This creates a negative pressure in the line between the shutdown device and the suction chamber, which prevents fuel from getting further into the suction chamber of the injection pump. The poppet valve is also released by the piston sliding back in the storage space, which passes into its closed position under the action of its valve closing spring. The feed pump is shut off from the suction chamber and feeds back into the fuel tank via an overflow valve.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Kraftstoffeinspritzvorrichtung mit den kennzeichnenden Merkmalen des Anspruchs 1 hat den Vorteil, mit handelsüblichen Bauelementen, wie Federspeicher, einfache Hydraulikventile und Magnetventil eine Schnellabschaltvorrichtung zu schaffen, die konstruktiv einfach aufgebaut und kostengünstig zu fertigen ist. Durch das Überströmventil wird der Saugraumdruck auf einen definierten Druck von z.B. 1 bar Überdruck eingestellt. Der den Saugraumdruck übersteigende Förderdruck, hier z.B. 2 bar Überdruck, spannt den Federspeicher, so daß dessen Federkammer das kleinstmögliche Volumen aufweist. Im Abschaltfalle wird der Bypaß geöffnet, wodurch der von dem Förderdruck in der Speicherkammer des Federspeichers erzeugte Überdruck zusammenbricht. Der Federspeicher entspannt sich, und das sich vergrößernde Federkammervolumen bewirkt eine Reduzierung des Druckes im Saugraum auf hier von weniger als 0,2 bar absolut, wodurch die Förderung von Kraftstoff zu den Einspritzdüsen schlagartig unterbrochen wird. Die Brennkraftmaschine erhält keinen Kraftstoff mehr und stellt unmittelbar ab.The fuel injection device according to the invention with the characterizing features of claim 1 has the advantage of creating a quick shutdown device with commercially available components, such as spring accumulators, simple hydraulic valves and solenoid valves, which is structurally simple and inexpensive to manufacture. The suction chamber pressure is reduced to a defined pressure of e.g. 1 bar overpressure set. The delivery pressure exceeding the suction chamber pressure, here e.g. 2 bar overpressure, tensions the spring accumulator so that its spring chamber has the smallest possible volume. In the event of a shutdown, the bypass is opened, as a result of which the excess pressure generated by the delivery pressure in the storage chamber of the spring accumulator breaks down. The spring accumulator relaxes, and the increasing spring chamber volume causes the pressure in the suction chamber to be reduced to less than 0.2 bar absolute, as a result of which the delivery of fuel to the injection nozzles is suddenly interrupted. The internal combustion engine no longer receives fuel and switches off immediately.

Durch die in den weiteren Ansprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen der im Anspruch 1 angegebenen Kraftstoffeinspritzvorrichtung möglich.Advantageous further developments and improvements of the fuel injection device specified in claim 1 are possible through the measures listed in the further claims.

Eine vorteilhafte Ausführungsform der Erfindung ergibt sich dabei aus Anspruch 2. Durch diese Ausbildung des elektromagnetischen Schaltventils ist die größte Ventilbetätigungskraft, hier die Schließkraft des Ventils, bei angezogenem Magnetanker aufzubringen. Dafür sind geringere Kräfte erforderlich als wenn die größte Ventilkraft bei ausgefahrenem Magnetanker entgegen der Kraft einer Schließfeder aufgebracht werden müßte. Dadurch läßt sich der Elektromagnet des Schaltventils, insbesondere dessen Wikkelraum, kleiner dimensionieren, und damit das Schaltventil kleinvolumig halten. Außerdem öffnet bei ungewollter Stromunterbrechung das Schaltventil und setzt dadurch die Kraftstoffeinspritzung still.An advantageous embodiment of the invention results from claim 2. This configuration of the electromagnetic switching valve means that the greatest valve actuation force, here the closing force of the valve, is to be applied when the magnet armature is tightened. For this, lower forces are required than if the greatest valve force had to be applied against the force of a closing spring when the magnet armature was extended. As a result, the electromagnet of the switching valve, in particular its winding space, can be dimensioned smaller, and the switching valve can thus be kept small in volume. In addition, the switching valve opens in the event of an unwanted power cut, thereby stopping fuel injection.

Eine vorteilhafte Ausführungsform der Erfindung ergibt sich auch aus Anspruch 4. Durch das vorgespannte Zulaufventil, das wirkungsmäßig parallel zur Speicherkammer des Federspeichers angeordnet ist, wird einerseits das Spannen des Federspeichers durch den Förderdruck der Förderpumpe bei Förderbeginn gesichert und andererseits eine anschlußseitige Absperrung des Saugraums der Einspritzpumpe zur Förderpumpe hin erzielt.An advantageous embodiment of the invention also results from claim 4. Due to the biased supply valve, which is arranged in effect parallel to the storage chamber of the spring accumulator, the tensioning of the spring accumulator is secured on the one hand by the delivery pressure of the feed pump at the start of delivery and on the other hand a connection-side shutoff of the suction chamber of the injection pump achieved towards the feed pump.

Eine vorteilhafte Ausführungsform der Erfindung ergibt sich auch aus Anspruch 6. Diese Maßnahme bringt eine Vereinfachung in der Montage der Kraftstoffeinspritzvorrichtung.An advantageous embodiment of the invention also results from claim 6. This measure simplifies the assembly of the fuel injection device.

Eine vorteilhafte Ausführungsform der Erfindung ergibt sich auch aus Anspruch 8, insbesondere in Verbindung mit Anspruch 9. Durch die dort angegebene Ausbildung des Zulaufventils muß dieses nicht mit einem so genau definierten Öffnungsdruck versehen werden, wie dies bei ebenfalls als Zulaufventil einsetzbaren Rückschlagventilen der Fall ist. Das Zulaufventil arbeitet sicherer und kennt auch nicht die bei Rückschlagventilen häufig auftretenden Probleme der Undichtigkeit, und zwar wegen der Überdeckung beim Abstellen.An advantageous embodiment of the invention also results from claim 8, in particular in connection with claim 9. Due to the design of the inlet valve specified there, it does not have to be provided with a precisely defined opening pressure, as is the case with check valves which can also be used as inlet valves. The inlet valve works more safely and is not aware of the leakage problems that frequently occur with non-return valves because of the overlap when it is turned off.

Eine vorteilhafte Ausführungsform der Erfindung ergibt sich auch aus Anspruch 10. Durch diese Maßnahme läßt sich eine zusätzliche Kraftstoffleitung vom Schaltventil zum Kraftstoffbehälter einsparen. Deren Funktion wird von der ohnehin vorhandenen Rücklaufleitung übernommen. Durch den gemäß Anspruch 11 erfolgenden Anschluß der Federkammer des Federspeichers an den abströmseitigen Bereich des Saugraums erfolgt die erforderliche Druckreduzierung im Saugraum auch bei solchen Kraftstoffeinspritzpumpen genügend schnell, bei denen strömungsbegrenzende oder -leitende Mittel im zuströmseitigen Breich des Saugraums vorgesehen sind und das Abstellen verzögern können.An advantageous embodiment of the invention also results from claim 10. This measure saves an additional fuel line from the switching valve to the fuel tank. Their function is taken over by the return line, which is already present. Due to the connection of the spring chamber of the spring accumulator to the outflow-side region of the suction chamber, the required pressure reduction in the suction chamber takes place quickly enough even in those fuel injection pumps in which flow-limiting or flow-guiding means are provided in the inflow-side region of the suction chamber and can delay the shutdown.

Die Erfindung ist anhand von in der Zeichnung dargestellten Ausführungsbeispielen in der nachfolgenden Beschreibung näher erläutert. Es zeigen teilweise schematisiert:

  • Figur 1 bis 4 jeweils ein Blockschaltbild für vier Ausführungsbeispiele einer Kraftstoffeinspritzvorrichtung mit einer Schnellabschaltvorrichtung.
The invention is explained in more detail in the following description with reference to exemplary embodiments shown in the drawing. Some of them show schematically:
  • 1 to 4 each show a block diagram for four exemplary embodiments of a fuel injection device with a quick shutdown device.

Beschreibung der AusführungsbeispieleDescription of the embodiments

Die in Figur 1 dargestellte, an sich bekannte Kraftstoffeinspritzvorrichtung für einen Dieselmotor als Beispiel einer Brennkraftmaschine weist eine nur schematisch angedeutete Kraftstoffeinspritzpumpe 10 auf. Die Kraftstoffeinspritzpumpe 10 saugt mit einem nicht dargestellten Pumpenelement Kraftstoff aus einem Saugraum 11 der Kraftstoffeinspritzpumpe 10 an, komprimiert diesen auf Einspritzdruck und verteilt die unter Einspritzdruck stehende Kraftstoffmenge an Einspritzdüsen, die den einzelnen Zylindern des Dieselmotors zugeordnet sind. In Figur 1 ist der Übersichtlichkeit halber nur eine einzige Einspritzdüse 43 für einen Motorzylinder dargestellt.The fuel injection device for a diesel engine, which is known per se and is shown in FIG. 1 as an example of an internal combustion engine, has a fuel injection pump 10 which is only indicated schematically. The fuel injection pump 10 sucks fuel from a suction chamber 11 of the fuel injection pump 10 with a pump element (not shown), compresses it to injection pressure and distributes the amount of fuel under injection pressure to injection nozzles that are assigned to the individual cylinders of the diesel engine. For the sake of clarity, FIG. 1 shows only a single injection nozzle 43 for an engine cylinder.

Der Saugraum 11 wird von einer Kraftstofförderpumpe 12 aus einem Kraftstoffbehälter 13 mit Kraftstoff gefüllt. Hierzu ist die Förderpumpe 12 über einen Saugstutzen 14 mit Kraftstoffilter 44 an dem Kraftstoffbehälter 13 und über eine Förderleitung 15 mit einem weiteren Kraftstoffilter 45 an dem Eingang des Saugraums 11 angeschlossen. Der Ausgang des Saugraums 11 ist über eine Rücklaufleitung 16 wieder mit dem Kraftstoffbehälter 13 verbunden. In der Förderleitung 15 ist ein Zulaufventil 17 und in der Rücklaufleitung 16 ist ein Überströmventil 18 mit jeweils definiertem Öffnungsdruck von hier 1 bar Überdruck, angeordnet. Die Durchflußrichtung des Zulaufventils 17 ist von der Förderpumpe 12 zu dem Saugraum 11 hin gerichtet, während die Durchflußrichtung des Überströmventils 18 von dem Saugraum 11 zu dem Kraftstoffbehälter 13 hin gerichtet ist. Die beiden hier als einfache Rückschlagventile ausgeführten Ventile 17, 18 sorgen dafür, daß eine Kraftstofförderung vom Kraftstoffbehälter 13 zu dem Saugraum 11 erst bei einem definierten Förderdruck von größer 2 bar absolut einsetzt und der Überdruck im Saugraum 11 konstant auf 1 bar gehalten wird.The suction chamber 11 is filled with fuel by a fuel delivery pump 12 from a fuel tank 13. For this purpose, the feed pump 12 is connected to the fuel tank 13 via a suction port 14 with a fuel filter 44 and via a feed line 15 to a further fuel filter 45 at the inlet of the suction chamber 11. The outlet of the suction chamber 11 is connected to the fuel tank 13 again via a return line 16. An inlet valve 17 is arranged in the delivery line 15 and an overflow valve 18 is arranged in the return line 16, each with a defined opening pressure of 1 bar overpressure here. The flow direction of the feed valve 17 is directed from the feed pump 12 to the suction chamber 11, while the flow direction of the overflow valve 18 is directed from the suction chamber 11 to the fuel tank 13. The two valves 17, 18 designed here as simple non-return valves ensure that fuel delivery from the fuel tank 13 to the suction chamber 11 only begins at a defined delivery pressure of greater than 2 bar and that the excess pressure in the suction chamber 11 is kept constant at 1 bar.

Die beiden Ventile 17, 18 sind Teil einer Abschaltvorrichtung 19 für die Kraftstoffeinspritzung im Not- oder Störungsfall. Die Abschaltvorrichtung 19 weist ferner einen zwischen der Förderpumpe 12 und dem Saugraum 11, also parallel zu dem Zulaufventil 17, angeordneten Federspeicher 20 auf, der durch eine Membran 21 in bekannter Weise in eine Speicherkammer 22 und eine Federkammer 23 unterteilt ist. In der Federkammer 23 ist eine Druckfeder 24, die sich einerseits an der Membran 21 und andererseits gehäuseseitig abstützt, und ein Anschlag 25 zur Begrenzung der Verschiebebewegung der Membran 21 angeordnet. Die Federkammer 23 ist mit dem Eingang des Saugraums 11 bzw. mit dem Ausgang des Zulaufventils 17 und die Speicherkammer 22 ist mit dem Ausgang der Förderpumpe 12 bzw. mit dem Eingang des Zulaufventils 17 verbunden. Die Druckfeder 24 ist so eingestellt, daß bei druckloser Federkammer 23 ein Druck in der Speicherkammer 22 von 0,8 bar Überdruck ausreichend ist, die Druckfeder 24 so weit zu komprimieren, daß sich die Membran 21 an den Anschlag 25 anlegt. In dieser Stellung der Membran 21 ist der Federspeicher 20 gespannt.The two valves 17, 18 are part of a shutdown device 19 for fuel injection in the event of an emergency or malfunction. The shutdown device 19 also has a spring accumulator 20 which is arranged between the feed pump 12 and the suction chamber 11, that is to say parallel to the inlet valve 17 and is divided in a known manner into a storage chamber 22 and a spring chamber 23 by a membrane 21. In the spring chamber 23 there is a compression spring 24, which is supported on the one hand on the membrane 21 and on the other hand on the housing side, and a stop 25 for limiting the displacement movement of the membrane 21. The spring chamber 23 is connected to the inlet of the suction chamber 11 or to the outlet valve 17 and the storage chamber 22 is connected to the outlet of the feed pump 12 or the inlet of the inlet valve 17. The compression spring 24 is set so that when the spring chamber 23 is depressurized, a pressure in the storage chamber 22 of 0.8 bar overpressure is sufficient to compress the compression spring 24 to such an extent that the membrane 21 bears against the stop 25. In this position of the membrane 21, the spring 20 is tensioned.

Ein weiterer Teil der Abschaltvorrichtung 19 ist ein Schaltventil 27, das in einem Bypaß 26 angeordnet ist, der den Ausgang der Förderpumpe 12 mit dem Kraftstoffbehälter 13 verbindet. Das als 2/ 2-Wege-Magnetventil ausgebildete Schaltventil 27 sperrt im Normalfall, d.h. bei laufendem Dieselmotor, den Bypaß 26 und gibt diesen im Abschaltfall, d.h. bei ansprechender Abschaltvorrichtung 19, frei. Wie in Fig. 1 schematisch angedeutet ist, hat das Schaltventil 27 ein Ventilglied 28, das mit einem eine Ventileinlaßöffnung 29 umgebenden Ventilsitz 30 zusammenwirkt. Das Ventilglied 28 ist mit einem Magnetanker 31 eines Elektromagneten 32 fest verbunden und wird von einer Ventilöffnungsfeder 33 bei unerregtem Elektromagneten 32 in der Ventiloffenstellung gehalten. Der Elektromagnet 32 wird von einem elektronischen Steuergerät 42 geschaltet, das mit einem an der Kraftstoffeinspritzpumpe 10 angeflanschten elektrischen Stellwerk 46 elektrisch verbunden ist und weitere Steuerfunktionen ausführt, die hier nicht von Bedeutung sind.Another part of the shutdown device 19 is a switching valve 27, which is arranged in a bypass 26, which connects the outlet of the feed pump 12 to the fuel tank 13. The switching valve 27 designed as a 2/2-way solenoid valve normally closes, i.e. with the diesel engine running, the bypass 26 and gives this in the event of a shutdown, i.e. with an appealing switch-off device 19, free. As indicated schematically in Fig. 1, the switching valve 27 has a valve member 28 which cooperates with a valve seat 30 surrounding a valve inlet opening 29. The valve member 28 is fixedly connected to a magnet armature 31 of an electromagnet 32 and is held in the valve open position by a valve opening spring 33 when the electromagnet 32 is not energized. The electromagnet 32 is switched by an electronic control unit 42 which is electrically connected to an electrical signal box 46 flanged to the fuel injection pump 10 and carries out further control functions which are not important here.

Die Wirkungsweise der beschriebenen Abschaltvorrichtung 19 ist wie folgt:The mode of operation of the shutdown device 19 described is as follows:

Mit Anlassen des Dieselmotors wird der Elektromagnet 32 des Schaltventils 27 bestromt. Der Magnetanker 31 wird angezogen und das Ventilglied 28 wird auf den Ventilsitz 30 unter Zusammendrücken der Ventilöffnungsfeder 33 aufgepreßt. Das Schaltventil 27 sperrt den Bypaß 26 ab. Da auf der Förderseite der Förderpumpe 12 noch kein Druck ansteht, ist die erforderliche Magnetkraft zum Schließen des Ventils relativ gering. Mit Einsetzen der Kraftstofförderung durch die Förderpump 12 muß dann die größte elektromagnetische Kraft zum Geschlossenhalten des Schaltventils 27 bei angezogenem Magnetanker 31 aufgebracht werden.When the diesel engine is started, the electromagnet 32 of the switching valve 27 is energized. The magnet armature 31 is attracted and the valve member 28 is pressed onto the valve seat 30 by compressing the valve opening spring 33. The switching valve 27 shuts off the bypass 26. Since there is still no pressure on the delivery side of the delivery pump 12, the magnetic force required to close the valve is relatively low. With the onset of fuel delivery by the feed pump 12, the greatest electromagnetic force must then be applied to keep the switching valve 27 closed when the magnet armature 31 is tightened.

Sobald bei einsetzender Kraftstofförderung durch die Förderpumpe 12 der Förderdruck den durch die Druckfeder 24 auf etwa 0,8 bar Überdruck eingestellten Spanndruck des Federspeichers 20 übersteigt, wird, der Federspeicher 20 durch Verschieben der Membran 21 gegen die Kraft der Druckfeder 24 gespannt. Sobald der Förderdruck 1 bar Überdruck übersteigt, öffnet das Zulaufventil 17 und Kraftstoff strömt über die Förderleitung 15 in den Saugraum 11 der Kraftstoffeinspritzpumpe 10. Übersteigt der Druck im Saugraum 11 1 bar Überdruck, so öffnet das Überströmventil 18 und überschüssiger Kraftstoff fließt über die Rücklaufleitung 16 wieder in den Kraftstoffbehälter 13. Der Druck im Saugraum 11 wird damit konstant auf 1 bar Überdruck gehalten und belastet die Federkammer 24 des Federspeichers 20. Die Förderpumpe 12 fördert jetzt mit einem Überdruck von 2 bar. In bekannter Weise versorgt nunmehr die Kraftstoffeinspritzpumpe 10 die Einspritzdüsen 43 der Zylinder des Dieselmotors mit unter Einspritzdruck stehendem Kraftstoff.As soon as the fuel delivery by the feed pump 12 begins, the feed pressure reaches the clamping pressure of the spring spring set by the pressure spring 24 to about 0.8 bar overpressure chers 20 exceeds, the spring accumulator 20 is tensioned by moving the membrane 21 against the force of the compression spring 24. As soon as the delivery pressure exceeds 1 bar overpressure, the inlet valve 17 opens and fuel flows via the delivery line 15 into the suction chamber 11 of the fuel injection pump 10.If the pressure in the suction chamber 11 exceeds 1 bar overpressure, the overflow valve 18 opens and excess fuel flows via the return line 16 back into the fuel tank 13. The pressure in the suction chamber 11 is thus kept constant at 1 bar overpressure and loads the spring chamber 24 of the spring accumulator 20. The feed pump 12 now delivers with an overpressure of 2 bar. In a known manner, the fuel injection pump 10 now supplies the injection nozzles 43 of the cylinders of the diesel engine with fuel under injection pressure.

Ein im Dieselmotor auftretender Störungsfall, der ein Abschalten des Dieselmotors erforderlich macht, wird von dem elektronischen Steuergerät 42 erkannt. Dieses schaltet die Erregerspannung am Elektromagneten 32 des Schaltventils 27 ab. Die Ventilöffnungsfeder 33 hebt das Ventilglied 28 vom Ventilsitz 30 ab. Das Schaltventil 27 öffnet. Der Druck auf der Ausgangsseite der Förderpumpe 12 wird über das geöffnete Schaltventil 27 abgebaut, wodurch die Saugraumdurchströmung unterbrochen wird, das Zulaufventil 17 und das Rückströmventil 18 schließen und den Saugraum 11 absperren. Durch die Druckentlastung der Speicherkammer 22 des Federspeichers 20 schiebt die Druckfeder 24 die Membran 21 zurück. Das Volumen der Federkammer 23 vergrößert sich und füllt sich mit einem aus dem Saugraum 11 abgesaugten Kraftstoffvolumen. Damit wird der Druck im Saugraum 11 auf weniger als 0,2 bar absolut abgesenkt. Bei diesem Druck im Saugraum 11 kann das Pumpenelement der Einspritzpumpe 10 nicht mehr ausreichend mit Kraftstoff aufgefüllt werden, so daß kein Kraftstoff mehr zu den Einspritzdüsen gefördert wird. Der Dieselmotor erhält damit keinen Kraftstoff mehr und stellt unmittelbar ab.An electronic control unit 42 detects a malfunction that occurs in the diesel engine and necessitates switching off the diesel engine. This switches off the excitation voltage on the electromagnet 32 of the switching valve 27. The valve opening spring 33 lifts the valve member 28 from the valve seat 30. The switching valve 27 opens. The pressure on the output side of the feed pump 12 is reduced via the open switching valve 27, as a result of which the flow through the suction chamber is interrupted, the inlet valve 17 and the return flow valve 18 close and the suction chamber 11 is shut off. Due to the pressure relief of the storage chamber 22 of the spring accumulator 20, the compression spring 24 pushes the membrane 21 back. The volume of the spring chamber 23 increases and fills with a fuel volume sucked out of the suction chamber 11. The pressure in the suction chamber 11 is thus reduced to less than 0.2 bar absolute. At this pressure in the suction chamber 11, the pump element of the injection pump 10 can no longer be sufficiently filled with fuel, so that no more fuel is delivered to the injection nozzles. The diesel engine is no longer fueled and stops immediately.

Die in Fig. 2 dargestellte Kraftstoffeinspritzvorrichtung unterscheidet sich von der in Fig. 1 nur durch die Zusammenfassung verschiedener Baugruppen der Abschaltvorrichtung 19 zu Baueinheiten. Gleiche Bauteile sind daher mit gleichen Bezugszeichen versehen.The fuel injection device shown in FIG. 2 differs from that in FIG. 1 only in the combination of different assemblies of the shutdown device 19 into structural units. The same components are therefore provided with the same reference numerals.

Das in der Rücklaufleitung 16 liegende Überströmventil 18 ist mit dem Schaltventil 27 zu einer Baueinheit 34 zusammengefaßt. Der Eingang des Schaltventils 27 ist nach wie vor mit dem Ausgang der Förderpumpe 12 verbunden, während der Ausgang des Schaltventils 27 unmittelbar an dem Ausgang des Überströmventils 18 angeschlossen ist. Durch diese Maßnahme entfällt der gesonderte Bypaßabschnitt vom Ausgang des Schaltventils 27 zu dem Kraftstoffbehälter 13. Der Kraftstoffrücklauf vom Ausgang des Schaltventils 27 erfolgt über die Rücklaufleitung 16.The overflow valve 18 located in the return line 16 is combined with the switching valve 27 to form a structural unit 34. The input of the switching valve 27 is still connected to the output of the feed pump 12, while the output of the switching valve 27 is connected directly to the output of the overflow valve 18. This measure eliminates the separate bypass section from the outlet of the switching valve 27 to the fuel tank 13. The fuel return from the outlet of the switching valve 27 takes place via the return line 16.

Das in der Förderleitung 15 liegende Zulaufventil 17 ist in dem Federspeicher 20 integriert, mit diesem also zu einer zweiten Baueinheit 35 zusammengefaßt. Die nach wie vor den Federspeicher 20 in Druckkammer 22 und Federkammer 23 unterteilende Membran 21 weist eine Durchflußöffnung 36 und einen diese umgebenden Ventilsitz 37 auf, mit dem das Ventilglied 38 des Zulaufventils 17 zusammenwirkt. Das Zulaufventil 17 ist mit einem Gehäusesteg 39 an der Membran 21 befestigt, und die Ventilschließfeder 40 stützt sich einerseits an dem Gehäusesteg 39 und andererseits an dem Ventilglied 38 ab. Der Gehäusesteg 39 bildet zugleich einen in der Funktion dem Anschlag 25 in Fig. 1 entsprechenden Anschlag 41, der nach einem Verschiebeweg der Membran 21 entgegen der Kraft der Druckfeder 24 am Boden der Federkammer 23 zur Anlage kommt. Auch hier sind das Überströmventil 18 und das Zulaufventil 17 als einfaches Rückschlagventil ausgebildet.The inlet valve 17 located in the delivery line 15 is integrated in the spring accumulator 20, that is to say it is combined to form a second structural unit 35. The diaphragm 21, which still divides the spring accumulator 20 into the pressure chamber 22 and the spring chamber 23, has a flow opening 36 and a valve seat 37 surrounding it, with which the valve member 38 of the inlet valve 17 cooperates. The inlet valve 17 is fastened to the membrane 21 with a housing web 39, and the valve closing spring 40 is supported on the one hand on the housing web 39 and on the other hand on the valve member 38. The housing web 39 also forms a stop 41 corresponding in function to the stop 25 in FIG. 1, which comes to rest against the force of the compression spring 24 against the bottom of the spring chamber 23 after a displacement path of the membrane 21. Here too, the overflow valve 18 and the inlet valve 17 are designed as a simple check valve.

Die Funktionsweise der Kraftstoffeinspritzvorrichtung gemäß Fig. 2 ist identisch mit der zu Fig. 1, so daß insoweit auf die vorstehende Beschreibung verwiesen wird.The mode of operation of the fuel injection device according to FIG. 2 is identical to that of FIG. 1, so that reference is made to the above description in this regard.

Die in Fig. 3 schematisch dargestellte Kraftstoffeinspritzvorrichtung unterscheidet sich von der in Fig. 2 nur durch eine andersartige Ausbildung des Zulaufventils 17', das ebenfalls in den Federspeicher 20 integriert ist, also mit dem Federspeicher 20 zu der Baueinheit 35 zusammengefaßt ist. Gleiche Bauteile sind daher mit gleichen Bezugszeichen versehen. Das Zulaufventil 17', das hier ebenfalls als Einwegventil wirkt, ist hier als Schieberventil, bestehend aus einem Steuerschieber 51 und einer den Steuerschieber 51 axial verschieblich aufnehmenden Führungshülse 52, ausgebildet. Das Zulaufventil 17' ist in der Federkammer 23 des Federspeichers 20 angeordnet, wobei die Führungshülse 52 am Boden der Federkammer 23 und der Steuerschieber 51 an der Membran 21 befestigt ist. Am Boden der Federkammer 23 und an der Membran 21 stützt sich in gleicher Weise wiederum die Druckfeder 24 ab. Die der Membran 21 zugekehrte Stirnseite der Führungshülse 52 bildet einen dem Anschlag 41 in Fig. 2 bzw. dem Anschlag 25 in Fig. 1 vergleichbaren Anschlag 53. Die Führungshülse 52 weist zwei diametral gegenüberliegende Radialbohrungen 54, 55 auf, die mit einer ringförmigen Steuernut 56 am Umfang des Steuerschiebers 51 zusammenwirken. Die Steuernut 56 ist über eine Querbohrung 57 mit einem als Sackloch ausgebildeten Axialkanal 58 verbunden. Der Axialkanal 58 mündet an der an der Membran 21 befestigten Stirnseite des Steuerschiebers 51, und zwar dort koaxial mit einer Durchflußöffnung 59 in der Membran 21. Die Steuernut 56 am Steuerschieber 51 und die Radialbohrungen 54, 55 in der Führungshülse 52 sind räumlich derart zueinander angeordnet, daß sie erste bei Anlage der Membran 21 an dem Anschlag 53 miteinander in Verbindung treten und dann Kraftstoff aus dem Speicherraum 22 über den Axialkanal 58, die Querbohrung 57, die Steuernut 56 und die Radialbohrungen 54, 55 in die Federkammer 23 einströmen kann. In allen anderen Stellungen der Membran 21 und damit des Steuerschiebers 51 ist die Steuernut 56 von der Innenwand der Führungshülse 52 flüssigkeitsdicht abgedeckt.The fuel injection device shown schematically in FIG. 3 differs from that in FIG. 2 only by a different design of the inlet valve 17 ', which is also integrated in the spring accumulator 20, that is to say it is combined with the spring accumulator 20 to form the structural unit 35. The same components are therefore provided with the same reference numerals. The inlet valve 17 ', which also acts here as a one-way valve, is designed here as a slide valve, consisting of a control slide 51 and a guide sleeve 52 which accommodates the control slide 51 in an axially displaceable manner. The inlet valve 17 'is arranged in the spring chamber 23 of the spring accumulator 20, the guide sleeve 52 being fastened to the bottom of the spring chamber 23 and the control slide 51 to the membrane 21. The compression spring 24 is in turn supported in the same way on the bottom of the spring chamber 23 and on the membrane 21. The end face of the guide sleeve 52 facing the membrane 21 forms a stop 53 comparable to the stop 41 in FIG. 2 or the stop 25 in FIG. 1. The guide sleeve 52 has two diametrically opposite radial bores 54, 55, which are provided with an annular control groove 56 cooperate on the circumference of the control slide 51. The control groove 56 is connected via a transverse bore 57 to an axial channel 58 designed as a blind hole. The axial channel 58 opens at the end face of the control slide 51 fastened to the membrane 21, specifically there coaxially with a flow opening 59 in the membrane 21. The control groove 56 on the control slide 51 and the radial bores 54, 55 in the guide sleeve 52 are spatially arranged in relation to one another that they first come into contact with each other when the diaphragm 21 abuts the stop 53 and then fuel can flow into the spring chamber 23 from the storage space 22 via the axial channel 58, the transverse bore 57, the control groove 56 and the radial bores 54, 55. In all other positions of the membrane 21 and thus of the control slide 51, the control groove 56 is covered in a liquid-tight manner by the inner wall of the guide sleeve 52.

Die Wirkungsweise dieser Kraftstoffeinspritzvorrichtung stimmt weitgehend mit den beiden vorstehend beschriebenen Kraftstoffeinspritzvorrichtungen überein, mit folgendem Unterschied: nach Anlassen des Dieselmotors und Absperren des Bypaß 26 durch das Schaltventil 27 verschiebt der in die Speicherkammer 22 einströmende Kraftstoff die Membran 21 gegen die Kraft der Rückstellfeder 24 bis zu dem Anschlag 53 an der Führungshülse 52. In dieser Stellung liegt die Steuernut 56 im Bereich der Radialbohrungen 54, 55 und der Durchfluß von der Förderpumpe 12 zu dem Saugraum 11 ist gegeben. Der im Saugraum 11 herrschende Druck wird ausschließlich von dem Überströmventil 18 bestimmt und kann beliebig eingestellt werden.The mode of operation of this fuel injection device largely corresponds to the two fuel injection devices described above, with the following difference: after the diesel engine is started and the bypass 26 is shut off by the switching valve 27, the fuel flowing into the storage chamber 22 displaces the diaphragm 21 against the force of the return spring 24 up to the stop 53 on the guide sleeve 52. In this position, the control groove 56 is in the region of the radial bores 54, 55 and the flow from the feed pump 12 to the suction chamber 11 is given. The pressure prevailing in the suction chamber 11 is determined exclusively by the overflow valve 18 and can be set as desired.

Erkennt das elektronische Steuergerät 42 den Störfall und schaltet die Magneterregung des Schaltventils 27 ab, so ist die Speicherkammer 22 an dem freigegebenen Bypaß 26 angeschlossen. Dadurch wird der Druck in der Speicherkammer 22 schlagartig abgebaut. Die Druckfeder 24 schiebt die Membran 21 und damit den an der Membran 21 befestigten Steuerschieber 51 zurück, wodurch die Steuernut 56 wieder von der Führungshülse 52 verschlossen wird und die Federkammer 23 wieder hermetisch von der Speicherkammer 22 abgetrennt ist. In gleicher Weise sorgt das sich vergrößernde Federkammervolumen für den nötigen Druckabbau im Saugraum 11 auf den Absolutdruck von 0,2 bar.If the electronic control unit 42 detects the fault and switches off the magnetic excitation of the switching valve 27, the storage chamber 22 is connected to the released bypass 26. As a result, the pressure in the storage chamber 22 is suddenly reduced. The compression spring 24 pushes back the diaphragm 21 and thus the control slide 51 fastened to the diaphragm 21, as a result of which the control groove 56 is closed again by the guide sleeve 52 and the spring chamber 23 is again hermetically separated from the storage chamber 22. In the same way, the increasing spring chamber volume ensures the necessary pressure reduction in the suction chamber 11 to the absolute pressure of 0.2 bar.

Die in Figur 4 dargestellte Kraftstoffeinspritzvorrichtung unterscheidt sich von der in Figur 1 im wesentlichen nur durch einen abweichend gestalteten Anschluß der Federkammer 23 des Federspeichers 20 an den Saugraum 11'. Außerdem wurde die jeweilige Anbaulage des Zulaufventils 17 und des Kraftstoffilters 45 verändert. Gleiche Bauteile sind deshalb auch hier gleich bezeichnet, der abweichend gestaltete Saugraum mit der Bezugszahl 11' versehen.The fuel injection device shown in FIG. 4 differs from that in FIG. 1 essentially only by a differently designed connection of the spring chamber 23 of the spring accumulator 20 to the suction chamber 11 '. In addition, the respective mounting position of the inlet valve 17 and the fuel filter 45 was changed. The same components are therefore also given the same designation here, and the differently designed suction chamber is given the reference number 11 '.

An die Förderleitung 15 der Förderpumpe 12 ist weiterhin sowohl die Speicherkammer 22 als auch der Eingang des Saugraums 11' angeschlossen, ebenfalls der mit dem Schaltventil 27 versehene Bypass 26. Die Federkammer 23 des Federspeichers 20 hat in Figur 4 jedoch keine Verbindung zur Förderleitung 15, sondern ist über eine Absaugleitung 61 mit dem abströmseitigen Bereich 11a' des Saugraums 11' verbunden, wobei die Absaugleitung 61 an einen stromaufwärts des Überströmventils 18 befindlichen Abschnitt 16a der Rücklaufleitung 16 angeschlossen ist.Both the storage chamber 22 and the inlet of the suction chamber 11 'are also connected to the delivery line 15 of the delivery pump 12, likewise the bypass 26 provided with the switching valve 27. However, the spring chamber 23 of the spring accumulator 20 has no connection to the delivery line 15 in FIG. but is connected via a suction line 61 to the downstream area 11a 'of the suction space 11', the suction line 61 being connected to a section 16a of the return line 16 located upstream of the overflow valve 18.

Selbstverständlich sind sowohl das Überströmventil 18 als auch die Federkammer 23 so nah wie möglich an den Saugraum 11' heran anzubauen, um den für das Abstellen teilweise zu evakuierenden Raum so klein wie möglich zu halten, was einem schnellen Abstellen zugute kommt. Aus diesem Grunde ist auch das Zulaufventil 17 näher an einen zuströmseitigen Bereich 11b' des Saugraums 11' heran eingezeichnet worden. Das Kraftstoffilter 45 ist, wie bei Einspritzanlagen üblich, direkt hinter der Förderpumpe 12 angeschlossen, so daß sein Kraftstoffvolumen das Abstellen nicht verzögern kann. Die vorstehend beschriebenen Anbaumaßnahmen zur Verringerung des zu evakuierenden Raumes bzw. Volumens sind selbstverständlich auch bei den zuvor beschriebenen Ausführungsbeispielen nach den Figuren 1 bis 3 von Vorteil und können deshalb auch dort angewendet werden.Of course, both the overflow valve 18 and the spring chamber 23 are to be mounted as close as possible to the suction space 11 'in order to keep the space to be partially evacuated as small as possible, which is beneficial for a quick shutdown. For this reason, the inlet valve 17 has also been drawn closer to an upstream region 11b 'of the suction chamber 11'. The fuel filter 45 is, as is usual in injection systems, connected directly behind the feed pump 12, so that its fuel volume cannot delay the shutdown. The above-described installation measures for reducing the space or volume to be evacuated are of course also advantageous in the previously described exemplary embodiments according to FIGS. 1 to 3 and can therefore also be used there.

Durch die mittels einer unterbrochenen Linie angedeutete Trennung des Saugraums 11' in einen abströmseitigen Bereich 11 a' und in einen zuströmseitigen Bereich 11 b' soll angedeutet werden, daß es sich hier um eine Kraftstoffeinspritzpumpe handelt, deren Saugraum 11' für eine gezielte Durchströmung von der Zulaufseite zur Abströmseite unterteilt ist und zuströmseitig den Durchfluß behindernde Drosselstellen aufweist. Eine solche Kraftstoffeinspritzpumpe ist z.B. aus Figur 6 der DE-A-35 09 536 bekannt und deshalb auch nicht Gegenstand der vorliegenden Erfindung.The separation of the suction chamber 11 'into an outflow-side region 11a' and into an inflow-side region 11b ', indicated by a broken line, is intended to indicate that this is a fuel injection pump, the suction chamber 11' of which is intended for a specific flow through the The inlet side to the downstream side is divided and has flow restricting restrictors on the inflow side. Such a fuel injection pump is e.g. known from Figure 6 of DE-A-35 09 536 and therefore not the subject of the present invention.

Die Wirkungsweise des zuvor beschriebenen vierten Ausführungsbeispiels entspricht im wesentlichen derjenigen des zu Figur 1 beschriebenen ersten Ausführungsbeispiels. Lediglich die sich beim Abstellvorgäng vergrößernde Federkammer 23 des Federspeichers 20 ist mittels der Absaugleitung 61 und hier des Abschnittes 16a der Rücklaufleitung 16, stromaufwärts des Überströmventils 18, an den abströmseitigen Bereich 11 a' des Saugraums 11' angeschlossen. Da dieser Anschluß auch bei diesem Ausführungsbeispiel zwischen dem Zulaufventil 17 und dem Überströmventil 18 erfolgt ist, wird auch hier, wie bei den zuvor beschriebenen Beispielen, bei offenem Schaltventil 27 und sich dann vergrößerndem Volumen der Federkammer 23 der Saugraum 11' under Unterdruck gesetzt, so daß die Einspritzpumpe 10 nicht mehr fördern kann und die zugehörige Brennkraftmaschine "abstirbt", d.h. stehenbleibt.The mode of operation of the fourth exemplary embodiment described above essentially corresponds to that of the first exemplary embodiment described for FIG. Only the spring chamber 23 of the spring accumulator 20, which enlarges during the shutdown process, is connected by means of the suction line 61 and here the section 16a of the return line 16, upstream of the overflow valve 18, to the outflow-side region 11a 'of the suction chamber 11'. Since this connection has also been made in this exemplary embodiment between the inlet valve 17 and the overflow valve 18, here too, as in the examples described above, with the switching valve 27 open and the volume of the spring chamber 23 increasing, the suction chamber 11 'is placed under negative pressure, so that the injection pump 10 can no longer deliver and the associated internal combustion engine "dies", ie stop.

Die in jedem der Ausführungsbeispiele verwirklichte Abschaltvorrichtung führt zu einem sehr schnellen Abstellen, wenn die Kraftstofförderpumpe 12 elektromotorisch angetrieben ist und im Abschaltfall auch die Förderpumpe stehenbleibt. Die beschriebenen Ausführungsbeispiele sind aber auch bei Vorhandensein einer mechanisch, z. B. von der Nockenwelle der Einspritzpumpe 10 angetriebenen Kraftstofförderpumpe vorteilhafterweise einsetzbar, da durch das Schaltventil 27 die Förderleitung 15 kurzgeschlossen wird, die Förderung in den Saugraum 11, 11' damit unterbleibt und das sich vergrößernde Volumen der Federkammer 23 für den zum Abstellen erforderlichen Unterdruck im Saugraum sorgt, so daß auch hier ein schnelles Abstellen erfolgt.The shutdown device implemented in each of the exemplary embodiments leads to very rapid shutdown when the fuel feed pump 12 is driven by an electric motor and the feed pump also stops in the event of a shutdown. The described embodiments are also in the presence of a mechanical, for. B. fuel pump driven by the camshaft of the injection pump 10 can advantageously be used since the delivery line 15 is short-circuited by the switching valve 27, the delivery into the suction chamber 11, 11 'thus stops and the increasing volume of the spring chamber 23 for the vacuum required for switching off Suction chamber ensures that quick parking is also possible here.

Die Erfindung umfaßt selbstverständlich auch Kombinationen der in den vier Ausführungsbeispielen beschriebenen Vorrichtung. So kann in einem Sonderfall die Federkammer 23 sowohl an den Eingang als auch an den Ausgang des Saugraums 11, 11' angeschlossen werden, wenn dies bei entsprechenden Großpumpen erforderlich ist. Ebenso ist ein mittiger Anschluß an den Saugraum denkbar, wenn ein entsprechender Anschluß vorgesehen wird und diese Maßnahme zu einem schnelleren Abstellen führt.The invention naturally also includes combinations of the device described in the four exemplary embodiments. Thus, in a special case, the spring chamber 23 can both the input as well as to the output of the suction chamber 11, 11 'are connected if this is necessary with corresponding large pumps. A central connection to the suction space is also conceivable if a corresponding connection is provided and this measure leads to faster shutdown.

Claims (11)

1. Fuel-injection device for internal-combustion engines, especially diesel internal-combustion engines, with a fuel-injection pump (10) which from a suction space (11) supplies injection nozzles (43) with fuel under injection pressure, with a fuel feed pump (12) which fills the suction space (11) of the fuel-injection pump (10) from a fuel tank (13)with fuel underfeed pressure, with an overflow valve (18) which is arranged between the suction space (11) and a return line leading to the fuel tank (13) and which limits the suction-space pressure, and with a fuel-injection cutoff device (19) which is arranged between the feed pump (12) and the injection pump (10) and which, when activated, connects an additional storage volume to the suction space (11) in order to reduce the suction-space pressure, characterized in that the cutoff device (19) has an inflow valve (17; 17') inserted into the inflow from the feed pump (12) into the suction space (11; 11') and opening towards the suction space (11; 11'1, furthermore a spring accumulator (20) which can be tensioned by means of the feed pressure and of which the storage chamber (22) is connected to the outlet of the feed pump (12) and the spring chamber (23) is connected directly to the suction space (11; 11') of the injection pump (10), and finally an electromagnetically actuated switch valve (27) which is arranged in a bypass (26) connecting the outlet of the feed pump (12) to the fuel tank (13) and which normally shuts off the bypass (26) and opens the latter when the cutoff device (19) is activated.
2. Device according to Claim 1, characterised in that the switch valve (27) is designed as a 2/2-way solenoid valve which opens in the non-energised state.
3. Device according to Claim 1 or 2, characterized in that the spring accumulator (20) has a diaphragm (21) which is loaded by a compression spring (24) and which separates the storage chamber (22) from the spring chamber (23) in a liquid-tight manner.
4. Device according to one of Claims 1 to 3, characterized in that, for tensioning the spring accumuator (20), the inflow valve (17; 17') inserted between the feed pump (12) and suction space (11; 11') has an opening pressure which is calculated as at least equal to the tensioning pressure of the spring accumulator (20).
5. Device according to Claim 4, characterized in that the spring chamber (23) of the spring accumulator (20) is connected to the inlet for the suction space (11) downstream of the inflow valve (17), and in that the inflow valve (17) is connected to the inlet and outlet of the spring accumulator (20) in parallel with the latter.
6. Device according to Claim 4, characterized in that the spring chamber (23) of the spring accumulator (20) is connected to the inlet of the suction space (11) downstream of the inflow valve (17; 17'), and in that the inflow valve (17; 17') is integrated in the spring accumulator (20).
7. Device according to Claim 6, characterized in that the diaphragm (21) has a throughflow orifice (36), in that the inflow valve (17) is designed as a non-return valve and is arranged in the spring chamber (23), and in that the valve member (38) of the inflow valve (17) interacts with a valve seat (37) surrounding the throughflow orifice (36).
8. Device according to Claim 6, characterized in that the inflow valve (17') is designed as a slide valve, the control slide (51) of which is connected to the diaphragm (21) and, after the tensioning of the spring accumulator (20) opens a connection between the storage chamber (22) and spring chamber (23) of the spring accumulator (20).
9. Device according to Claim 8, characterized in that the inflow valve (17') has a guide sleeve (52), arranged fixedly in the spring chamber (23) and having at least one radial bore (54, 55), and a control slide (51) which is axially displaceable in the guide sleeve (52) and which is fastened to the diaphragm (21) of the spring accumulator (20) and carries an annular control groove (56) which is connected to the storage chamber (22) of the spring accumulator (20) via bores (57, 58) and a throughflow orifice (59) in the diaphragm (21), and in that the radial bore (54, 55) in the guide sleeve (52) and the control groove (56) in the control slide (51) are so arranged in relation to one another that they are connected to one another after a predetermined displacement travel of the control slide (51) connected to the diaphragm (21).
10. Device according to one of Claims 1 to 9, characterized in that the overflow valve (18) located in the return line (16) and the switch valve (27) are combined to form a constructional unit (34) and the outlet of the switch valve (27) is connected to the outlet of the overflow valve (18).
11. Device according to one of Claims 1 to 4, characterized in thatthe spring chamber (23) of the spring accumulator (20) is connected, upstream of the overflow valve (18), to the region (11a') of the suction space (11') located on the flow-off side.
EP87904028A 1986-07-05 1987-06-25 Fuel injection device for internal combustion engines Expired - Lifetime EP0303624B1 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE3622626 1986-07-05
DE3622626 1986-07-05
DE19873720067 DE3720067A1 (en) 1986-07-05 1987-06-16 FUEL INJECTION DEVICE FOR INTERNAL COMBUSTION ENGINES
DE3720067 1987-06-16

Publications (2)

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EP0303624A1 EP0303624A1 (en) 1989-02-22
EP0303624B1 true EP0303624B1 (en) 1990-05-30

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EP87904028A Expired - Lifetime EP0303624B1 (en) 1986-07-05 1987-06-25 Fuel injection device for internal combustion engines

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US (1) US4957084A (en)
EP (1) EP0303624B1 (en)
JP (1) JPH01503160A (en)
DE (2) DE3720067A1 (en)
WO (1) WO1988000292A1 (en)

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Also Published As

Publication number Publication date
DE3720067A1 (en) 1988-01-07
WO1988000292A1 (en) 1988-01-14
DE3762986D1 (en) 1990-07-05
JPH01503160A (en) 1989-10-26
US4957084A (en) 1990-09-18
EP0303624A1 (en) 1989-02-22

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