EP1092863A2 - Pressure regulating valve for an accumulator-type fuel injection system for internal combustion engines - Google Patents

Pressure regulating valve for an accumulator-type fuel injection system for internal combustion engines Download PDF

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Publication number
EP1092863A2
EP1092863A2 EP00120442A EP00120442A EP1092863A2 EP 1092863 A2 EP1092863 A2 EP 1092863A2 EP 00120442 A EP00120442 A EP 00120442A EP 00120442 A EP00120442 A EP 00120442A EP 1092863 A2 EP1092863 A2 EP 1092863A2
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EP
European Patent Office
Prior art keywords
valve member
valve
bore
pressure control
sections
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Withdrawn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
EP00120442A
Other languages
German (de)
French (fr)
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EP1092863A3 (en
Inventor
Holger Dr. Rapp
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Robert Bosch GmbH
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Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1092863A2 publication Critical patent/EP1092863A2/en
Publication of EP1092863A3 publication Critical patent/EP1092863A3/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Withdrawn legal-status Critical Current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
    • F02M63/02—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
    • F02M63/023—Means for varying pressure in common rails
    • F02M63/0235—Means for varying pressure in common rails by bleeding fuel pressure
    • F02M63/025—Means for varying pressure in common rails by bleeding fuel pressure from the common rail
    • 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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/005—Arrangement of electrical wires and connections, e.g. wire harness, sockets, plugs; Arrangement of electronic control circuits in or on fuel injection apparatus
    • 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
    • F02M63/005—Pressure relief valves
    • F02M63/0052—Pressure relief valves with means for adjusting the opening pressure, e.g. electrically controlled
    • 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
    • F02M69/54—Arrangement of fuel pressure regulators

Definitions

  • the invention relates to a pressure control valve for Storage fuel injection system for internal combustion engines according to the preamble of claim 1.
  • Such a pressure control valve is known from the literature, for example through the specialist book Diesel Engine Management, 2nd edition, Vieweg publishing house, 1998, pages 270, 271.
  • This Pressure control valve is used to control the pressure in one Fuel storage.
  • the pressure control valve has one in one Axial bore against the force of a closing spring displaceably guided, piston-shaped valve member.
  • the Valve member acts on a closing element in the closing direction of the pressure control valve and presses it against one Valve seat.
  • the valve member forms an armature of one Electromagnet to support the power of the Closing spring is energized.
  • the valve member has a relatively large length and is cylindrical, it is due to shape and Positional tolerances of the valve member and the bore It is difficult to have a defined management and investment Valve member in the bore over its entire length to reach.
  • the pressure control valve according to the invention with the features according to claim 1 has the advantage that the Valve member defined via its guide sections in the Bore is guided and thus the reliability of the Pressure control valve is improved.
  • FIG. 1 shows a pressure control valve in a longitudinal section
  • Figure 2 in an enlarged view Valve member of the pressure control valve according to a first Embodiment
  • Figure 3 shows the valve member according to a second embodiment.
  • FIG. 1 is a section Storage fuel injection system for internal combustion engines, especially self-igniting internal combustion engines, shown.
  • the storage fuel injection system that too is referred to as a common rail injection system, has one High pressure pump 10 on, through the fuel under high pressure from a fuel storage tank 11 into one Fuel storage 12 is promoted.
  • the fuel storage 12 is tubular, for example, as a so-called rail, educated.
  • Lines 14 run from the fuel accumulator 12 to the injection points on the internal combustion engine 16, in each of which a valve 18 is arranged.
  • a pressure control valve 20 For setting the pressure in the fuel accumulator 12 is a pressure control valve 20 provided that at the outlet of the high pressure pump 10 or Fuel storage 12 can be arranged.
  • the pressure control valve 20 has a valve body 24, in a bore 26 is formed in the one piston-shaped valve member 28 arranged axially displaceable which is explained in more detail below.
  • a mounting flange 22 through which the valve body on the high pressure pump 10 or on Fuel storage 12 is attached.
  • the valve body 24 has an annular space 30 coaxially surrounding the bore 26 in which an electromagnet 32 with a coil winding is arranged.
  • an electromagnet 32 with a coil winding is arranged on the valve body 24 a Plugged connector 23, the electrical Contacting the electromagnet 32 is used.
  • a spring plate 34 On the Connection element 23 facing side of the valve body 24 a spring plate 34 is arranged, which the annular space 30th covered and on the side facing away from the annular space 30 a biased spring 36, for example as Helical compression spring is formed, supports.
  • the spring 36 is supported on the other hand with the valve body 24 connected lid 38, which in a hollow cylindrical Approach 40 of the valve body 24 is used.
  • the Approach 40 of the valve body 24 has a larger cross section as the ringarum 30 and the lid 38 can for example held by flanging the extension 40 in the valve body 24 his.
  • the valve member 28 protrudes into the extension 40 the bore 26 out and there has a reduced Diameter so that an annular shoulder on the valve member 28 42 is formed.
  • the valve member 28 protrudes with its end in a hole in the spring plate 34, which is in axial Direction on the annular shoulder 42 of the valve member 28 supports.
  • the bore 26 has in its approach 40 opposite end region an enlarged diameter in which a valve insert 44 is inserted.
  • the Valve insert 44 can be in valve body 24, for example be held by a protruding from the valve body 24 Edge is flanged over the valve insert 44.
  • the Valve insert 44 has a bore 46 that at least approximately coaxial to the bore 26 of the valve body 24 is arranged and into which the end region of the valve member 28 protrudes, which tapers, for example, conically can be trained.
  • the diameter of the bore 46 in Valve insert 44 reduces away from valve member 28, being at the transition from bore 46 to its smaller one Diameter of a valve seat 48 is formed for example, can be approximately conical. After this to the valve seat 48 section has the Bore 46 again a larger diameter.
  • valve insert 44 in the Valve insert 44 is a closing element 50, for example in FIG Arranged in the form of a ball, which with the valve seat 48th cooperates.
  • the valve insert 44 points in the area in FIG the end region of the valve member 28 in its bore 46 protrudes one or more openings 52 through which the Bore 46 connected to the surroundings of the valve insert 44 is.
  • the valve member 28 is enlarged in Figure 2 according to a first embodiment shown.
  • the valve member 28 consists for example of steel and forms an anchor of the Electromagnet 32.
  • the valve member points as before explained above at its top in Figures 1 and 2 End area has a smaller diameter, which makes the Ring shoulder 42 is formed, on which the spring plate 34th supports.
  • On its area arranged in the bore 26 the valve member 28 has several, preferably two in axially offset from each other Guide sections 54 which have a diameter, which is only slightly smaller than the diameter of the hole, so that the guide portions 54 with little radial play are arranged in the bore 26 and the valve member 28 displaceable in the bore via its guide sections 54 is led.
  • the guide sections 54 are short Cylinder sections formed and have axial Longitudinal sections, that is the longitudinal axis 29 of the valve member 28 containing longitudinal sections, straight, parallel to Longitudinal axis 29 of the valve member 28 extending surface lines on. Outside of the guide sections 54 is the diameter of the valve member 28 less than on the guide sections 54 and significantly smaller than the diameter of the bore 26, so that there is no contact of the valve member 28 with the bore 26 is given.
  • the transition between the Guide sections 54 and the remaining areas of the Valve member 28 can, for example, as in FIG. 2 represented by approximately conical Transition sections 56 take place.
  • the valve member 28 can for example by turning.
  • valve member 128 is according to a second Embodiment shown.
  • the valve member 128 is made again made of steel, for example, and forms an anchor of the electromagnet 32.
  • the valve member 128 has in its Several, preferably arranged in the bore 26 area two staggered in the axial direction Guide sections 154.
  • the guide sections 154 again have a diameter that is only slightly smaller is than the diameter of the hole so that the Guide sections 154 with little radial play in the Bore 26 are arranged and the valve member 28 via its Guide portions 154 slidable in the bore 26 is led.
  • the guide sections 154 are crowned formed and have convex in axial longitudinal sections curved surface lines.
  • the surface lines of the Guide sections 154 can, for example, at least approximately as circular sections with a radius R1 be trained.
  • the transitions between the Guide sections 154 and the remaining areas of the Valve member 128 can be rounded with in axial Longitudinal sections of concave curved surface lines that for example at least approximately as circular sections a radius R2 can be formed.
  • the valve member 128 can be made by turning or rolling. Through the rounded guide portions 154 is a tilt of the Valve member 128 avoided in the bore 26 with certainty.
  • the function of the pressure control valve 20 is shown below explained. If the electromagnet 32 is not energized, so is the valve member 28 and 128 by the spring 36, the forms a closing spring in the valve insert 44 pressed in, the valve member 28,128 with its Front end rests on the closing element 50 and this against the Valve seat 48 presses.
  • the closing element 50 is under pressure on the outlet side of the high pressure pump 10 or from the pressure in Fuel storage 12 acts on the Closing element 50 one of the force of the closing spring 36 counteracting force generated. If the one generated by the print Force is greater than the force of the closing spring 36, so the closing element 50 is lifted from the valve seat 48 and together with the valve member 28, 128 and the spring plate 34 postponed.
  • the pressure control valve 20 When the pressure control valve 20 is open, it flows out the fuel reservoir 12 fuel through the bore 46, the valve seat 48 and the openings 52 of the valve insert 44 off into a relief room, for example in the Fuel storage tank 11. If the electromagnet 32 is not is energized, the pressure control valve 20 already opens a relatively low pressure in the fuel accumulator, the is determined by the force of the closing spring 36. If the Pressure in the fuel accumulator 12 is to be increased the electromagnet 32 is energized so that the valve member 28, 128 in addition to the force of the closing spring 36 also by the magnetic force acting on the valve member in Closing direction is applied and the closing element 50 presses against the valve seat 48.
  • the Energization of the electromagnet 32 is by a Control device determines the signals over various Operating parameters of the internal combustion engine 16 are supplied and the amperage for the electromagnet 32 is set so that for each Operating state of the internal combustion engine 16 required Pressure in the fuel reservoir 12 sets.
  • the current for the electromagnet 32 for example be changed so that the power supply is clocked, for example with pulse width modulation.

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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)
  • Magnetically Actuated Valves (AREA)

Abstract

The valve has an axially guided piston-shaped valve element movable against the force of a closing spring and that acts on a closure element and presses it against a valve seat. The valve element forms the armature of an electromagnet supplied with current to augment the closing force of the spring and has guide sections offset in the axial direction that guide it in the bore and has a reduced cross-section outside the guide section region.

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einem Druckregelventil für ein Speicherkraftstoffeinspritzsystem für Brennkraftmaschinen nach der Gattung des Anspruchs 1.The invention relates to a pressure control valve for Storage fuel injection system for internal combustion engines according to the preamble of claim 1.

Ein solches Druckregelventil ist aus der Literatur bekannt, beispielsweise durch das Fachbuch Dieselmotor-Management, 2.Auflage, Verlag Vieweg, 1998, Seiten 270,271. Dieses Druckregelventil dient zur Regelung des Druckes in einem Kraftstoffspeicher. Das Druckregelventil weist ein in einer Bohrung gegen die Kraft einer Schließfeder axial verschiebbar geführtes, kolbenförmiges Ventilglied auf. Das Ventilglied wirkt in Schließrichtung auf ein Schließelement des Druckregelventils und presst dieses gegen einen Ventilsitz. Das Ventilglied bildet einen Anker eines Elektromagneten, der zur Unterstützung der Kraft der Schließfeder bestrombar ist. Durch die Schließfeder wird über das Ventilglied das Schließelement mit einer bestimmten Kraft gegen den Ventilsitz gedrückt, wobei das Schließelement durch den auf dieses wirkenden Druck im Kraftstoffspeicher vom Ventilsitz abgehoben wird, wenn die durch den Druck erzeugte Kraft die Kraft der Schließfeder überschreitet, und Kraftstoff aus dem Kraftstoffspeicher über das geöffnete Druckregelventil in einen Entlastungsraum abfließt. Zur Einstellung eines höheren Drucks im Kraftstoffspeicher wird der Elektromagnet bestromt, so daß die Schließkraft, die über das Ventilglied auf das Schließelement ausgeübt wird, erhöht wird und somit das Schließelement erst bei einem höheren Druck im Kraftstoffspeicher vom Ventilsitz abhebt und Kraftstoff aus dem Kraftstoffspeicher in den Entlastungsraum abfließen läßt. Das Ventilglied weist eine relativ große Länge auf und ist zylinderförmig ausgebildet, wobei es aufgrund von Form- und Lagetoleranzen des Ventilglieds und der Bohrung schwierig ist, eine definierte Führung und Anlage des Ventilglieds in der Bohrung über dessen gesamte Länge zu erreichen. Es können hierbei eine undefinierte Anlage des Ventilglieds in der Bohrung, eine Schieflage des Ventilglieds vor allem bei bestromtem Elektromagneten und bedingt hierdurch eine erhöhte Reibung zwischen dem Ventilglied und der Bohrung auftreten. Dies kann wiederum zu einer Funktionsbeeinträchtigung des Druckregelventils führen, weobei insbesondere schnelle Bewegungen des Ventilglieds beeinträchtigt sind und somit keine exakte Einstellung des Drucks im Kraftstoffspeicher erfolgen kann.Such a pressure control valve is known from the literature, for example through the specialist book Diesel Engine Management, 2nd edition, Vieweg publishing house, 1998, pages 270, 271. This Pressure control valve is used to control the pressure in one Fuel storage. The pressure control valve has one in one Axial bore against the force of a closing spring displaceably guided, piston-shaped valve member. The Valve member acts on a closing element in the closing direction of the pressure control valve and presses it against one Valve seat. The valve member forms an armature of one Electromagnet to support the power of the Closing spring is energized. Through the closing spring the closing element with a specific via the valve member Force pressed against the valve seat, the Closing element by the pressure acting on it Fuel reservoir is lifted off the valve seat when the force generated by the pressure the force of the closing spring exceeds, and fuel from the fuel storage via the open pressure control valve into a relief chamber drains away. To set a higher pressure in the Fuel is supplied to the electromagnet so that the closing force on the valve member Closing element is exercised, is increased and thus that Closing element only at a higher pressure in the The fuel accumulator lifts off the valve seat and the fuel runs out flow out of the fuel accumulator into the relief chamber leaves. The valve member has a relatively large length and is cylindrical, it is due to shape and Positional tolerances of the valve member and the bore It is difficult to have a defined management and investment Valve member in the bore over its entire length to reach. An undefined system of the Valve member in the bore, an imbalance of the Valve member especially with energized electromagnet and causes an increased friction between the Valve member and the bore occur. This, in turn, can a functional impairment of the pressure control valve lead, whereby especially rapid movements of the Valve member are impaired and therefore no exact Adjustment of the pressure in the fuel accumulator can take place.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Druckregelventil mit den Merkmalen gemäß Anspruch 1 hat demgegenüber den Vorteil, daß das Ventilglied über seine Führungsabschnitte definiert in der Bohrung geführt ist und somit die Funktionssicherheit des Druckregelventils verbessert ist.The pressure control valve according to the invention with the features according to claim 1 has the advantage that the Valve member defined via its guide sections in the Bore is guided and thus the reliability of the Pressure control valve is improved.

In den abhängigen Ansprüchen sind vorteilhafte Ausgestaltungen und Weiterbildungen des erfindungsgemäßen Druckregelventils angegeben. Durch die Ausbildung gemäß Anspruch 3 ist ein Verkanten des Ventilglieds in der Bohrung vermieden. In the dependent claims are advantageous Refinements and developments of the invention Pressure control valve specified. By training according to Claim 3 is tilting of the valve member in the bore avoided.

Zeichnungdrawing

Zwei Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 ein Druckregelventil in einem Längsschnitt, Figur 2 in vergrößerter Darstellung ein Ventilglied des Druckregelventils gemäß einem ersten Ausführungsbeispiel und Figur 3 das Ventilglied gemäß einem zweiten Ausführungsbeispiel.Two embodiments of the invention are in the Drawing shown and in the description below explained in more detail. 1 shows a pressure control valve in a longitudinal section, Figure 2 in an enlarged view Valve member of the pressure control valve according to a first Embodiment and Figure 3 shows the valve member according to a second embodiment.

Beschreibung der AusführungsbeispieleDescription of the embodiments

In Figur 1 ist ausschnittsweise ein Speicherkraftstoffeinspritzsystem für Brennkraftmaschinen, insbesondere selbstzündende Brennkraftmaschinen, dargestellt. Das Speicherkraftstoffeinspritzsystem, das auch als Common-Rail-Einspritzsystem bezeichnet wird, weist eine Hochdruckpumpe 10 auf, durch die Kraftstoff unter Hochdruck aus einem Kraftstoffvorratstank 11 in einen Kraftstoffspeicher 12 gefördert wird. Der Kraftstoffspeicher 12 ist beispielsweise röhrenförmig, als sogenanntes Rail, ausgebildet. Vom Kraftstoffspeicher 12 fahren Leitungen 14 zu den Einspritzstellen an der Brennkraftmaschine 16 ab, in denen jeweils ein Ventil 18 angeordnet ist. Zur Einstellung des Drucks im Kraftstoffspeicher 12 ist ein Druckregelventil 20 vorgesehen, das am Auslaß der Hochdruckpumpe 10 oder am Kraftstoffspeicher 12 angeordnet sein kann.In Figure 1 is a section Storage fuel injection system for internal combustion engines, especially self-igniting internal combustion engines, shown. The storage fuel injection system that too is referred to as a common rail injection system, has one High pressure pump 10 on, through the fuel under high pressure from a fuel storage tank 11 into one Fuel storage 12 is promoted. The fuel storage 12 is tubular, for example, as a so-called rail, educated. Lines 14 run from the fuel accumulator 12 to the injection points on the internal combustion engine 16, in each of which a valve 18 is arranged. For setting the pressure in the fuel accumulator 12 is a pressure control valve 20 provided that at the outlet of the high pressure pump 10 or Fuel storage 12 can be arranged.

Das Druckregelventil 20 weist einen Ventilkörper 24 auf, in dem eine Bohrung 26 ausgebildet ist, in der ein kolbenförmiges Ventilglied 28 axial verschiebbar angeordnet ist, das nachfolgend noch näher erläutert wird. Am Ventilkörper 24 ist ein Befestigungsflansch 22 ausgebildet, über den der Ventilkörper an der Hochdruckpumpe 10 oder am Kraftstoffspeicher 12 befestigt ist. Der Ventilkörper 24 weist einen die Bohrung 26 koaxial umgebenden Ringraum 30 auf, in dem ein Elektromagnet 32 mit einer Spulenwicklung angeordnet ist. Auf den Ventilkörper 24 ist ein Anschlußelement 23 aufgesteckt, der zur elektrischen Kontaktierung des Elektromagneten 32 dient. Auf der dem Anschlußelement 23 zugewandten Seite des Ventilkörpers 24 ist ein Federteller 34 angeordnet, der den Ringraum 30 überdeckt und an dessen dem Ringraum 30 abgewandter Seite sich eine vorgespannte Feder 36, die beispielsweise als Schraubendruckfeder ausgebildet ist, abstützt. Die Feder 36 stützt sich andererseits an einem mit dem Ventilkörper 24 verbundenen Deckel 38 ab, der in einen hohlzylinderförmigen Ansatz 40 des Ventilkörpers 24 eingesetzt ist. Der Ansatz 40 des Ventilkörpers 24 weist einen größeren Querschnitt auf als der Ringarum 30 und der Deckel 38 kann beispielsweise durch Umbördeln des Ansatzes 40 im Ventilkörper 24 gehalten sein. Das Ventilglied 28 ragt in den Ansatz 40 hinein aus der Bohrung 26 heraus und weist dort einen verringerten Durchmesser auf, so daß am Ventilglied 28 eine Ringschulter 42 gebildet ist. Das Ventilglied 28 ragt mit seinem Ende in eine Bohrung des Federtellers 34 hinein, der sich in axialer Richtung an der Ringschulter 42 des Ventilglieds 28 abstützt.The pressure control valve 20 has a valve body 24, in a bore 26 is formed in the one piston-shaped valve member 28 arranged axially displaceable which is explained in more detail below. At the Valve body 24 has a mounting flange 22, through which the valve body on the high pressure pump 10 or on Fuel storage 12 is attached. The valve body 24 has an annular space 30 coaxially surrounding the bore 26 in which an electromagnet 32 with a coil winding is arranged. On the valve body 24 is a Plugged connector 23, the electrical Contacting the electromagnet 32 is used. On the Connection element 23 facing side of the valve body 24 a spring plate 34 is arranged, which the annular space 30th covered and on the side facing away from the annular space 30 a biased spring 36, for example as Helical compression spring is formed, supports. The spring 36 is supported on the other hand with the valve body 24 connected lid 38, which in a hollow cylindrical Approach 40 of the valve body 24 is used. The Approach 40 of the valve body 24 has a larger cross section as the ringarum 30 and the lid 38 can for example held by flanging the extension 40 in the valve body 24 his. The valve member 28 protrudes into the extension 40 the bore 26 out and there has a reduced Diameter so that an annular shoulder on the valve member 28 42 is formed. The valve member 28 protrudes with its end in a hole in the spring plate 34, which is in axial Direction on the annular shoulder 42 of the valve member 28 supports.

Die Bohrung 26 weist in ihrem dem Ansatz 40 gegenüberliegenden Endbereich einen vergrößerten Durchmesser auf, in den ein Ventileinsatz 44 eingesetzt ist. Der Ventileinsatz 44 kann im Ventilkörper 24 beispielsweise gehalten sein, indem ein vom Ventilkörper 24 abstehender Rand über den Ventileinsatz 44 umgebördelt ist. Der Ventileinsatz 44 weist eine Bohrung 46 auf, die zumindest annähernd koaxial zur Bohrung 26 des Ventilkörpers 24 angeordnet ist und in die der Endbereich des Ventilglieds 28 hineinragt, der beispielsweise sich etwa konisch verjüngend ausgebildet sein kann. Der Durchmesser der Bohrung 46 im Ventileinsatz 44 verringert sich vom Ventilglied 28 weg, wobei am Übergang der Bohrung 46 zu ihrem kleineren Durchmesser ein Ventilsitz 48 gebildet ist, der beispielsweise etwa konisch ausgebildet sein kann. Nach dem an den Ventilsitz 48 anschließenden Abschnitt weist die Bohrung 46 wieder einen größeren Durchmesser auf. Im Ventileinsatz 44 ist ein Schließelement 50 beispielsweise in Form einer Kugel angeordnet, das mit dem Ventilsitz 48 zusammenwirkt. Der Ventileinsatz 44 weist in dem Bereich, in dem der Endbereich des Ventilglieds 28 in dessen Bohrung 46 ragt, eine oder mehrere Öffnungen 52 auf, durch die die Bohrung 46 mit der Umgebung des Ventileinsatzes 44 verbunden ist.The bore 26 has in its approach 40 opposite end region an enlarged diameter in which a valve insert 44 is inserted. The Valve insert 44 can be in valve body 24, for example be held by a protruding from the valve body 24 Edge is flanged over the valve insert 44. The Valve insert 44 has a bore 46 that at least approximately coaxial to the bore 26 of the valve body 24 is arranged and into which the end region of the valve member 28 protrudes, which tapers, for example, conically can be trained. The diameter of the bore 46 in Valve insert 44 reduces away from valve member 28, being at the transition from bore 46 to its smaller one Diameter of a valve seat 48 is formed for example, can be approximately conical. After this to the valve seat 48 section has the Bore 46 again a larger diameter. in the Valve insert 44 is a closing element 50, for example in FIG Arranged in the form of a ball, which with the valve seat 48th cooperates. The valve insert 44 points in the area in FIG the end region of the valve member 28 in its bore 46 protrudes one or more openings 52 through which the Bore 46 connected to the surroundings of the valve insert 44 is.

Das Ventilglied 28 ist in Figur 2 vergrößert gemäß einem ersten Ausführungsbeispiel dargestellt. Das Ventilglied 28 besteht beispielsweise aus Stahl und bildet einen Anker des Elektromagneten 32. Das Ventilglied weist wie bereits vorstehend erläutert an seinem in Figur 1 und 2 oberen Endbereich einen kleineren Durchmesser auf, wodurch die Ringschulter 42 gebildet ist, an der sich der Federteller 34 abstützt. Auf seinem in der Bohrung 26 angeordneten Bereich weist das Ventilglied 28 mehrere, vorzugsweise zwei in axialer Richtung zueinander versetzt angeordnete Führungsabschnitte 54 auf, die einen Durchmesser aufweisen, der nur wenig kleiner ist als der Durchmesser der Bohrung, so daß die Führungsabschnitte 54 mit geringem radialem Spiel in der Bohrung 26 angeordnet sind und das Ventilglied 28 über seine Führungsabschnitte 54 in der Bohrung verschiebbar geführt ist. Die Führungsabschnitte 54 sind als kurze Zylinderabschnitte ausgebildet und weisen in axialen Längsschnitten, das sind die Längsachse 29 des Ventilglieds 28 enthaltende Längsschnitte, gerade, parallel zur Längsachse 29 des Ventilglieds 28 verlaufende Mantellinien auf. Außerhalb der Führungsabschnitte 54 ist der Durchmesser des Ventilglieds 28 geringer als an den Führungsabschnitten 54 und deutlich geringer als der Durchmesser der Bohrung 26, so daß dort keine Anlage des Ventilglieds 28 an der Bohrung 26 gegeben ist. Der Übergang zwischen den Führungsabschnitten 54 und den übrigen Bereichen des Ventilglieds 28 kann beispielsweise wie in Figur 2 dargestellt, durch etwa konisch verlaufende Übergangsabschnitte 56 erfolgen. Das Ventilglied 28 kann beispielsweise durch Drehen hergestellt werden.The valve member 28 is enlarged in Figure 2 according to a first embodiment shown. The valve member 28 consists for example of steel and forms an anchor of the Electromagnet 32. The valve member points as before explained above at its top in Figures 1 and 2 End area has a smaller diameter, which makes the Ring shoulder 42 is formed, on which the spring plate 34th supports. On its area arranged in the bore 26 the valve member 28 has several, preferably two in axially offset from each other Guide sections 54 which have a diameter, which is only slightly smaller than the diameter of the hole, so that the guide portions 54 with little radial play are arranged in the bore 26 and the valve member 28 displaceable in the bore via its guide sections 54 is led. The guide sections 54 are short Cylinder sections formed and have axial Longitudinal sections, that is the longitudinal axis 29 of the valve member 28 containing longitudinal sections, straight, parallel to Longitudinal axis 29 of the valve member 28 extending surface lines on. Outside of the guide sections 54 is the diameter of the valve member 28 less than on the guide sections 54 and significantly smaller than the diameter of the bore 26, so that there is no contact of the valve member 28 with the bore 26 is given. The transition between the Guide sections 54 and the remaining areas of the Valve member 28 can, for example, as in FIG. 2 represented by approximately conical Transition sections 56 take place. The valve member 28 can for example by turning.

In Figur 3 ist das Ventilglied 128 gemäß einem zweiten Ausführungsbeispiel dargestellt. Das Ventilglied 128 besteht dabei wieder beispielsweise aus Stahl und bildet einen Anker des Elektromagneten 32. Das Ventilglied 128 weist in seinem in der Bohrung 26 angeordneten Bereich mehrere, vorzugsweise zwei in axialer Richtung zueinander versetzt angeordnete Führungsabschnitte 154 auf. Die Führungsabschnitte 154 weisen wiederum einen Durchmesser auf, der nur wenig kleiner ist als der Durchmesser der Bohrung, so daß die Führungsabschnitte 154 mit geringem radialem Spiel in der Bohrung 26 angeordnet sind und das Ventilglied 28 über seine Führungsabschnitte 154 in der Bohrung 26 verschiebbar geführt ist. Die Führungsabschnitte 154 sind ballig ausgebildet und weisen in axialen Längsschnitten konvex gekrümmte Mantellinien auf. Die Mantellinien der Führungsabschnitte 154 können beispielsweise zumindest annähernd als Kreisabschnitte mit einem Radius R1 ausgebildet sein. Die Übergänge zwischen den Führungsabschnitten 154 und den übrigen Bereichen des Ventilglieds 128 können gerundet sein mit in axialen Längsschnitten konkav gekrümmten Mantellinien, die beispielsweise zumindest annähernd als Kreisabschnitte mit einem Radius R2 ausgebildet sein können. Das Ventilglied 128 kann durch Drehen oder Rollen hergestellt werden. Durch die gerundeten Führungsabschnitte 154 ist ein Verkanten des Ventilglieds 128 in der Bohrung 26 mit Sicherheit vermieden.In Figure 3, the valve member 128 is according to a second Embodiment shown. The valve member 128 is made again made of steel, for example, and forms an anchor of the electromagnet 32. The valve member 128 has in its Several, preferably arranged in the bore 26 area two staggered in the axial direction Guide sections 154. The guide sections 154 again have a diameter that is only slightly smaller is than the diameter of the hole so that the Guide sections 154 with little radial play in the Bore 26 are arranged and the valve member 28 via its Guide portions 154 slidable in the bore 26 is led. The guide sections 154 are crowned formed and have convex in axial longitudinal sections curved surface lines. The surface lines of the Guide sections 154 can, for example, at least approximately as circular sections with a radius R1 be trained. The transitions between the Guide sections 154 and the remaining areas of the Valve member 128 can be rounded with in axial Longitudinal sections of concave curved surface lines that for example at least approximately as circular sections a radius R2 can be formed. The valve member 128 can be made by turning or rolling. Through the rounded guide portions 154 is a tilt of the Valve member 128 avoided in the bore 26 with certainty.

Nachfolgend wird die Funktion des Durckregelventils 20 erläutert. Wenn der Elektromagnet 32 nicht bestromt ist, so wird das Ventilglied 28 bzw. 128 durch die Feder 36, die eine Schließfeder bildet, in den Ventileinsatz 44 hineingedrückt, wobei das Ventilglied 28,128 mit seinem Stirnende am Schließelement 50 anliegt und dieses gegen den Ventilsitz 48 presst. Das Schließelement 50 ist vom Druck auf der Auslaßseite der Hochdruckpumpe 10 bzw. vom Druck im Kraftstoffspeicher 12 beaufschlagt, der auf das Schließelement 50 eine der Kraft der Schließfeder 36 entgegenwirkende Kraft erzeugt. Wenn die vom Druck erzeugte Kraft größer ist als die Kraft der Schließfeder 36, so wird das Schließelement 50 vom Ventilsitz 48 abgehoben und zusammen mit dem Ventilglied 28,128 und dem Federteller 34 verschoben. Bei geöffnetem Druckregelventil 20 strömt aus dem Kraftstoffspeicher 12 Kraftstoff durch die Bohrung 46, den Ventilsitz 48 und die Öffnungen 52 des Ventileinsatzes 44 ab in einen Entlastungsraum, beispielsweise in den Kraftstoffvorratstank 11. Wenn der Elektromagnet 32 nicht bestromt ist, so öffnet das Druckregelventil 20 bereits bei einem relativ geringen Druck im Kraftstoffspeicher, der durch die Kraft der Schließfeder 36 bestimmt ist. Wenn der Druck im Kraftstoffspeicher 12 erhöht werden soll, so wird der Elektromagnet 32 bestromt, so daß das Ventilglied 28,128 zusätzlich zu der Kraft der Schließfeder 36 auch durch die auf das Ventilglied wirkende magnetische Kraft in Schließrichtung beaufschlagt wird und das Schließelement 50 gegen den Ventilsitz 48 presst. Wenn die vom Druck im Kraftstoffspeicher 12 auf das Schließelement 50 erzeugte Kraft größer ist als die Kraft der Schließfeder 36 und die magnetische Kraft auf das Ventilglied 28,128, so öffnet das Druckregelventil 20 und bleibt in seiner geöffneten Stellung und hält den Druck im Kraftstoffspeicher 12 konstant. Eine veränderte Fördermenge der Hochdruckpumpe 10 oder eine Entnahme von Kraftstoff aus dem Kraftstoffspeicher 12 bei der Einspritzung von Kraftstoff in der Brennkraftmaschine 16 gleicht das Druckregelventil 20 durch unterschiedliche Öffnung aus. Die durch den Elektromagneten 32 auf das Ventilglied 28 bzw. 128 ausgeübte magnetische Kraft ist abhängig vom Strom, der durch den Elektromagneten 32 fließt, beispielsweise mit monoton steigender Kennlinie. Die Bestromung des Elektromagneten 32 wird durch eine Steuereinrichtung bestimmt, der Signale über verschiedene Betriebsparameter der Brennkraftmaschine 16 zugeführt werden und durch die die Stromstärke für den Elektromagneten 32 derart eingestellt wird, daß sich der für den jeweiligen Betriebszustand der Brennkraftmaschine 16 erforderliche Druck im Kraftstoffspeicher 12 einstellt. Die Stromstärke für den Elektromagneten 32 kann beispielsweise dadurch verändert werden, daß die Stromzufuhr getaktet wird, beispielsweise mit einer Pulsweitenmodulation.The function of the pressure control valve 20 is shown below explained. If the electromagnet 32 is not energized, so is the valve member 28 and 128 by the spring 36, the forms a closing spring in the valve insert 44 pressed in, the valve member 28,128 with its Front end rests on the closing element 50 and this against the Valve seat 48 presses. The closing element 50 is under pressure on the outlet side of the high pressure pump 10 or from the pressure in Fuel storage 12 acts on the Closing element 50 one of the force of the closing spring 36 counteracting force generated. If the one generated by the print Force is greater than the force of the closing spring 36, so the closing element 50 is lifted from the valve seat 48 and together with the valve member 28, 128 and the spring plate 34 postponed. When the pressure control valve 20 is open, it flows out the fuel reservoir 12 fuel through the bore 46, the valve seat 48 and the openings 52 of the valve insert 44 off into a relief room, for example in the Fuel storage tank 11. If the electromagnet 32 is not is energized, the pressure control valve 20 already opens a relatively low pressure in the fuel accumulator, the is determined by the force of the closing spring 36. If the Pressure in the fuel accumulator 12 is to be increased the electromagnet 32 is energized so that the valve member 28, 128 in addition to the force of the closing spring 36 also by the magnetic force acting on the valve member in Closing direction is applied and the closing element 50 presses against the valve seat 48. If the pressure in the Fuel accumulator 12 generated on the closing element 50 Force is greater than the force of the closing spring 36 and the magnetic force on the valve member 28, 128, so that opens Pressure control valve 20 and remains in its open position and keeps the pressure in the fuel accumulator 12 constant. A changed delivery rate of the high pressure pump 10 or a Withdrawal of fuel from the fuel accumulator 12 the injection of fuel in the internal combustion engine 16 equalizes the pressure control valve 20 by different Opening out. The by the electromagnet 32 on the Valve member 28 or 128 is applied magnetic force depending on the current flowing through the electromagnet 32, for example with a monotonically increasing characteristic curve. The Energization of the electromagnet 32 is by a Control device determines the signals over various Operating parameters of the internal combustion engine 16 are supplied and the amperage for the electromagnet 32 is set so that for each Operating state of the internal combustion engine 16 required Pressure in the fuel reservoir 12 sets. The current for the electromagnet 32, for example be changed so that the power supply is clocked, for example with pulse width modulation.

Claims (4)

Druckregelventil für ein Speicherkraftstoffeinspritzsystem für Brennkraftmaschinen zur Regelung des Druckes in einem Kraftstoffspeicher (12), mit einem in einer Bohrung (26) gegen die Kraft einer Schließfeder (36) axial verschiebbar geführten kolbenförmigen Ventilglied (28;128), das auf ein Schließelement (50) in Schließrichtung wirkt und dieses gegen einen Ventilsitz (48) presst, wobei das Ventilglied (28;128) einen Anker eines Elektromagneten (32) bildet, der zur Unterstützung der Schließkraft der Schließfeder (36) bestrombar ist, dadurch gekennzeichnet, daß das Ventilglied (28;128) in axialer Richtung zueinander versetzt angeordnete Führungsabschnitte (54;154) aufweist, über die es in der Bohrung (26) geführt ist, und daß das Ventilglied (28;128) außerhalb der Führungsabschnitte (54;154) eine kleineren Querschnitt aufweist als im Bereich der Führungsabschnitte (54;154).Pressure control valve for one Storage fuel injection system for internal combustion engines for regulating the pressure in a fuel accumulator (12), with one in a bore (26) against the force of one Closing spring (36) guided axially displaceable piston-shaped valve member (28; 128) on a Closing element (50) acts in the closing direction and this presses against a valve seat (48), the valve member (28; 128) forms an armature of an electromagnet (32) which to support the closing force of the closing spring (36) can be energized, characterized in that the valve member (28; 128) arranged offset to one another in the axial direction Guide sections (54; 154) over which it in the Bore (26) is guided, and that the valve member (28; 128) a smaller one outside the guide sections (54; 154) Cross-section than in the area of the guide sections (54; 154). Druckregelventil nach Anspruch 1, dadurch gekennzeichnet, daß die Führungsabschnitte (54) des Ventilglieds (28) als Zylinderabschnitte ausgebildet sind mit in axialen Längsschnitten geraden Mantellinien.Pressure control valve according to claim 1, characterized in that the guide portions (54) of the valve member (28) as Cylinder sections are formed with in axial Longitudinal sections of straight surface lines. Druckregelventil nach Anspruch 1, dadurch gekennzeichnet, daß die Führungsabschnitte (154) des Ventilglieds (128) ballig ausgebildet sind mit in axialen Längsschnitten konvex gekrümmten Mantellinien.Pressure control valve according to claim 1, characterized in that the guide sections (154) of the valve member (128) are convex with convex in axial longitudinal sections curved surface lines. Druckregelventil nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß das Ventilglied (28;128) zwei Führungsabschnitte (54;154) aufweist.Pressure control valve according to one of claims 1 to 3, characterized in that the valve member (28; 128) two Has guide sections (54; 154).
EP00120442A 1999-10-15 2000-09-19 Pressure regulating valve for an accumulator-type fuel injection system for internal combustion engines Withdrawn EP1092863A3 (en)

Applications Claiming Priority (2)

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DE19949814 1999-10-15
DE19949814A DE19949814A1 (en) 1999-10-15 1999-10-15 Pressure regulating valve for a storage fuel injection system for internal combustion engines

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EP1092863A2 true EP1092863A2 (en) 2001-04-18
EP1092863A3 EP1092863A3 (en) 2003-07-02

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EP (1) EP1092863A3 (en)
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US6349703B1 (en) 2002-02-26
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EP1092863A3 (en) 2003-07-02

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