WO2004111437A1 - Device for setting a variable flow cross-section - Google Patents

Device for setting a variable flow cross-section Download PDF

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Publication number
WO2004111437A1
WO2004111437A1 PCT/DE2004/000685 DE2004000685W WO2004111437A1 WO 2004111437 A1 WO2004111437 A1 WO 2004111437A1 DE 2004000685 W DE2004000685 W DE 2004000685W WO 2004111437 A1 WO2004111437 A1 WO 2004111437A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve member
fuel
valve
flow cross
section
Prior art date
Application number
PCT/DE2004/000685
Other languages
German (de)
French (fr)
Inventor
Sascha Ambrock
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
Priority to DE502004004245T priority Critical patent/DE502004004245D1/en
Priority to EP04725275A priority patent/EP1631741B1/en
Publication of WO2004111437A1 publication Critical patent/WO2004111437A1/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
    • 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
    • F02M63/0012—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
    • 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
    • F02M63/0275—Arrangement of common rails
    • F02M63/028—Returnless common rail system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/02—Fuel-injection apparatus having means for reducing wear

Definitions

  • the invention relates to a device for setting a variable flow cross-section according to the preamble of claim 1.
  • Such a device is known from DE 198 53 103 Al.
  • This device is used to set a variable flow cross section in a fuel connection of a fuel injection device of an internal combustion engine.
  • the device has an electrical actuator in the form of an electromagnet and a control valve actuated by it.
  • the control valve has a hollow valve member which is guided in a cylinder bore of a valve housing and which can be displaced by the actuator against a restoring force.
  • the valve member controls a flow cross-section in cooperation with at least one opening opening on the jacket of the cylinder bore.
  • Fuel under pressure flows into the interior of the valve member and fuel flows out of the control valve through at least one opening in the jacket of the valve member and the at least one opening in the jacket of the cylinder bore.
  • the device is arranged between a feed pump and a high-pressure pump in order to ensure a variable flow cross-section between the feed pump and the high-pressure pump and thus variable intake quantities of fuel in the
  • the high-pressure pump delivers fuel to a store from which fuel is taken for injection at the internal combustion engine.
  • a relatively high friction occurs between the valve member and the cylinder bore, which leads to a strong hysteresis in the movement of the valve member and corresponding hysteresis in the setting of the
  • the device according to the invention with the features according to claim 1 has the advantage that the at least one groove on the valve member enables lubrication between the valve member and the cylinder bore, since the groove is supplied with fuel under pressure from the interior of the valve member. This reduces the friction between the valve member and the cylinder bore, thereby improving the function of the device and reducing wear.
  • Fuel injection device for an internal combustion engine in a schematic representation, Figure 2 in an enlarged view, a device for setting a variable flow cross-section of the
  • 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 one
  • the fuel injection device has a feed pump 12, through which fuel is fed from the fuel tank 10 to at least one 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 the store 16 to injectors 20 arranged on the cylinders of the internal combustion engine.
  • 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 one
  • Control device 23 is controlled by which the time and duration of the fuel injection by the injectors 20 is determined as a function of operating parameters of the internal combustion engine, such as speed, load, temperature and others. - A -
  • 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, wherein 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 at least one or more pump elements.
  • a device 44 is arranged between the feed pump 12 and the high-pressure pump 14, by means of which a variable flow cross section can be set and which forms a fuel metering device here.
  • the fuel metering device 44 has a control valve 46 actuated by an electrical actuator 45, for example an electromagnet or a piezo actuator, by means of which the flow cross-section 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 supplied by the
  • High-pressure pump 14 is conveyed under high pressure into the accumulator 16 in order to maintain a predetermined pressure in the accumulator 16 which is dependent on the operating parameters of the internal combustion engine.
  • a pressure sensor 17 is arranged on the accumulator 16, which is connected to the control device 23 and which supplies a signal for the actual pressure in the accumulator 16.
  • the fuel metering device 44 is shown enlarged in accordance with an exemplary embodiment.
  • the fuel metering device 44 is part of the Control valve 46 a valve housing 50, in which a valve member 54 formed as a hollow piston is slidably guided in a cylinder bore 52.
  • the valve member 54 can be pot-shaped and have a bottom with at least one opening at one end.
  • Valve housing 50 can form a magnetic core of actuator 45 designed as an electromagnet. At least one opening 56 opens at the jacket of the cylinder bore 52 and forms a connection to the high-pressure pump 14. A circumferential annular groove 58 is formed in the cylinder bore 52, into which the at least one opening 56 opens.
  • the cylinder bore 52 is designed as a blind bore in the valve housing 50 and is closed at its open end with a cover 60 inserted into it, for example pressed or screwed in.
  • the cover 60 has an opening 62 which forms a connection to the feed pump 12. The fuel delivered by the feed pump 12 thus flows into the cylinder bore 52 and into the interior of the hollow valve member 54 through the opening 62 in the cover 60.
  • the valve member 54 has in its jacket at least one, preferably a plurality of openings 64 arranged distributed over its circumference.
  • the openings 64 are designed, for example, in such a way that they become narrower in the axial direction towards the end region of the valve member 54 facing away from the cover 60.
  • the openings 64 can also have any other shape.
  • a prestressed spring 66 is clamped between the cover 60 and the valve member 54, by means of which the valve member 54 is pressed away from the cover 60.
  • the actuator 45 acts on the bottom thereof at least indirectly, for example via a rod 68. If the actuator 45 is not actuated, that is to say is de-energized, the valve member 54 is pressed away from the cover 60 by the spring 66, the openings 64 in the valve member 54 with the annular groove 58 then being the same Largely cover cylinder bore 52, so that a large flow cross section for the fuel from feed pump 12 to high-pressure pump 14 is released.
  • the valve member 54 When the actuator 45 is actuated, that is to say energized, the valve member 54 is displaced towards the cover 60 against the force of the spring 66. When the valve member 54 is displaced, the openings 64 of the valve member 54 overlap less and less with the annular groove 48 of the cylinder bore 52, so that an increasingly smaller flow cross section for the fuel is released from the feed pump 12 to the high-pressure pump 14.
  • the released flow cross section is proportional to the position of the valve member 54, which in turn is proportional to the actuation, in particular the current strength, of the actuator 45.
  • the shape of the openings 64 in the valve member 54 can influence the change in the size of the released flow cross-section when the valve member 54 is shifted, and thus a desired characteristic curve of the device can be achieved. With the narrowing openings 64, a non-linear characteristic curve of the device is achieved, the
  • Flow cross section is disproportionately reduced with increasing displacement of the valve member 54 to the cover 60.
  • the valve member 54 is moved so far towards the cover 60 that its openings 64 no longer overlap with the annular groove 58 of the cylinder bore 52 and the flow cross section is at least approximately completely closed.
  • the openings 64 in the valve member 54 can also be omitted, the size of the flow cross-section then being controlled by the end of the jacket of the valve member 54 due to its different overlap with the annular groove 58 of the valve housing 50.
  • the valve member 54 has in its jacket at least one groove 70 which extends at least over part of its circumference.
  • the groove 70 is as Forms annular groove extending over the entire circumference of the valve member 54.
  • At least two grooves 70 are preferably provided, each of which is arranged near an axial end region of the valve member 54.
  • the groove 70 arranged near the end region of the valve member 54 facing the cover 60 is arranged at an axial distance from the openings 64 and does not overlap them.
  • the grooves 70 are each connected to the interior of the valve member 54 via at least one bore 72.
  • the pressure generated by the feed pump 12 prevails in the interior of the valve member 54, so that fuel under pressure is constantly supplied to the grooves 70 of the valve member 54 from the interior of the valve member 54. This ensures good lubrication between the valve member 54 and the cylinder bore 52 and thus low friction and wear.

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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

The invention relates to a device for setting a variable flow cross-section in a fuel connection for a fuel injection device on an internal combustion engine, comprising an electrical actuator (45) and a regulating valve (46) controlled thereby. The regulating valve (46) comprises a hollow valve body (54), running in a cylinder drilling (52) of a valve housing (50), which may be displaced against a restoring force (66), by means of the actuator (45). The valve body (54) controls a flow cross-section with an opening (64) embodied in the sleeve thereof in cooperation with at least one opening (56) which opens at the sleeve of the cylinder drilling (52), whereby the regulating valve (46) in the cylinder drilling (52) and the interior of the valve body (54) are supplied with fuel under pressure and fuel from the regulating valve (46) flows out through the at least one opening (64) in the valve body (54) and the at least one opening (56), opening out at the sleeve of the cylinder drilling (52). The valve body (54) comprises at least one groove (70) in the sleeve thereof, running over at least a part of the circumference, connected to the interior of the valve body (54).

Description

Einrichtung zur Einstellung eines veränderlichen DurchflussquerschnittsDevice for setting a variable flow cross-section
Stand der TechnikState of the art
Die Erfindung geht aus von einer Einrichtung zur Einstellung eines veränderlichen Durchflussquerschnitts nach der Gattung des Anspruchs 1.The invention relates to a device for setting a variable flow cross-section according to the preamble of claim 1.
Eine solche Einrichtung ist durch die DE 198 53 103 Al bekannt. Diese Einrichtung dient zur Einstellung eines veränderlichen Durchflussquerschnitts in einer Kraftstoffverbindung einer Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine. Die Einrichtung weist einen elektrischen Aktor in Form eines Elektromagneten und ein durch diesen betätigtes Regelventil auf. Das Regelventil weist ein in einer Zylinderbohrung eines Ventilgehäuses geführtes hohel Ventilglied auf, das durch den Aktor gegen eine Rückstellkraft verschiebbar ist. Das Ventilglied steuert dabei in Zusammenwirkung mit wenigstens einer am Mantel der Zylinderbohrung mündenden Öffnung einen Durchflussquerschnitt. Dem Regelventil fließt dabei in das Innere des Ventilglieds unter Druck stehender Kraftstoff zu und aus dem Regelventil fließt durch wenigstens eine Öffnung im Mantel des Ventilglieds und die wenigstens eine Öffnung am Mantel der Zylinderbohrung Kraftstoff ab. Die Einrichtung ist zwischen einer Förderpumpe und einer Hochdruckpumpe angeordnet, um einen veränderlichen Durchflussquerschnitt zwischen der Förderpumpe und der Hochdruckpumpe und damit veränderliche Ansaugmengen an Kraftstoff bei derSuch a device is known from DE 198 53 103 Al. This device is used to set a variable flow cross section in a fuel connection of a fuel injection device of an internal combustion engine. The device has an electrical actuator in the form of an electromagnet and a control valve actuated by it. The control valve has a hollow valve member which is guided in a cylinder bore of a valve housing and which can be displaced by the actuator against a restoring force. The valve member controls a flow cross-section in cooperation with at least one opening opening on the jacket of the cylinder bore. Fuel under pressure flows into the interior of the valve member and fuel flows out of the control valve through at least one opening in the jacket of the valve member and the at least one opening in the jacket of the cylinder bore. The device is arranged between a feed pump and a high-pressure pump in order to ensure a variable flow cross-section between the feed pump and the high-pressure pump and thus variable intake quantities of fuel in the
Hochdruckpumpe zu ermöglichen. Durch die Hochdruckpumpe wird Kraftstoff in einen Speicher gefördert, aus dem Kraftstoff zur Einspritzung an der Brennkraftmaschine entnommen wird. Bei dieser bekannten Einrichtung besteht das Problem, dass zwischen dem Ventilglied und der Zylinderbohrung eine relativ hohe Reibung auftritt, die zu einer starken Hysterese in der Bewegung des Ventilglieds und entsprechender Hysterese bei der Einstellung desTo enable high pressure pump. The high-pressure pump delivers fuel to a store from which fuel is taken for injection at the internal combustion engine. In this known device there is the problem that a relatively high friction occurs between the valve member and the cylinder bore, which leads to a strong hysteresis in the movement of the valve member and corresponding hysteresis in the setting of the
Durchflussquerschnitts führt. Es kann hier somit nicht mehr durch eine vorgegebene Ansteuerung des Aktors ein definierter Durchflussquerschnitt eingestellt werden, da das Ventilglied infolge der starken Reibung nicht in die erforderliche Stellung bewegt werden kann. Die starke Reibung führt außerdem zu erhöhtem Verschleiß des Ventilglieds und des Ventilgehäuses.Flow cross section leads. It is therefore no longer possible to set a defined flow cross-section here by a predetermined control of the actuator, since the valve member cannot be moved into the required position due to the strong friction. The strong friction also leads to increased wear of the valve member and the valve housing.
Vorteile der ErfindungAdvantages of the invention
Die erfindungsgemäße Einrichtung mit den Merkmalen gemäß Anspruch 1 hat demgegenüber den Vorteil, dass durch die wenigstens eine Nut am Ventilglied eine Schmierung zwischen dem Ventilglied und der Zylinderbohrung ermöglicht ist, da der Nut unter Druck stehender Kraftstoff aus dem Inneren des Ventilglieds zugeführt wird. Hierdurch wird die Reibung zwischen dem Ventilglied und der Zylinderbohrung verringert und dadurch die Funktion der Einrichtung verbessert sowie der Verschleiß verringert.The device according to the invention with the features according to claim 1 has the advantage that the at least one groove on the valve member enables lubrication between the valve member and the cylinder bore, since the groove is supplied with fuel under pressure from the interior of the valve member. This reduces the friction between the valve member and the cylinder bore, thereby improving the function of the device and reducing wear.
In den abhängigen Ansprüchen sind vorteilhafte Ausgestaltungen und Weiterbildungen der erfindungsgemäßen Einrichtung angegeben. Die Ausbildung gemäß Anspruch 2 ermöglicht eine weiter verbesserte Schmierung zwischen Ventilglied und Zylinderbohrung.Advantageous refinements and developments of the device according to the invention are specified in the dependent claims. The embodiment according to claim 2 enables a further improved lubrication between the valve member and the cylinder bore.
Zeichnungdrawing
Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 eineAn embodiment of the invention is shown in the drawing and in the following description explained. 1 shows a
Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine in schematischer Darstellung, Figur 2 in vergrößerter Darstellung eine Einrichtung zur Einstellung eines veränderlichen Durchflussquerschnitts derFuel injection device for an internal combustion engine in a schematic representation, Figure 2 in an enlarged view, a device for setting a variable flow cross-section of the
Kraftstoffeinspritzeinrichtung in einem Längsschnitt und Figur 3 die Einrichtung in einem Querschnitt.Fuel injection device in a longitudinal section and Figure 3 shows the device in a cross section.
Beschreibung des AusführungsbeispielsDescription of the embodiment
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 einenFIG. 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 one
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 wenigstens 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 elektronischeFuel 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 fed from the fuel tank 10 to at least one 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 the store 16 to injectors 20 arranged on the cylinders of the internal combustion engine. 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 one
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. - A -Control device 23 is controlled by which the time and duration of the fuel injection by the injectors 20 is determined as a function of operating parameters of the internal combustion engine, such as speed, load, temperature and others. - A -
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. Die Hochdruckpumpe 14 kann als Radialkolbenpumpe ausgebildet sein und weist wenigstens ein oder mehrere Pumpenelemente auf.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, wherein 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 at least one or more pump elements.
Zwischen der Förderpumpe 12 und der Hochdruckpumpe 14 ist eine Einrichtung 44 angeordnet, durch die ein veränderlicher Durchflussquerschnitt eingestellt werden kann und die hier eine KraftstoffZumesseinrichtung bildet. Die KraftstoffZumesseinrichtung 44 weist ein durch einen elektrischen Aktor 45, beispielsweise einen Elektromagneten oder einen Piezoaktor, betätigtes Regelventil 46 auf, durch das der Durchflussquerschnitt 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 dieA device 44 is arranged between the feed pump 12 and the high-pressure pump 14, by means of which a variable flow cross section can be set and which forms a fuel metering device here. The fuel metering device 44 has a control valve 46 actuated by an electrical actuator 45, for example an electromagnet or a piezo actuator, by means of which the flow cross-section 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 supplied by the
Hochdruckpumpe 14 unter Hochdruck in den Speicher 16 gefördert wird, um im Speicher 16 einen vorgegebenen, von Betriebsparametern der Brennkraftmaschine abhängigen Druck aufrechtzuerhalten. Am Speicher 16 ist dabei ein Drucksensor 17 angeordnet, der mit der Steuereinrichtung 23 verbunden ist und dieser ein Signal für den tatsächlichen Druck im Speicher 16 zuführt.High-pressure pump 14 is conveyed under high pressure into the accumulator 16 in order to maintain a predetermined pressure in the accumulator 16 which is dependent on the operating parameters of the internal combustion engine. A pressure sensor 17 is arranged on the accumulator 16, which is connected to the control device 23 and which supplies a signal for the actual pressure in the accumulator 16.
In den Figuren 2 und 3 ist die Kraftstoffzumeßeinrichtung 44 vergrößert gemäß einem Ausführungsbeispiel dargestellt. Die Kraftstoffzumeßeinrichtung 44 weist als Teil des Regelventils 46 ein Ventilgehäuse 50 auf, in dem in einer Zylinderbohrung 52 ein als hohler Kolben ausgebildetes Ventilglied 54 verschiebbar geführt ist. Das Ventilglied 54 kann topfförmig ausgebildet sein und an einem Ende einen Boden mit wenigstens einer Öffnung aufweisen. DasIn FIGS. 2 and 3, the fuel metering device 44 is shown enlarged in accordance with an exemplary embodiment. The fuel metering device 44 is part of the Control valve 46 a valve housing 50, in which a valve member 54 formed as a hollow piston is slidably guided in a cylinder bore 52. The valve member 54 can be pot-shaped and have a bottom with at least one opening at one end. The
Ventilgehäuse 50 kann einen Magnetkern des als Elektromagnet ausgeführten Aktors 45 bilden. Am Mantel der Zylinderbohrung 52 mündet wenigstens eine Öffnung 56, die eine Verbindung zur Hochdruckpumpe 14 bildet. In der Zylinderbohrung 52 ist eine umlaufende Ringnut 58 ausgebildet, in die die wenigstens eine Öffnung 56 mündet. Die Zylinderbohrung 52 ist als Sackbohrung im Ventilgehäuse 50 ausgebildet und an ihrem offenen Ende mit einer in diese eingesetzten, beispielsweise eingepressten oder eingeschraubten Deckel 60 verschlossen. Der Deckel 60 weist eine Öffnung 62 auf, die eine Verbindung zur Förderpumpe 12 bildet. In die Zylinderbohrung 52 und in das Innere des hohlen Ventilglieds 54 fließt somit durch die Öffnung 62 im Deckel 60 der durch die Förderpumpe 12 geförderte Kraftstoff zu. Das Ventilglied 54 weist in seinem Mantel wenigstens eine, vorzugsweise mehrere über dessen Umfang verteilt angeordnete Öffnungen 64 auf. Die Öffnungen 64 sind beispielsweise derart ausgebildet, dass diese in axialer Richtung zu dem dem Deckel 60 abgewandten Endbereich des Ventilglieds 54 hin schmäler werden. Die Öffnungen 64 können auch eine beliebige andere Form aufweisen.Valve housing 50 can form a magnetic core of actuator 45 designed as an electromagnet. At least one opening 56 opens at the jacket of the cylinder bore 52 and forms a connection to the high-pressure pump 14. A circumferential annular groove 58 is formed in the cylinder bore 52, into which the at least one opening 56 opens. The cylinder bore 52 is designed as a blind bore in the valve housing 50 and is closed at its open end with a cover 60 inserted into it, for example pressed or screwed in. The cover 60 has an opening 62 which forms a connection to the feed pump 12. The fuel delivered by the feed pump 12 thus flows into the cylinder bore 52 and into the interior of the hollow valve member 54 through the opening 62 in the cover 60. The valve member 54 has in its jacket at least one, preferably a plurality of openings 64 arranged distributed over its circumference. The openings 64 are designed, for example, in such a way that they become narrower in the axial direction towards the end region of the valve member 54 facing away from the cover 60. The openings 64 can also have any other shape.
Zwischen dem Deckel 60 und dem Ventilglied 54 ist eine vorgespannte Feder 66 eingespannt, durch die das Ventilglied 54 vom Deckel 60 weggedrückt wird. Am dem Deckel 60 abgewandten Endbereich des Ventilglieds 54 greift an dessen Boden zumindest mittelbar, beispielsweise über eine Stange 68, der Aktor 45 an. Wenn der Aktor 45 nicht angesteuert ist, also stromlos ist, so wird das Ventilglied 54 durch die Feder 66 vom Deckel 60 weggedrückt, wobei sich dann die Öffnungen 64 im Ventilglied 54 mit der Ringnut 58 der Zylinderbohrung 52 weitgehend überdecken, so dass ein grosser Durchflussquerschnitt für den Kraftstoff von der Förderpumpe 12 zur Hochdruckpumpe 14 freigegeben ist. Wenn der Aktor 45 angesteuert, also bestromt wird, so wird das Ventilglied 54 gegen die Kraft der Feder 66 zum Deckel 60 hin verschoben. Bei der Verschiebung des Ventilglieds 54 überdecken sich die Öffnungen 64 des Ventilglieds 54 zunehmend weniger mit der Ringnut 48 der Zylinderbohrung 52, so dass ein zunehmend kleinerer Durchflussquerschnitt für den Kraftstoff von der Förderpumpe 12 zur Hochdruckpumpe 14 freigegeben wird. Der freigegebene Durchflussquerschnitt ist dabei proportional zur Stellung des Ventilglieds 54, die wiederum proportional zur Ansteuerung, insbesondere der Stromstärke, des Aktors 45 ist. Durch die Form der Öffnungen 64 im Ventilglied 54 kann die Änderung der Größe des freigegebenen Durchflussquerschnitts bei einer Verschiebung des Ventilglieds 54 beeinflusst werden und damit eine gewünschte Kennlinie der Einrichtung erreicht werden. Bei den schmäler werdenden Öffnungen 64 wird eine nichtlineare Kennlinie der Einrichtung erreicht, wobei derA prestressed spring 66 is clamped between the cover 60 and the valve member 54, by means of which the valve member 54 is pressed away from the cover 60. At the end area of the valve member 54 facing away from the cover 60, the actuator 45 acts on the bottom thereof at least indirectly, for example via a rod 68. If the actuator 45 is not actuated, that is to say is de-energized, the valve member 54 is pressed away from the cover 60 by the spring 66, the openings 64 in the valve member 54 with the annular groove 58 then being the same Largely cover cylinder bore 52, so that a large flow cross section for the fuel from feed pump 12 to high-pressure pump 14 is released. When the actuator 45 is actuated, that is to say energized, the valve member 54 is displaced towards the cover 60 against the force of the spring 66. When the valve member 54 is displaced, the openings 64 of the valve member 54 overlap less and less with the annular groove 48 of the cylinder bore 52, so that an increasingly smaller flow cross section for the fuel is released from the feed pump 12 to the high-pressure pump 14. The released flow cross section is proportional to the position of the valve member 54, which in turn is proportional to the actuation, in particular the current strength, of the actuator 45. The shape of the openings 64 in the valve member 54 can influence the change in the size of the released flow cross-section when the valve member 54 is shifted, and thus a desired characteristic curve of the device can be achieved. With the narrowing openings 64, a non-linear characteristic curve of the device is achieved, the
Durchflussquerschnitt mit zunehmendem Verschiebeweg des Ventilglieds 54 zum Deckel 60 hin überproportional verringert wird. Bei Ansteuerung des Aktors 45 mit maximaler Stromstärke wird das Ventilglied 54 so weit zum Deckel 60 hin verschoben, dass dessen Öffnungen 64 sich nicht mehr mit der Ringnut 58 der Zylinderbohrung 52 überdecken und der Durchflussquerschnitt zumindest annähernd vollständig verschlossen ist. Alternativ können die Öffnungen 64 im Ventilglied 54 auch entfallen, wobei dann durch das Ende des Mantels des Ventilglieds 54 durch dessen unterschiedliche Überdeckung mit der Ringnut 58 des Ventilgehäuses 50 die Größe des Durchflussquerschnitts gesteuert wird.Flow cross section is disproportionately reduced with increasing displacement of the valve member 54 to the cover 60. When the actuator 45 is actuated with the maximum current, the valve member 54 is moved so far towards the cover 60 that its openings 64 no longer overlap with the annular groove 58 of the cylinder bore 52 and the flow cross section is at least approximately completely closed. Alternatively, the openings 64 in the valve member 54 can also be omitted, the size of the flow cross-section then being controlled by the end of the jacket of the valve member 54 due to its different overlap with the annular groove 58 of the valve housing 50.
Das Ventilglied 54 weist in seinem Mantel wenigstens eine, sich zumindest über einen Teil von dessen Umfang erstreckende Nut 70 auf. Vorzugsweise ist die Nut 70 als über den gesamten Umfang des Ventilglieds 54 verlaufende Ringnut ausbildet. Vorzugsweise sind wenigstens zwei Nuten 70 vorgesehen, die jeweils nahe einem axialen Endbereich des Ventilglieds 54 angeordnet sind. Die nahe dem dem Deckel 60 zugewandten Endbereich des Ventilglieds 54 angeordnete Nut 70 ist mit axialem Abstand zu den Öffnungen 64 angeordnet und überdeckt sich mit diesen nicht. Die Nuten 70 sind über jeweils wenigstens eine Bohrung 72 mit dem Inneren des Ventilglieds 54 verbunden. Im Inneren des Ventilglieds 54 herrscht ständig der von der Förderpumpe 12 erzeugte Druck, so dass den Nuten 70 des Ventilglieds 54 ständig unter Druck stehender Kraftstoff aus dem Inneren des Ventilglieds 54 zugeführt wird. Hierdurch wird eine gute Schmierung zwischen dem Ventilglied 54 und der Zylinderbohrung 52 und damit eine geringe Reibung und ein geringer Verschleiß sichergestellt. The valve member 54 has in its jacket at least one groove 70 which extends at least over part of its circumference. Preferably, the groove 70 is as Forms annular groove extending over the entire circumference of the valve member 54. At least two grooves 70 are preferably provided, each of which is arranged near an axial end region of the valve member 54. The groove 70 arranged near the end region of the valve member 54 facing the cover 60 is arranged at an axial distance from the openings 64 and does not overlap them. The grooves 70 are each connected to the interior of the valve member 54 via at least one bore 72. The pressure generated by the feed pump 12 prevails in the interior of the valve member 54, so that fuel under pressure is constantly supplied to the grooves 70 of the valve member 54 from the interior of the valve member 54. This ensures good lubrication between the valve member 54 and the cylinder bore 52 and thus low friction and wear.

Claims

Ansprüche Expectations
1. Einrichtung zur Einstellung eines veränderlichen Durchflussquerschnitts in einer Kraftstoffverbindung einer Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine mit einem elektrischen Aktor (45) und einem durch diesen betätigten Regelventil (46) , wobei das Regelventil (46) ein in einer Zylinderbohrung (52) eines Ventilgehäuses (50) geführtes hohles Ventilglied (54) aufweist, das durch den Aktor (45) gegen eine Rückstellkraft (66) verschiebbar ist, wobei das Ventilglied (54) mit seinem Mantel in Zusammenwirkung mit wenigstens einer am Mantel der Zylinderbohrung (52) mündenden Öffnung (56) einen Durchflussquerschnitt steuert, wobei dem Regelventil (46) in die Zylinderbohrung (52) und das Innere des Ventilglieds (54) unter Druck stehender Kraftstoff zugeführt wird und Kraftstoff aus dem Regelventil (46) durch die wenigstens eine am Mantel der Zylinderbohrung (52) mündende Öffnung (56) abfließt, dadurch gekennzeichnet, dass das Ventilglied (54) in seinem Mantel wenigstens eine sich zumindest über einen Teil seines Umfangs erstreckende Nut (70) aufweist, die mit dem Inneren des Ventilglieds (54) verbunden ist.1. Device for setting a variable flow cross-section in a fuel connection of a fuel injection device for an internal combustion engine with an electric actuator (45) and a control valve (46) actuated by the latter, the control valve (46) being in a cylinder bore (52) of a valve housing (50 ) guided hollow valve member (54) which can be displaced by the actuator (45) against a restoring force (66), the valve member (54) with its jacket in cooperation with at least one opening (56) opening on the jacket of the cylinder bore (52) ) controls a flow cross-section, fuel under pressure being supplied to the control valve (46) into the cylinder bore (52) and the interior of the valve member (54) and fuel from the control valve (46) through the at least one on the jacket of the cylinder bore (52) flows out opening (56), characterized in that the valve member (54) in its jacket little at least one groove (70) extending over at least part of its circumference, which is connected to the interior of the valve member (54).
2. Einrichtung nach Anspruch 1, dadurch gekennzeichnet, dass das Ventilglied (54) nahe seinen beiden axialen Endbereichen jeweils wenigstens eine Nut (70) aufweist.2. Device according to claim 1, characterized in that the valve member (54) has at least one groove (70) near its two axial end regions.
3. Einrichtung nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass sich die wenigstens eine Nut (70) über den gesamten Umfang des Ventilglieds (54) erstreckt. 3. Device according to claim 1 or 2, characterized in that the at least one groove (70) extends over the entire circumference of the valve member (54).
4. Einrichtung nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass die wenigstens eine Nut (70) über wenigstens eine Bohrung (72) im Ventilglied (54) mit dem Inneren des Ventilglieds (54) verbunden ist.4. Device according to one of claims 1 to 3, characterized in that the at least one groove (70) via at least one bore (72) in the valve member (54) is connected to the interior of the valve member (54).
5. Einrichtung nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass der Aktor (45) ein Elektromagnet ist und dass das Ventilgehäuse (50) einen Magnetkern des Aktors (45) bildet.5. Device according to one of the preceding claims, characterized in that the actuator (45) is an electromagnet and that the valve housing (50) forms a magnetic core of the actuator (45).
6. Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine mit einer Förderpumpe (12) und einer Hochdruckpumpe (14) , wobei durch die Förderpumpe (12) Kraftstoff zur Hochdruckpumpe (14) gefördert wird und durch die Hochdruckpumpe (14) Kraftstoff in einen Speicher (16) gefördert wird, aus dem Kraftstoff zur Einspritzung an der Brennkraftmaschine entnommen wird, dadurch gekennzeichnet, dass zwischen der Förderpumpe (12) und der Hochdruckpumpe (14) eine Einrichtung zur Einstellung eines veränderlichen Durchflussquerschnitts nach einem der vorstehenden Ansprüche angeordnet ist. 6. Fuel injection device for an internal combustion engine with a feed pump (12) and a high-pressure pump (14), fuel being conveyed to the high-pressure pump (14) by the feed pump (12) and fuel being conveyed into a reservoir (16) by the high-pressure pump (14) , from which fuel is taken for injection on the internal combustion engine, characterized in that a device for setting a variable flow cross section according to one of the preceding claims is arranged between the feed pump (12) and the high pressure pump (14).
PCT/DE2004/000685 2003-05-27 2004-04-02 Device for setting a variable flow cross-section WO2004111437A1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE502004004245T DE502004004245D1 (en) 2003-05-27 2004-04-02 DEVICE FOR ADJUSTING A DIFFICULT FLOW INTERFACE
EP04725275A EP1631741B1 (en) 2003-05-27 2004-04-02 Device for setting a variable flow cross-section

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10324010A DE10324010A1 (en) 2003-05-27 2003-05-27 Mechanism for adjusting variable through-flow cross-section in fuel connection of fuel injection unit of an internal combustion engine, comprises a valve member which has a groove running over circumference of its cover
DE10324010.1 2003-05-27

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WO2004111437A1 true WO2004111437A1 (en) 2004-12-23

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WO2012155162A1 (en) * 2011-05-18 2012-11-22 Robert Bosch Gmbh High-pressure pump arrangement for pumping combustible fuel from a tank into a high-pressure container
WO2015110242A1 (en) * 2014-01-27 2015-07-30 Robert Bosch Gmbh Electromagnetically controlled valve for a high pressure pump and high pressure pump

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DE102007000077B4 (en) 2006-02-08 2018-06-28 Denso Corporation Fuel injection system for an internal combustion engine

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WO2012155162A1 (en) * 2011-05-18 2012-11-22 Robert Bosch Gmbh High-pressure pump arrangement for pumping combustible fuel from a tank into a high-pressure container
WO2015110242A1 (en) * 2014-01-27 2015-07-30 Robert Bosch Gmbh Electromagnetically controlled valve for a high pressure pump and high pressure pump

Also Published As

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EP1631741B1 (en) 2007-07-04
DE10324010A1 (en) 2004-12-16
DE502004004245D1 (en) 2007-08-16
EP1631741A1 (en) 2006-03-08

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