EP1321663A2 - Fuel injection device for an internal combustion engine - Google Patents

Fuel injection device for an internal combustion engine Download PDF

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Publication number
EP1321663A2
EP1321663A2 EP02024857A EP02024857A EP1321663A2 EP 1321663 A2 EP1321663 A2 EP 1321663A2 EP 02024857 A EP02024857 A EP 02024857A EP 02024857 A EP02024857 A EP 02024857A EP 1321663 A2 EP1321663 A2 EP 1321663A2
Authority
EP
European Patent Office
Prior art keywords
valve member
fuel
valve
fuel injection
injection device
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.)
Withdrawn
Application number
EP02024857A
Other languages
German (de)
French (fr)
Other versions
EP1321663A3 (en
Inventor
Dietmar Van Der Linden
Achim Koehler
Sascha Ambrock
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1321663A2 publication Critical patent/EP1321663A2/en
Publication of EP1321663A3 publication Critical patent/EP1321663A3/en
Withdrawn legal-status Critical Current

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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
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0017—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means
    • 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
    • F02M53/00—Fuel-injection apparatus characterised by having heating, cooling or thermally-insulating means
    • 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/04—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps
    • F02M59/06—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps with cylinders arranged radially to driving shaft, e.g. in V or star arrangement
    • 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/34—Varying fuel delivery in quantity or timing by throttling of passages to pumping elements or of overflow passages, e.g. throttling by means of a pressure-controlled sliding valve having liquid stop or abutment
    • 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
    • F02M63/0001—Fuel-injection apparatus with specially arranged lubricating system, e.g. by fuel oil
    • 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
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
    • 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
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • 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
    • F02M69/00—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel
    • F02M69/46—Details, component parts or accessories not provided for in, or of interest apart from, the apparatus covered by groups F02M69/02 - F02M69/44
    • F02M69/52—Arrangement of fuel metering devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/60—Fuel-injection apparatus having means for facilitating the starting of engines, e.g. with valves or fuel passages for keeping residual pressure in common rails

Definitions

  • the invention relates to a fuel injection device for an internal combustion engine according to the preamble of claim 1.
  • Such a fuel injection device is known from DE 198 53 103 A1.
  • This fuel injection device has a delivery pump, through which fuel is delivered to a high-pressure pump, the high-pressure pump delivering fuel under high pressure to a storage device.
  • a fuel metering device is provided, which is arranged between the feed pump and the high-pressure pump.
  • the fuel metering device is used to control the amount of fuel delivered to the store by the high-pressure pump depending on the operating parameters of the internal combustion engine.
  • the fuel metering device comprises an actuator in the form of an electromagnet and a control valve actuated by it, which has a slide-shaped valve member which is guided in a cylinder bore of a valve housing and which can be moved by an armature of the electromagnet against a return spring.
  • the valve member In cooperation with an outlet opening of the valve housing, the valve member controls a flow cross-section from the feed pump to the high-pressure pump via its outer jacket depending on the stroke. In a closed position of the valve member, this is with its outer jacket in Cover with the drain opening so that the flow cross section is completely closed.
  • the valve member since the valve member must be displaceable in the cylinder bore of the valve housing, there is a small gap between the outer casing and the cylinder bore through which a leakage amount of fuel can pass and reach the high-pressure pump via the drain opening, even if due to the operating parameters of the internal combustion engine, for example in the Thrust operation, no fuel needs to be pumped by the high pressure pump. Measures are therefore necessary in order to discharge this amount of fuel leakage so that it cannot reach the high-pressure pump. This makes the construction and manufacture of the fuel injection device complex.
  • the fuel injection device according to the invention with the features of claim 1 has the advantage that the high pressure pump can be completely separated from the feed pump by the valve member by means of the sealing surface in cooperation with the valve seat, so that no further measures are required for this and the structure and manufacture the fuel injection device are simplified accordingly.
  • FIG. 1 shows a fuel injection device for an internal combustion engine in a schematic illustration
  • FIG. 2 shows an enlarged illustration of a fuel metering device of the fuel injection device according to a first exemplary embodiment in a first position
  • FIG. 3 shows the fuel metering device in a second position
  • FIG. 4 shows the fuel metering device in a view in the direction of arrow IV in Figure 2 and Figure 5, the fuel metering device according to a second embodiment.
  • FIG. 1 shows a fuel injection device for an internal combustion engine, for example of a motor vehicle.
  • the internal combustion engine is preferably a self-igniting internal combustion engine and has one or more cylinders.
  • the motor vehicle has a fuel reservoir 10 in which fuel is stored for the operation of the internal combustion engine.
  • the fuel injection device has a feed pump 12, through which fuel is delivered from the fuel reservoir 10 to a high-pressure pump 14.
  • the high-pressure pump 14 pumps fuel into a reservoir 16, which can be tubular, for example, or in any other form. Lines 18 lead from memory 16 to arranged on the cylinders of the internal combustion engine Injectors 20 from.
  • An electrical control valve 22 is arranged on each of the injectors 20, through which an opening of the injectors is controlled, in order to thus effect fuel injection by the respective injector 20 or to prevent fuel injection.
  • the control valves 22 are controlled by an electronic control device 23, which determines the point in time and the duration of the fuel injection by the injectors 20 as a function of operating parameters of the internal combustion engine, such as, for example, speed, load, temperature and others.
  • a return for unused fuel leads back from the injectors 20, at least indirectly, for example via a line 24 common to all injectors, into the fuel reservoir 10.
  • a line 26 can also return from the reservoir 16 to the fuel tank 10, in which a pressure relief valve 28 is arranged, in order to prevent an impermissibly high pressure from building up in the reservoir 16.
  • the high pressure pump 14 is mechanically driven by the internal combustion engine and thus proportional to the speed of the internal combustion engine.
  • the feed pump 12 can also be driven mechanically by the internal combustion engine, and a common drive shaft can be provided for the high pressure pump 14 and the feed pump 12.
  • the feed pump 12 may alternatively also have an electric motor drive, for example.
  • the high-pressure pump 14 can be designed as a radial piston pump and has a plurality of, for example three, pump elements 30 arranged at a uniform angular distance from one another, each of which has a pump piston 34 driven in one stroke by a polygon 32 in connection with an eccentric shaft, each of which delimits a pump working space 36.
  • a check valve 38 opening towards the accumulator 16, through which the separation between the pump work spaces 36 and the accumulator 16 takes place during the suction stroke of the pump pistons 34.
  • a check valve 39 which opens towards the pump work rooms 36 and through which the pump work rooms 36 and the feed pump 12 are separated during the delivery stroke of the pump pistons 34.
  • the pump work spaces 36 are connected to the outlet of the feed pump 12 when the check valves 39 are open and are filled with fuel, the pump work spaces 36 being separated from the accumulator 16 by the closed check valves 38 are.
  • the pump working spaces 36 are connected to the accumulator 16 when the check valves 38 are open and are separated from the outlet of the delivery pump 12 by the closed check valves 39.
  • One or more filters are preferably arranged between the feed pump 12 and the fuel reservoir 10.
  • a coarse filter 40 can be provided first, followed by a fine filter 42, whereby the fine filter 42 can additionally have a water separator.
  • a fuel metering device 44 is arranged between the feed pump 12 and the high pressure pump 14.
  • the fuel metering device 44 has a control valve 46 actuated by an electrical actuator 45, for example an electromagnet or a piezo actuator that the flow from the feed pump 12 to the high pressure pump 14 is continuously adjustable.
  • the fuel metering device 44 is also controlled by the control device 23, in such a way that a fuel quantity is supplied to the high-pressure pump 14 by the feed pump 12, which in turn is then pumped under high pressure into the memory 16 by the high-pressure pump 14 in order to have a predetermined value in the memory 16 to maintain pressure dependent on operating parameters of the internal combustion engine.
  • the fuel metering device 44 is shown enlarged according to a first embodiment.
  • the fuel metering device 44 has a valve housing 50, in which a slide-shaped valve member 54 is displaceably guided in a cylinder bore 52.
  • the valve member 54 has at least one recess 56 in its outer jacket, which extends in the direction of the longitudinal axis 55 of the valve member 54 over part of the longitudinal extent and also over part of the circumference of the valve member 54.
  • the recess 56 is explained in more detail below.
  • an outlet opening 58 opening into the cylinder bore 52 is formed, with which the recess 56 of the valve member 54 cooperates to control the size of a flow cross section.
  • the drain opening 58 is connected to the suction side of the high pressure pump 14.
  • the recess 56 extends in the longitudinal direction on the valve member 54 up to an end face of the valve member 54.
  • the valve member 54 has a sealing surface 60 which, for example, as shown in FIG. 2, can be at least approximately tapered in the shape of a truncated cone.
  • the valve member 54 tapers in the shape of a truncated cone towards its end.
  • the sealing surface 60 can alternatively, for example, at least approximately spherical segment-shaped.
  • an inlet opening 62 opens, which is connected to the outlet of the feed pump 12.
  • a valve seat 64 is formed in the valve housing 50, with which the valve member 54 cooperates with its sealing surface 60 to close the inlet opening 62.
  • the valve seat 64 can also be at least approximately frustoconical, the cone angles of the sealing surface 60 and the valve seat 64 being the same or different.
  • the valve seat 64 widens towards the valve member 54.
  • the cone angle of the valve seat 64 is preferably greater than the cone angle of the sealing surface 60, so that the valve member 54 only comes into contact with the valve seat 64 with the edge of its sealing surface 60 at the end of the valve member 54.
  • An armature 66 of the electromagnet 45 engages on the valve member 54 on the side facing away from the valve seat 64, by means of which the valve member 54 can be displaced toward the valve seat 64 when the electromagnet 45 is energized.
  • a return spring 68 acts on the valve member 54.
  • the function of the fuel metering device 44 is explained below. If no fuel is to be conveyed into the accumulator 16 by the high-pressure pump 14, the electromagnet 45 is energized by the control device 23 with a high current, so that the valve member 54 against the force of the return spring 68 with its sealing surface 60 in contact with the valve seat 64 is brought as shown in Figure 2.
  • the inlet opening 62 is completely closed by the valve member 54, even if pressure is generated by the feed pump 12.
  • the recess 56 of the The valve member 54 is not in overlap with the drain opening 58, but the valve member 54 with its full cylindrical cross section is in overlap with the drain opening 58.
  • the end of the recess 56 is also in the direction of the longitudinal axis 55 of the valve member 54 at a distance h from the edge of the drain opening 58 arranged.
  • the electromagnet 45 is energized by the control device 23 with a lower current intensity, so that the valve member 54 is caused by the return spring 68 to move in the opening direction 70 and with its sealing surface 60 lifts off the valve seat 64 and releases the inlet opening 62.
  • the recess 56 is not yet in register with the drain opening 58, so that no flow cross-section is released, but only a small amount of fuel leakage between the outer jacket of the valve member 54 and the cylinder bore 52 can pass through and reach the high pressure pump 14.
  • valve member 54 When the valve member 54 is lifted with its sealing surface 60 from the valve seat 64, the space delimited between the valve member 54 and the end wall 53 in the cylinder bore 52 is filled with fuel under the pressure generated by the feed pump 12. Only when the idle stroke h of the valve member 54 has been passed through does its recess 56 overlap with the drain opening 58 and releases a flow cross-section, as shown in FIG. 3. With this configuration, a separation between the function of completely closing the inlet opening 62 by the valve member 54 when no fuel is to be conveyed by the high-pressure pump 14 and the function of controlling the flow cross section by the valve member 54 is achieved.
  • the recess 56 on the valve member 54 widens in such a way that an increasingly larger flow cross-section is released from the cylinder bore 52 into the outlet opening 58 when the valve member 54 moves in its opening direction 70.
  • the region 57 of the recess 56 which interacts with the drain opening 58 can, for example, be trapezoidal, as shown in FIG. 4, the region 57 widening toward the end of the valve member 54 which has the sealing surface 60.
  • the region 57, up to the end of the valve member 54 has a recess which is narrower than the region 57 and runs approximately parallel to the longitudinal axis 55 of the valve member 54.
  • Activation of the electromagnet 45 by the control device 23 with different current strengths can be achieved, for example, by actuating the electromagnet 45 in a pulse-width-modulated manner, the current strength and thus the size of the released flow cross-section being dependent on the pulse width.
  • the metering device 144 is shown according to a second embodiment.
  • the metering device 144 has the valve housing 150 with the cylinder bore 152, in which the valve member 154 is displaceably guided.
  • the valve member 154 is pot-shaped and has a closed end toward the armature 66 of the electromagnet 45 with a base 172 against which the armature 66 abuts.
  • the valve member 154 has at least one, preferably a plurality of openings 156 distributed over its circumference.
  • the at least one drain opening 158 is formed in the valve housing 150, with a plurality of openings 158 distributed over the circumference of the valve housing 150 being provided, with which the openings 156 of the valve member 154 cooperate to control the size of the flow cross section.
  • a component 174 is sealingly inserted into the cylinder bore 152 from the side facing away from the electromagnet 45 and has a connection piece 176 projecting into the valve member 154 from its open end.
  • a channel 177 runs as a connection to the outlet of the feed pump 12 and the channel 177 opens into one Inlet opening 162 at the end of the nozzle 176 in the valve member 154.
  • the inlet opening 162 is surrounded by a valve seat 164 at the front end of the nozzle 176.
  • a separate sealing element 178 which has a sealing surface and which is designed, for example, as a ball.
  • the ball 178 can be held in a carrier 180 which is inserted into the cylinder bore 152, in particular pressed into it.
  • the ball 178 protrudes with a part of its circumference from the carrier 180 to the nozzle 176.
  • this rests with the ball 178 on the valve seat 164 at the front end of the connector 176 and closes the inlet opening 162.
  • the openings 156 of the valve member 154 only overlap after an empty stroke h has been passed, as in the first exemplary embodiment with the drain openings 158 of the valve housing 150 and then control the size of the flow area.

Abstract

Fuel injection device for an internal combustion engine comprises a valve element (54) with a sealing surface (60) which interacts with a valve seat (64) to control an inlet opening (62) leading from a feed pump into the cylinder bore (52) and which completely closes the inlet opening in a position in which it lies with the sealing surface on the valve seat. <??>Preferred Features: The valve element does not release with its outer casing a through flow cross-section during a return stroke (h) away from the valve seat. After the empty stroke the outer casing (56) releases an increasingly greater stroke-dependent through flow cross-section. The sealing surface of the valve element tapers conically toward the end of the valve element.

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine nach der Gattung des Anspruchs 1.The invention relates to a fuel injection device for an internal combustion engine according to the preamble of claim 1.

Eine solche Kraftstoffeinspritzeinrichtung ist durch die DE 198 53 103 A1 bekannt. Diese Kraftstoffeinspritzeinrichtung weist eine Förderpumpe auf, durch die Kraftstoff zu einer Hochdruckpumpe gefördert wird, wobei die Hochdruckpumpe Kraftstoff unter Hochdruck in einen Speicher fördert. Weiterhin ist eine Kraftstoffzumeßeinrichtung vorgesehen, die zwischen der Förderpumpe und der Hochdruckpumpe angeordnet ist. Die Kraftstoffzumeßeinrichtung dient zur Steuerung der durch die Hochdruckpumpe in den Speicher geförderten Kraftstoffmenge abhängig von Betriebsparametern der Brennkraftmaschine. Die Kraftstoffzumeßeinrichtung umfaßt einen Aktor in Form eines Elektromagneten und ein durch diesen betätigtes Regelventil, das ein in einer Zylinderbohrung eines Ventilgehäuses geführtes schieberförmiges Ventilglied aufweist, das durch einen Anker des Elektromagneten gegen eine Rückstellfeder bewegbar ist. Das Ventilglied steuert in Zusammenwirkung mit einer Ablauföffnung des Ventilgehäuses über seinen Außenmantel hubabhängig einen Durchflußquerschnitt von der Förderpumpe zur Hochdruckpumpe. In einer Schließstellung des Ventilglieds befindet sich dieses mit seinem Außenmantel in Überdeckung mit der Ablauföffnung, so daß der Durchflußquerschnitt vollständig verschlossen wird. Da das Ventilglied in der Zylinderbohrung des Ventilgehäuses jedoch verschiebbar sein muß ist zwischen dessen Außenmantel und der Zylinderbohrung ein geringer Spalt vorhanden, durch den eine Leckmenge an Kraftstoff hindurchtreten und über die Ablauföffnung zur Hochdruckpumpe gelangen kann, auch wenn aufgrund der Betriebsparameter der Brennkraftmaschine, beispielsweise im Schubbetrieb, durch die Hochdruckpumpe kein Kraftstoff gefördert zu werden braucht. Es sind daher Maßnahmen erforderlich, um diese Leckmenge an Kraftstoff abzuführen, so daß diese nicht zur Hochdruckpumpe gelangen kann. Hierdurch wird der Aufbau und die Fertigung der Kraftstoffeinspritzeinrichtung aufwendig.Such a fuel injection device is known from DE 198 53 103 A1. This fuel injection device has a delivery pump, through which fuel is delivered to a high-pressure pump, the high-pressure pump delivering fuel under high pressure to a storage device. Furthermore, a fuel metering device is provided, which is arranged between the feed pump and the high-pressure pump. The fuel metering device is used to control the amount of fuel delivered to the store by the high-pressure pump depending on the operating parameters of the internal combustion engine. The fuel metering device comprises an actuator in the form of an electromagnet and a control valve actuated by it, which has a slide-shaped valve member which is guided in a cylinder bore of a valve housing and which can be moved by an armature of the electromagnet against a return spring. In cooperation with an outlet opening of the valve housing, the valve member controls a flow cross-section from the feed pump to the high-pressure pump via its outer jacket depending on the stroke. In a closed position of the valve member, this is with its outer jacket in Cover with the drain opening so that the flow cross section is completely closed. However, since the valve member must be displaceable in the cylinder bore of the valve housing, there is a small gap between the outer casing and the cylinder bore through which a leakage amount of fuel can pass and reach the high-pressure pump via the drain opening, even if due to the operating parameters of the internal combustion engine, for example in the Thrust operation, no fuel needs to be pumped by the high pressure pump. Measures are therefore necessary in order to discharge this amount of fuel leakage so that it cannot reach the high-pressure pump. This makes the construction and manufacture of the fuel injection device complex.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Kraftstoffeinspritzeinrichtung mit den Merkmalen gemäß Anspruch 1 hat demgegenüber den Vorteil, daß durch das Ventilglied mittels der Dichtfläche in Zusammenwirkung mit dem Ventilsitz die Hochdruckpumpe vollständig von der Förderpumpe getrennt werden kann, so daß hierfür keine weiteren Maßnahmen erforderlich sind und der Aufbau und die Fertigung der Kraftstoffeinspritzeinrichtung entsprechend vereinfacht sind.The fuel injection device according to the invention with the features of claim 1 has the advantage that the high pressure pump can be completely separated from the feed pump by the valve member by means of the sealing surface in cooperation with the valve seat, so that no further measures are required for this and the structure and manufacture the fuel injection device are simplified accordingly.

In den abhängigen Ansprüchen sind vorteilhafte Ausgestaltungen und Weiterbildungen der erfindungsgemäßen Kraftstoffeinspritzeinrichtung angegeben. Durch die Ausbildung gemäß Anspruch 2 ist eine Trennung zwischen der vollständigen Abdichtung mittels der Dichtfläche und der Steuerung der Größe des Durchflußquerschnitts über den Außenmantel des Ventilglieds erreicht. Durch die Merkmale der Ansprüche 3 bis 5 wird eine sichere Abdichtung durch die Dichtfläche des Ventilglieds in Zusammenwirkung mit dem Ventilsitz ermöglicht.Advantageous refinements and developments of the fuel injection device according to the invention are specified in the dependent claims. Due to the design according to claim 2, a separation between the complete seal by means of the sealing surface and the control of the size of the flow cross section via the outer jacket of the valve member is achieved. The features of claims 3 to 5 provide a secure seal through the Sealing surface of the valve member in cooperation with the valve seat allows.

Zeichnungdrawing

Zwei Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 eine Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine in schematischer Darstellung, Figur 2 in vergrößerter Darstellung eine Kraftstoffzumeßeinrichtung der Kraftstoffeinspritzeinrichtung gemäß einem ersten Ausführungsbeispiel in einer ersten Stellung, Figur 3 die Kraftstoffzumeßeinrichtung in einer zweiten Stellung, Figur 4 die Kraftstoffzumeßeinrichtung in einer Ansicht in Pfeilrichtung IV in Figur 2 und Figur 5 die Kraftstoffzumeßeinrichtung gemäß einem zweiten Ausführungsbeispiel.Two embodiments of the invention are shown in the drawing and explained in more detail in the following description. 1 shows a fuel injection device for an internal combustion engine in a schematic illustration, FIG. 2 shows an enlarged illustration of a fuel metering device of the fuel injection device according to a first exemplary embodiment in a first position, FIG. 3 shows the fuel metering device in a second position, and FIG. 4 shows the fuel metering device in a view in the direction of arrow IV in Figure 2 and Figure 5, the fuel metering device according to a second embodiment.

Beschreibung der AusführungsbeispieleDescription of the embodiments

In Figur 1 ist eine Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine beispielsweise eines Kraftfahrzeugs dargestellt. Die Brennkraftmaschine ist vorzugsweise eine selbstzündende Brennkraftmaschine und weist einen oder mehrere Zylinder auf. Das Kraftfahrzeug weist einen Kraftstoffvorratsbehälter 10 auf, in dem Kraftstoff für den Betrieb der Brennkraftmaschine bevorratet ist. Die Kraftstoffeinspritzeinrichtung weist eine Förderpumpe 12 auf, durch die Kraftstoff aus dem Kraftstoffvorratsbehälter 10 zu einer Hochdruckpumpe 14 gefördert wird. Die Hochdruckpumpe 14 fördert Kraftstoff in einen Speicher 16, der beispielsweise rohrförmig oder in beliebiger anderer Form ausgebildet sein kann. Vom Speicher 16 führen Leitungen 18 zu an den Zylindern der Brennkraftmaschine angeordneten Injektoren 20 ab. An den Injektoren 20 ist jeweils ein elektrisches Steuerventil 22 angeordnet, durch das eine Öffnung der Injektoren gesteuert wird, um so eine Kraftstoffeinspritzung durch den jeweiligen Injektor 20 zu bewirken oder eine Kraftstoffeinspritzung zu verhindern. Die Steuerventile 22 werden durch eine elektronische Steuereinrichtung 23 angesteuert, durch die in Abhängigkeit von Betriebsparametern der Brennkraftmaschine, wie beispielsweise Drehzahl, Last, Temperatur und weiteren, der Zeitpunkt und die Dauer der Kraftstoffeinspritzung durch die Injektoren 20 bestimmt wird. Von den Injektoren 20 führt ein Rücklauf für nicht verbrauchten Kraftstoff zumindest mittelbar beispielsweise über eine für alle Injektoren gemeinsame Leitung 24 in den Kraftstoffvorratsbehälter 10 zurück. Vom Speicher 16 kann ebenfalls eine Leitung 26 zum Kraftstoffvorratsbehälter 10 zurückführen, in der ein Druckbegrenzungsventil 28 angeordnet ist, um zu verhindern, daß sich im Speicher 16 ein unzulässig hoher Druck aufbaut.FIG. 1 shows a fuel injection device for an internal combustion engine, for example of a motor vehicle. The internal combustion engine is preferably a self-igniting internal combustion engine and has one or more cylinders. The motor vehicle has a fuel reservoir 10 in which fuel is stored for the operation of the internal combustion engine. The fuel injection device has a feed pump 12, through which fuel is delivered from the fuel reservoir 10 to a high-pressure pump 14. The high-pressure pump 14 pumps fuel into a reservoir 16, which can be tubular, for example, or in any other form. Lines 18 lead from memory 16 to arranged on the cylinders of the internal combustion engine Injectors 20 from. An electrical control valve 22 is arranged on each of the injectors 20, through which an opening of the injectors is controlled, in order to thus effect fuel injection by the respective injector 20 or to prevent fuel injection. The control valves 22 are controlled by an electronic control device 23, which determines the point in time and the duration of the fuel injection by the injectors 20 as a function of operating parameters of the internal combustion engine, such as, for example, speed, load, temperature and others. A return for unused fuel leads back from the injectors 20, at least indirectly, for example via a line 24 common to all injectors, into the fuel reservoir 10. A line 26 can also return from the reservoir 16 to the fuel tank 10, in which a pressure relief valve 28 is arranged, in order to prevent an impermissibly high pressure from building up in the reservoir 16.

Die Hochdruckpumpe 14 wird mechanisch durch die Brennkraftmaschine und damit proportional zur Drehzahl der Brennkraftmaschine angetrieben. Die Förderpumpe 12 kann ebenfalls mechanisch durch die Brennkraftmaschine angetrieben werden, wobei für die Hochdruckpumpe 14 und die Förderpumpe 12 eine gemeinsame Antriebswelle vorgesehen sein kann. Die Förderpumpe 12 kann alternativ auch beispielsweise einen elektromotorischen Antrieb aufweisen.The high pressure pump 14 is mechanically driven by the internal combustion engine and thus proportional to the speed of the internal combustion engine. The feed pump 12 can also be driven mechanically by the internal combustion engine, and a common drive shaft can be provided for the high pressure pump 14 and the feed pump 12. The feed pump 12 may alternatively also have an electric motor drive, for example.

Die Hochdruckpumpe 14 kann als Radialkolbenpumpe ausgebildet sein und weist mehrere, beispielsweise drei mit gleichmäßigem Winkelabstand voneinander angeordnete Pumpenelemente 30 auf, die jeweils einen durch einen Polygon 32 in Verbindung mit einer Exzenterwelle in einer Hubbewegung angetriebenen Pumpenkolben 34 aufweisen, die jeweils einen Pumpenarbeitsraum 36 begrenzen. In den Verbindungen der Pumpenarbeitsräume 36 mit dem Speicher 16 ist jeweils ein zum Speicher 16 hin öffnendes Rückschlagventil 38 angeordnet, durch das die Trennung zwischen den Pumpenarbeitsräumen 36 und dem Speicher 16 beim Saughub der Pumpenkolben 34 erfolgt. In den Verbindungen der Pumpenarbeitsräume 36 mit der Förderpumpe 12 ist jeweils ein zu den Pumpenarbeitsräumen 36 hin öffnendes Rückschlagventil 39 angeordnet, durch das die Trennung zwischen den Pumpenarbeitsräumen 36 und der Förderpumpe 12 beim Förderhub der Pumpenkolben 34 erfolgt. Während eines jeweiligen Saughubs der Pumpenkolben 34, wenn diese sich radial nach innen bewegen, sind die Pumpenarbeitsräume 36 bei geöffneten Rückschlagventilen 39 mit dem Auslaß der Förderpumpe 12 verbunden und werden mit Kraftstoff befüllt, wobei die Pumpenarbeitsräume 36 durch die geschlossenen Rückschlagventile 38 vom Speicher 16 getrennt sind. Während eines jeweiligen Förderhubs der Pumpenkolben 34, wenn diese sich radial nach außen bewegen, sind die Pumpenarbeitsräume 36 bei geöffneten Rückschlagventilen 38 mit dem Speicher 16 verbunden und durch die geschlossenen Rückschlagventile 39 vom Auslaß der Förderpumpe 12 getrennt.The high-pressure pump 14 can be designed as a radial piston pump and has a plurality of, for example three, pump elements 30 arranged at a uniform angular distance from one another, each of which has a pump piston 34 driven in one stroke by a polygon 32 in connection with an eccentric shaft, each of which delimits a pump working space 36. In the Connections of the pump work spaces 36 to the accumulator 16 are each arranged a check valve 38 opening towards the accumulator 16, through which the separation between the pump work spaces 36 and the accumulator 16 takes place during the suction stroke of the pump pistons 34. In the connections between the pump work rooms 36 and the feed pump 12 there is a check valve 39 which opens towards the pump work rooms 36 and through which the pump work rooms 36 and the feed pump 12 are separated during the delivery stroke of the pump pistons 34. During a respective suction stroke of the pump pistons 34, when they move radially inward, the pump work spaces 36 are connected to the outlet of the feed pump 12 when the check valves 39 are open and are filled with fuel, the pump work spaces 36 being separated from the accumulator 16 by the closed check valves 38 are. During a respective delivery stroke of the pump pistons 34, when these move radially outward, the pump working spaces 36 are connected to the accumulator 16 when the check valves 38 are open and are separated from the outlet of the delivery pump 12 by the closed check valves 39.

Zwischen der Förderpumpe 12 und dem Kraftstoffvorratsbehälter 10 sind vorzugsweise ein oder mehrere Filter angeordnet. Es kann beispielsweise ausgehend vom Kraftstoffvorratsbehälter 10 zunächst ein Grobfilter 40 und diesem nachgeordnet ein Feinfilter 42 vorgesehen sein, wobei der Feinfilter 42 zusätzlich einen Wasserabscheider aufweisen kann.One or more filters are preferably arranged between the feed pump 12 and the fuel reservoir 10. For example, starting from the fuel reservoir 10, a coarse filter 40 can be provided first, followed by a fine filter 42, whereby the fine filter 42 can additionally have a water separator.

Zwischen der Förderpumpe 12 und der Hochdruckpumpe 14 ist eine Kraftstoffzumeßeinrichtung 44 angeordnet. Die Kraftstoffzumeßeinrichtung 44 weist ein durch einen elektrischen Aktor 45, beispielsweise einen Elektromagneten oder einen Piezoaktor, betätigtes Regelventil 46 auf, durch das der Durchfluß von der Förderpumpe 12 zur Hochdruckpumpe 14 kontinuierlich verstellbar ist. Die Kraftstoffzumeßeinrichtung 44 wird ebenfalls durch die Steuereinrichtung 23 angesteuert, in der Weise, daß durch die Förderpumpe 12 eine Kraftstoffmenge der Hochdruckpumpe 14 zugeführt wird, die dann wiederum durch die Hochdruckpumpe 14 unter Hochdruck in den Speicher 16 gefördert wird, um im Speicher 16 einen vorgegebenen, von Betriebsparametern der Brennkraftmaschine abhängigen Druck aufrechtzuerhalten.A fuel metering device 44 is arranged between the feed pump 12 and the high pressure pump 14. The fuel metering device 44 has a control valve 46 actuated by an electrical actuator 45, for example an electromagnet or a piezo actuator that the flow from the feed pump 12 to the high pressure pump 14 is continuously adjustable. The fuel metering device 44 is also controlled by the control device 23, in such a way that a fuel quantity is supplied to the high-pressure pump 14 by the feed pump 12, which in turn is then pumped under high pressure into the memory 16 by the high-pressure pump 14 in order to have a predetermined value in the memory 16 to maintain pressure dependent on operating parameters of the internal combustion engine.

In den Figuren 2 bis 4 ist die Kraftstoffzumeßeinrichtung 44 vergrößert gemäß einem ersten Ausführungsbeispiel dargestellt. Die Kraftstoffzumeßeinrichtung 44 weist als Teil des Regelventils 46 ein Ventilgehäuse 50 auf, in dem in einer Zylinderbohrung 52 ein schieberförmiges Ventilglied 54 verschiebbar geführt ist. Das Ventilglied 54 weist in seinem Außenmantel wenigstens eine Ausnehmung 56 auf, die sich in Richtung der Längsachse 55 des Ventilglieds 54 über einen Teil der Längserstreckung und außerdem über einen Teil des Umfangs des Ventilglieds 54 erstreckt. Die Ausnehmung 56 wird nachfolgend noch näher erläutert. Im Ventilgehäuse 50 ist eine in die Zylinderbohrung 52 mündende Ablauföffnung 58 ausgebildet, mit der die Ausnehmung 56 des Ventilglieds 54 zur Steuerung der Größe eines Durchflußquerschnitts zusammenwirkt. Die Ablauföffnung 58 ist mit der Saugseite der Hochdruckpumpe 14 verbunden.2 to 4, the fuel metering device 44 is shown enlarged according to a first embodiment. As part of the control valve 46, the fuel metering device 44 has a valve housing 50, in which a slide-shaped valve member 54 is displaceably guided in a cylinder bore 52. The valve member 54 has at least one recess 56 in its outer jacket, which extends in the direction of the longitudinal axis 55 of the valve member 54 over part of the longitudinal extent and also over part of the circumference of the valve member 54. The recess 56 is explained in more detail below. In the valve housing 50, an outlet opening 58 opening into the cylinder bore 52 is formed, with which the recess 56 of the valve member 54 cooperates to control the size of a flow cross section. The drain opening 58 is connected to the suction side of the high pressure pump 14.

Die Ausnehmung 56 reicht am Ventilglied 54 in Längsrichtung bis zu einer Stirnseite des Ventilglieds 54. An dieser Stirnseite weist das Ventilglied 54 eine Dichtfläche 60 auf, die beispielsweise wie in Figur 2 dargestellt zumindest annähernd kegelstumpfförmig verjüngend ausgebildet sein kann. Das Ventilglied 54 verjüngt sich dabei kegelstumpförmig zu seinem Ende hin. Die Dichtfläche 60 kann alternativ auch beispielsweise zumindest annähernd kugelsegmentförmig ausgebildet sein. In der der Dichtfläche 60 des Ventilglieds 54 gegenüberliegenden Stirnwand 53 der Zylinderbohrung 52 mündet eine Zulauföffnung 62, die mit dem Auslaß der Förderpumpe 12 verbunden ist. Die Zulauföffnung 62 umgebend ist im Ventilgehäuse 50 ein Ventilsitz 64 ausgebildet, mit dem das Ventilglied 54 mit seiner Dichtfläche 60 zum Verschließen der Zulauföffnung 62 zusammenwirkt. Der Ventilsitz 64 kann ebenfalls zumindest annähernd kegelstumpfförmig ausgebildet sein, wobei die Kegelwinkel der Dichtfläche 60 und des Ventilsitzes 64 gleich oder unterschiedlich sein können. Der Ventilsitz 64 erweitert sich dabei zum Ventilglied 54 hin. Vorzugsweise ist der Kegelwinkel des Ventilsitzes 64 größer als der Kegelwinkel der Dichtfläche 60, so daß das Ventilglied 54 nur mit der Kante seiner Dichtfläche 60 am Ende des Ventilglieds 54 am Ventilsitz 64 zur Anlage kommt.The recess 56 extends in the longitudinal direction on the valve member 54 up to an end face of the valve member 54. On this end face, the valve member 54 has a sealing surface 60 which, for example, as shown in FIG. 2, can be at least approximately tapered in the shape of a truncated cone. The valve member 54 tapers in the shape of a truncated cone towards its end. The sealing surface 60 can alternatively, for example, at least approximately spherical segment-shaped. In the end wall 53 of the cylinder bore 52 opposite the sealing surface 60 of the valve member 54, an inlet opening 62 opens, which is connected to the outlet of the feed pump 12. Surrounding the inlet opening 62, a valve seat 64 is formed in the valve housing 50, with which the valve member 54 cooperates with its sealing surface 60 to close the inlet opening 62. The valve seat 64 can also be at least approximately frustoconical, the cone angles of the sealing surface 60 and the valve seat 64 being the same or different. The valve seat 64 widens towards the valve member 54. The cone angle of the valve seat 64 is preferably greater than the cone angle of the sealing surface 60, so that the valve member 54 only comes into contact with the valve seat 64 with the edge of its sealing surface 60 at the end of the valve member 54.

Am Ventilglied 54 greift auf der dem Ventilsitz 64 abgewandten Seite ein Anker 66 des Elektromagneten 45 an, durch den bei einer Bestromung des Elektromagneten 45 das Ventilglied 54 zum Ventilsitz 64 hin verschiebbar ist. Auf der dem Anker 66 gegenüberliegenden Seite greift am Ventilglied 54 eine Rückstellfeder 68 an. Nachfolgend wird die Funktion der Kraftstoffzumeßeinrichtung 44 erläutert. Wenn durch die Hochdruckpumpe 14 kein Kraftstoff in den Speicher 16 gefördert werden soll, so wird der Elektromagnet 45 durch die Steuereinrichtung 23 mit einer hohen Stromstärke bestromt, so daß das Ventilglied 54 gegen die Kraft der Rückstellfeder 68 mit seiner Dichtfläche 60 in Anlage am Ventilsitz 64 gebracht wird wie dies in Figur 2 dargestellt ist. In dieser Schließstellung wird durch das Ventilglied 54 die Zulauföffnung 62 vollständig geschlossen, auch wenn durch die Förderpumpe 12 Druck erzeugt wird. In dieser Schließstellung befindet sich die Ausnehmung 56 des Ventilglieds 54 nicht in Überdeckung mit der Ablauföffnung 58 sondern das Ventilglied 54 befindet sich mit seinem vollen zylinderförmigen Querschnitt in Überdeckung mit der Ablauföffnung 58. Das Ende der Ausnehmung 56 ist außerdem in Richtung der Längsachse 55 des Ventilglieds 54 mit einem Abstand h vom Rand der Ablauföffnung 58 angeordnet.An armature 66 of the electromagnet 45 engages on the valve member 54 on the side facing away from the valve seat 64, by means of which the valve member 54 can be displaced toward the valve seat 64 when the electromagnet 45 is energized. On the side opposite the armature 66, a return spring 68 acts on the valve member 54. The function of the fuel metering device 44 is explained below. If no fuel is to be conveyed into the accumulator 16 by the high-pressure pump 14, the electromagnet 45 is energized by the control device 23 with a high current, so that the valve member 54 against the force of the return spring 68 with its sealing surface 60 in contact with the valve seat 64 is brought as shown in Figure 2. In this closed position, the inlet opening 62 is completely closed by the valve member 54, even if pressure is generated by the feed pump 12. In this closed position, the recess 56 of the The valve member 54 is not in overlap with the drain opening 58, but the valve member 54 with its full cylindrical cross section is in overlap with the drain opening 58. The end of the recess 56 is also in the direction of the longitudinal axis 55 of the valve member 54 at a distance h from the edge of the drain opening 58 arranged.

Wenn durch die Hochdruckpumpe 14 eine geringe Kraftstoffmenge in den Speicher 16 gefördert werden soll, so wird der Elektromagnet 45 durch die Steuereinrichtung 23 mit einer geringeren Stromstärke bestromt, so daß sich das Ventilglied 54 bewirkt durch die Rückstellfeder 68 in Öffnungsrichtung 70 bewegt und mit seiner Dichtfläche 60 vom Ventilsitz 64 abhebt und die Zulauföffnung 62 freigibt. Ausgehend von der Schließstellung des Ventilglieds 54 befindet sich dabei über einen Leerhub h des Ventilglieds 54 zunächst dessen Ausnehmung 56 noch nicht in Überdeckung mit der Ablauföffnung 58, so daß noch kein Durchflußquerschnitt freigegeben wird, sondern lediglich eine geringe Leckmenge an Kraftstoff zwischen dem Außenmantel des Ventilglieds 54 und der Zylinderbohrung 52 hindurchtreten kann und zur Hochdruckpumpe 14 gelangen kann. Wenn das Ventilglied 54 mit seiner Dichtfläche 60 vom Ventilsitz 64 abgehoben ist, so füllt sich der zwischen dem Ventilglied 54 und der Stirnwand 53 in der Zylinderbohrung 52 begrenzte Raum mit Kraftstoff unter dem von der Förderpumpe 12 erzeugten Druck. Erst wenn der Leerhub h des Ventilglieds 54 durchfahren ist, so kommt dessen Ausnehmung 56 in Überdeckung mit der Ablauföffnung 58 und gibt einen Durchflußquerschnitt frei wie dies in Figur 3 dargestellt ist. Durch diese Ausbildung wird eine Trennung zwischen der Funktion des vollständigen Verschließens der Zulauföffnung 62 durch das Ventilglied 54, wenn kein Kraftstoff von der Hochdruckpumpe 14 gefördert werden soll, und der Funktion der Steuerung des Durchflußquerschnitts durch das Ventilglied 54 erreicht.If a small amount of fuel is to be conveyed into the accumulator 16 by the high-pressure pump 14, the electromagnet 45 is energized by the control device 23 with a lower current intensity, so that the valve member 54 is caused by the return spring 68 to move in the opening direction 70 and with its sealing surface 60 lifts off the valve seat 64 and releases the inlet opening 62. Starting from the closed position of the valve member 54 there is an idle stroke h of the valve member 54, the recess 56 is not yet in register with the drain opening 58, so that no flow cross-section is released, but only a small amount of fuel leakage between the outer jacket of the valve member 54 and the cylinder bore 52 can pass through and reach the high pressure pump 14. When the valve member 54 is lifted with its sealing surface 60 from the valve seat 64, the space delimited between the valve member 54 and the end wall 53 in the cylinder bore 52 is filled with fuel under the pressure generated by the feed pump 12. Only when the idle stroke h of the valve member 54 has been passed through does its recess 56 overlap with the drain opening 58 and releases a flow cross-section, as shown in FIG. 3. With this configuration, a separation between the function of completely closing the inlet opening 62 by the valve member 54 when no fuel is to be conveyed by the high-pressure pump 14 and the function of controlling the flow cross section by the valve member 54 is achieved.

Es kann vorgesehen sein, daß sich die Ausnehmung 56 am Ventilglied 54 derart verbreitert, daß durch diese bei Bewegung des Ventilglieds 54 in dessen Öffnungsrichtung 70 ein zunehmend größerer Durchflußquerschnitt aus der Zylinderbohrung 52 in die Ablauföffnung 58 freigegeben wird. Der mit der Ablauföffnung 58 zusammenwirkende Bereich 57 der Ausnehmung 56 kann dabei wie in Figur 4 dargestellt beispielsweise trapezförmig ausgebildet sein, wobei sich der Bereich 57 zu dem die Dichtfläche 60 aufweisenden Ende des Ventilglieds 54 hin verbreitert. An den Bereich 57 anschließend bis zum Ende des Ventilglieds 54 ist die Ausnehmung als gegenüber dem Bereich 57 schmälerer Schlitz ausgebildet und verläuft etwa parallel zur Längsachse 55 des Ventilglieds 54. Beim Hub des Ventilglieds 54 in dessen Öffnungsrichtung 70 kommt zunächst der Bereich 57 der Ausnehmung 56 mit seinem schmalen Ende in Überdeckung mit der Ablauföffnung 58, so daß entsprechend ein geringer Durchflußquerschnitt freigegeben wird. Mit zunehmendem Hub des Ventilglieds 54 in dessen Öffnungsrichtung 70 kommt der Bereich 57 mit größerer Breite in Überdeckung mit der Ablauföffnung 58, so daß ein entsprechend größerer Durchflußquerschnitt freigegeben wird. Somit können durch Ansteuerung des Elektromagneten 45 durch die Steuereinrichtung 23 mit unterschiedlicher Stromstärke unterschiedliche Durchflußquerschnitte durch das Ventilglied 54 gesteuert werden, um entsprechend unterschiedliche Saugmengen für die Hochdruckpumpe 14 bereitzustellen.It can be provided that the recess 56 on the valve member 54 widens in such a way that an increasingly larger flow cross-section is released from the cylinder bore 52 into the outlet opening 58 when the valve member 54 moves in its opening direction 70. The region 57 of the recess 56 which interacts with the drain opening 58 can, for example, be trapezoidal, as shown in FIG. 4, the region 57 widening toward the end of the valve member 54 which has the sealing surface 60. The region 57, up to the end of the valve member 54, has a recess which is narrower than the region 57 and runs approximately parallel to the longitudinal axis 55 of the valve member 54. When the valve member 54 is lifted in its opening direction 70, the region 57 of the recess 56 comes first with its narrow end in overlap with the drain opening 58, so that a small flow cross-section is released accordingly. With increasing stroke of the valve member 54 in its opening direction 70, the region 57 with a greater width comes into overlap with the outlet opening 58, so that a correspondingly larger flow cross section is released. Thus, by controlling the electromagnet 45 by the control device 23 with different current strength, different flow cross sections can be controlled by the valve member 54 in order to provide correspondingly different suction quantities for the high pressure pump 14.

Eine Ansteuerung des Elektromagneten 45 durch die Steuereinrichtung 23 mit unterschiedlichen Stromstärken kann beispielsweise erreicht werden, indem der Elektromagnet 45 getaktet pulsweitenmoduliert angesteuert wird, wobei die Stromstärke und damit die Größe des freigegebenen Durchflußquerschnitts abhängig ist von der Pulsweite. Wenn sich das Ventilglied 54 gemäß Figur 2 in seiner Schließstellung befindet, so ist die Saugseite der Hochdruckpumpe 14 vollständig von der Förderpumpe 12 getrennt, so daß auf der Saugseite der Hochdruckpumpe 14 nur ein geringer Druck herrscht. Die Rückschlagventile 39 der Pumpenarbeitsräume 36 der Hochdruckpumpe 14 brauchen daher nur gegenüber einem geringen Druck abzudichten, so daß diese bereits bei einem geringer Druck öffnen können. Hierdurch ergeben sich nur geringe Anforderungen an die Förderpumpe 12, der Erst- und Wiederstart der Brennkraftmaschine wird verbessert und der Wirkungsgrad der Hochdruckpumpe 14 wird verbessert, da die Drosselverluste an den Rückschlagventilen 39 gering sind.Activation of the electromagnet 45 by the control device 23 with different current strengths can be achieved, for example, by actuating the electromagnet 45 in a pulse-width-modulated manner, the current strength and thus the size of the released flow cross-section being dependent on the pulse width. If 2 is in its closed position, the suction side of the high pressure pump 14 is completely separated from the feed pump 12, so that there is only a low pressure on the suction side of the high pressure pump 14. The check valves 39 of the pump work spaces 36 of the high-pressure pump 14 therefore only need to seal against a low pressure, so that they can open at a low pressure. As a result, there are only slight demands on the feed pump 12, the first and restart of the internal combustion engine is improved and the efficiency of the high-pressure pump 14 is improved since the throttle losses at the check valves 39 are low.

In Figur 5 ist die Zumeßeinrichtung 144 gemäß einem zweiten Ausführungsbeispiel dargestellt. Die Zumeßeinrichtung 144 weist das Ventilgehäuse 150 mit der Zylinderbohrung 152 auf, in der das Ventilglied 154 verschiebbar geführt ist. Das Ventilglied 154 ist dabei topfförmig ausgebildet und weist zum Anker 66 des Elektromagneten 45 hin ein geschlossenes Ende mit einem Boden 172 auf, an dem der Anker 66 anliegt. In seinem Mantel weist das Ventilglied 154 wenigstens eine, vorzugsweise mehrere über dessen Umfang verteilte Öffnungen 156 auf. Im Ventilgehäuse 150 ist entsprechend die wenigstens eine Ablauföffnung 158 ausgebildet, wobei vorzugsweise mehrere über den Umfang des Ventilgehäuses 150 verteilte Öffnungen 158 vorgesehen sind, mit der die Öffnungen 156 des Ventilglieds 154 zur Steuerung der Größe des Durchflußquerschnitts zusammenwirken. In die Zylinderbohrung 152 ist von der dem Elektromagneten 45 abgewandten Seite her ein Bauteil 174 dicht eingesetzt, das einen in das Ventilglied 154 von dessen offenem End her hineinragenden Stutzen 176 aufweist. Durch das Bauteil 174 verläuft ein Kanal 177 als Verbindung zum Auslaß der Förderpumpe 12 und der Kanal 177 mündet in einer Zulauföffnung 162 am Ende des Stutzens 176 im Ventilglied 154. Die Zulauföffnung 162 ist von einem Ventilsitz 164 am Stirnende des Stutzens 176 umgeben.In Figure 5, the metering device 144 is shown according to a second embodiment. The metering device 144 has the valve housing 150 with the cylinder bore 152, in which the valve member 154 is displaceably guided. The valve member 154 is pot-shaped and has a closed end toward the armature 66 of the electromagnet 45 with a base 172 against which the armature 66 abuts. In its jacket, the valve member 154 has at least one, preferably a plurality of openings 156 distributed over its circumference. Correspondingly, the at least one drain opening 158 is formed in the valve housing 150, with a plurality of openings 158 distributed over the circumference of the valve housing 150 being provided, with which the openings 156 of the valve member 154 cooperate to control the size of the flow cross section. A component 174 is sealingly inserted into the cylinder bore 152 from the side facing away from the electromagnet 45 and has a connection piece 176 projecting into the valve member 154 from its open end. Through the component 174, a channel 177 runs as a connection to the outlet of the feed pump 12 and the channel 177 opens into one Inlet opening 162 at the end of the nozzle 176 in the valve member 154. The inlet opening 162 is surrounded by a valve seat 164 at the front end of the nozzle 176.

Im Endbereich des Ventilglieds 154 zu dessen Boden 172 hin ist ein separates Dichtelement 178 eingesetzt, das eine Dichtfläche aufweist und das beispielsweise als Kugel ausgebildet ist. Die Kugel 178 kann dabei in einem Träger 180 gehalten sein, der in die Zylinderbohrung 152 eingesetzt, insbesondere in diese eingepresst ist. Die Kugel 178 ragt mit einem Teil ihres Umfangs aus dem Träger 180 heraus zum Stutzen 176 hin. In der Schließstellung des Ventilglieds 154 liegt dieses mit der Kugel 178 am Ventilsitz 164 am Stirnende des Stutzens 176 an und verschließt die Zulauföffnung 162. Ausgehend von dieser Schließstellung kommen die Öffnungen 156 des Ventilglieds 154 wie beim ersten Ausführungsbeispiel erst nach Durchfahren eines Leerhubs h in Überdeckung mit den Ablauföffnungen 158 des Ventilgehäuses 150 und steuern dann die Größe des Durchflußquerschnitts.In the end region of the valve member 154 towards the bottom 172 of a separate sealing element 178 is used, which has a sealing surface and which is designed, for example, as a ball. The ball 178 can be held in a carrier 180 which is inserted into the cylinder bore 152, in particular pressed into it. The ball 178 protrudes with a part of its circumference from the carrier 180 to the nozzle 176. In the closed position of the valve member 154, this rests with the ball 178 on the valve seat 164 at the front end of the connector 176 and closes the inlet opening 162. Starting from this closed position, the openings 156 of the valve member 154 only overlap after an empty stroke h has been passed, as in the first exemplary embodiment with the drain openings 158 of the valve housing 150 and then control the size of the flow area.

Claims (8)

Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine mit einer Förderpumpe (12), durch die Kraftstoff aus einem Kraftstoffvorratsbehälter (10) zur Saugseite einer Hochdruckpumpe (14) gefördert wird, wobei die Hochdruckpumpe (14) abhängig von Betriebsparametern der Brennkraftmaschine Kraftstoff in einen Speicher (16) fördert, mit einer Kraftstoffzumeßeinrichtung (44;144) zur Einstellung der durch die Hochdruckpumpe (14) in den Speicher (16) geförderten Kraftstoffmenge, wobei die Kraftstoffzumeßeinrichtung (44;144) einen Aktor (45) und ein durch diesen betätigtes Regelventil (46) aufweist, wobei das Regelventil (46) ein in einer Zylinderbohrung (52;152) eines Ventilgehäuses (50;150) geführtes schieberförmiges Ventilglied (54;154) aufweist, das durch den Aktor (45) gegen eine Rückstellkraft (68) verschiebbar ist, und wobei das Ventilglied (54;154) mit seinem Außenmantel (56;156) in Zusammenwirkung mit einem Ablauf (58;158) aus der Zylinderbohrung (52;152) einen Durchflußquerschnitt von der Förderpumpe (12) zur Hochdruckpumpe (14) steuert, dadurch gekennzeichnet, daß das Ventilglied (54;154) mit einer Dichtfläche (60;178) mit einem Ventilsitz (64;164) zur Steuerung einer von der Förderpumpe (12) herführenden, in die Zylinderbohrung (52;152) mündenden Zulauföffnung (62;162) zusammenwirkt und in einer Stellung, in der es mit der Dichtfläche (60;178) am Ventilsitz (64;164) anliegt, die Zulauföffnung (62;162) vollständig verschließt.Fuel injection device for an internal combustion engine with a feed pump (12), through which fuel is delivered from a fuel reservoir (10) to the suction side of a high-pressure pump (14), the high-pressure pump (14) delivering fuel to a reservoir (16) depending on operating parameters of the internal combustion engine, with a fuel metering device (44; 144) for setting the amount of fuel delivered by the high pressure pump (14) into the accumulator (16), the fuel metering device (44; 144) having an actuator (45) and a control valve (46) actuated by the latter, wherein the control valve (46) has a slide-shaped valve member (54; 154) guided in a cylinder bore (52; 152) of a valve housing (50; 150), which can be displaced by the actuator (45) against a restoring force (68), and wherein the valve member (54; 154) with its outer casing (56; 156) in cooperation with an outlet (58; 158) from the cylinder bore (52; 152) Flow cross section controls from the feed pump (12) to the high pressure pump (14), characterized in that the valve member (54; 154) with a sealing surface (60; 178) with a valve seat (64; 164) for controlling one of the feed pump (12) leading inlet opening (62; 162) opening into the cylinder bore (52; 152) and in a position in which it rests with the sealing surface (60; 178) on the valve seat (64; 164), the inlet opening (62; 162) completely closed. Kraftstoffeinspritzeinrichtung nach Anspruch 1, dadurch gekennzeichnet, daß durch das Ventilglied (54;154) ausgehend von seiner Schließstellung, in der es mit der Dichtfläche (60;178) am Ventilsitz (64;164) anliegt, bei einer vom Ventilsitz (64;164) weggerichteten Hubbewegung zunächst auf einem Leerhub (h) mit seinem Außenmantel noch keinen Durchflußquerschnitt freigibt und erst nach Durchfahren des Leerhubs (h) hubabhängig mit seinem Außenmantel (56;156) einen zunehmend größeren Durchflußquerschnitt freigibt.Fuel injection device according to Claim 1, characterized in that , starting from its closed position, in which it rests with the sealing surface (60; 178) on the valve seat (64; 164), the valve member (54; 154) at one of the valve seat (64; 164 ) directed stroke movement initially does not release a flow cross-section on its idle stroke (h) with its outer jacket and only releases an increasingly larger flow cross-section with its outer jacket (56; 156) depending on the stroke. Kraftstoffeinspritzeinrichtung nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß die Dichtfläche (60) des Ventilglieds (54) sich zum Ende des Ventilglieds (54) hin verjüngend, zumindest annähernd kegelstumpfförmig ausgebildet ist.Fuel injection device according to Claim 1 or 2, characterized in that the sealing surface (60) of the valve member (54) tapers towards the end of the valve member (54), at least approximately in the shape of a truncated cone. Kraftstoffeinspritzeinrichtung nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß die Dichtfläche (60) des Ventilglieds (54) zumindest annähernd kugelsegmentförmig ausgebildet ist.Fuel injection device according to claim 1 or 2, characterized in that the sealing surface (60) of the valve member (54) is at least approximately spherical segment-shaped. Kraftstoffeinspritzeinrichtung nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß der Ventilsitz (64;164) sich zum Ventilglied (54) hin erweiternd, vorzugsweise zumindest annähernd kegelstumpfförmig ausgebildet ist.Fuel injection device according to one of Claims 1 to 4, characterized in that the valve seat (64; 164) widens towards the valve member (54), preferably at least approximately in the shape of a truncated cone. Kraftstoffeinspritzeinrichtung nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß in die Zylinderbohrung (152) ein Bauteil (174) eingesetzt ist, das einen zur Dichtfläche (178) weisenden Stutzen (176) aufweist, an dessen Ende der Ventilsitz (164) ausgebildet ist.Fuel injection device according to one of Claims 1 to 5, characterized in that a component (174) is inserted into the cylinder bore (152) and has a connecting piece (176) pointing towards the sealing surface (178), at the end of which the valve seat (164) is formed is. Kraftstoffeinspritzeinrichtung nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, daß die Dichtfläche (178) an einem mit dem Ventilglied (154) verbundenen Dichtelement (178) ausgebildet ist.Fuel injection device according to one of claims 1 to 6, characterized in that the sealing surface (178) a sealing element (178) connected to the valve member (154) is formed. Kraftstoffeinspritzeinrichtung nach Anspruch 6 und 7, dadurch gekennzeichnet, daß das Ventilglied (154) topfförmig ausgebildet ist, daß der Stutzen (176) in das Ventilglied (154) von dessen offener Seite her hineinragt und daß das Dichtelement (178) im Ventilglied (154) im Bereich von dessen geschlossenem Ende angeordnet ist.Fuel injection device according to Claims 6 and 7, characterized in that the valve member (154) is pot-shaped, that the connecting piece (176) projects into the valve member (154) from its open side and that the sealing element (178) in the valve member (154) is arranged in the region of its closed end.
EP02024857A 2001-12-19 2002-11-08 Fuel injection device for an internal combustion engine Withdrawn EP1321663A3 (en)

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DE10162385 2001-12-19

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AU (1) AU2002363846A1 (en)
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EP1321663A3 (en) 2003-07-02
US20030136384A1 (en) 2003-07-24
DE10261780A1 (en) 2003-07-03
AU2002363846A1 (en) 2003-06-30
WO2003052262A1 (en) 2003-06-26
DE10295868D2 (en) 2004-11-11
JP2003222059A (en) 2003-08-08

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