EP2321519A1 - Device for supplying an internal combustion engine with fuel - Google Patents

Device for supplying an internal combustion engine with fuel

Info

Publication number
EP2321519A1
EP2321519A1 EP09780160A EP09780160A EP2321519A1 EP 2321519 A1 EP2321519 A1 EP 2321519A1 EP 09780160 A EP09780160 A EP 09780160A EP 09780160 A EP09780160 A EP 09780160A EP 2321519 A1 EP2321519 A1 EP 2321519A1
Authority
EP
European Patent Office
Prior art keywords
piston
fuel
pressure
valve
channel
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.)
Granted
Application number
EP09780160A
Other languages
German (de)
French (fr)
Other versions
EP2321519B1 (en
Inventor
Friedrich Boecking
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 EP2321519A1 publication Critical patent/EP2321519A1/en
Application granted granted Critical
Publication of EP2321519B1 publication Critical patent/EP2321519B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • 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
    • 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
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • 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
    • 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
    • F02M63/0012—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
    • F02M63/0042—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing combined with valve seats of the lift valve type
    • 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
    • F02M63/0047—Four-way valves or valves with more than four ways
    • 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
    • F02M63/0049—Combined valve units, e.g. for controlling pumping chamber and injection valve
    • 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
    • F02M63/0059—Arrangements of valve actuators
    • F02M63/0061—Single actuator acting on two or more valve bodies
    • 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
    • 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 device according to the preamble of claim 1.
  • Such a device is known from DE 102 47 564 A1.
  • the fuel is supplied to the suction valve of a high-pressure pump with the aid of a fuel pump via a metering unit depending on the needs metered, the fuel in the high-pressure pump to a pressure of up to 1600 bar compressed and a high pressure valve in one High-pressure accumulator, the so-called rail, is fed to which the injection nozzles of an internal combustion engine are connected. They bring about the actual injection of the fuel required for operation into the combustion chambers of the internal combustion engine. Depending on the speed of an internal combustion engine requires different amounts of fuel. In order to have sufficient fuel quantities available in the rail under all operating conditions, the high-pressure pump is designed to meet the greatest possible demand of the associated internal combustion engine.
  • the device according to the invention with the features according to claim 1 has the advantage that a pressure control valve and a metering unit are no longer required as independent and independent functional units, but support each other in their effect.
  • the entire functional unit is therefore extremely robust and reliable. Damage caused by overpressure in the area of the rail, the lines and the metering unit can thereby be reliably avoided.
  • advantageous refinements and developments of the device according to the invention are given.
  • the embodiment according to claim 2 has the advantage that the two valves are not able to affect their effect and that absolute tightness is ensured at least in one of the valves in the closed state.
  • the embodiment according to claim 3 and 4 have the advantage of particularly good durability and low wear.
  • the embodiment according to claim 5 has the advantage that the piston can be rotated in the cylinder, without me giving a change in reliability. This simplifies the assembly significantly.
  • the embodiment according to claim 6 describes an embodiment in which a piston of T-shaped profile is received in a cylinder of T-shaped profile adapted thereto, the recess opening as a ring cylinder when the piston is displaced in the cylinder in the longitudinal direction , In the same sense, the recess decreases when the size of the relative displacement is reduced.
  • the design is particularly easy to manufacture and assemble.
  • FIG. 9 shows the basic structure of a device according to the invention
  • FIG. 2 shows a detail of FIG. 1 in which the piston of the metering valve is surrounded by an annular groove which can be brought into coincidence with the openings of the intake line.
  • Fig. 3 shows a detail of Fig. 1, wherein the piston and the cylinder receiving it have a stepped reduced cross-section, wherein the piston enclosing a hollow cylindrical space results, which can be brought into line with the mouths of the intake line, when the piston opposite the cylinder is displaced in the longitudinal direction.
  • corresponding reference numerals designate functionally matching objects.
  • the device shown in Fig. 1 is used to supply an internal combustion engine with fuel. It comprises a fuel reservoir 1 and a high-pressure pump 2, which are connected by a suction line 3, a metering valve 4, which causes a change in the passage cross-section of the intake passage 3, a rail 5 for receiving divellbeaufmanntem fuel and a pressure control valve 6 for regulating the pressure in the Rail 5.
  • the metering valve 4 and the pressure regulating valve 6 are combined in a common housing 7 and have opposite opening directions, the metering valve 4 and the pressure regulating valve 6 have closing members 4.1, 6.1, the rigidly connected to each other and on a matching movement axis 14 are only rectified and jointly displaced. Only one of the closing members 6.1, namely that of the pressure regulating valve 6, can be applied directly to a valve seat 6.2, while the other is designed as a stopless slider 4.2. Both valves are characterized by a particularly good reliability.
  • the pressable to the valve seat 6.2 closing member 6.1 of the pressure control valve 6 is a ball. Accordingly, it is very easy to manufacture and is characterized by a particularly low wear and reliability.
  • the permeability of the pressure control valve 6 is determined by the respective distance of the ball from the associated valve seat 6.2.
  • the slide 4.2 of the metering valve 4 is formed by a longitudinally displaceable in a channel of the housing 7, longitudinally displaceable piston, wherein the housing 7 is penetrated within the longitudinal extent of the piston of a transverse bore 7.1 transverse and wherein the piston with a control edge 4.3 sealingly in front of the Channel-side inlet openings of the transverse bore 7.1 is slidable.
  • the control edge 4.3 of the piston in front of the channel-side inlet openings whose passage cross section and thus at the same time the passage cross section of the intake pipe 3 is changed.
  • the piston is provided to open the transverse bore 7.1 with at least one recess which can be brought into coincidence with the channel-side inlet openings of the transverse bore 7.1.
  • the control edge 4.3 is formed by the edge, in which the transverse bore and the lateral surface of the piston limit each other.
  • Fig. 2 shows a first design in which the piston is enclosed to form the recess of a radially outwardly open annular groove 4.4 and / or is penetrated transversely by a can be brought into coincidence with the transverse bore 7.1 supplementary bore.
  • the control edge 4.3 is included formed by a circumferential surface of the piston bounding annular surface.
  • Fig. 3 shows a second design in which the control edge 4.3 radially outwardly defines a first annular surface of the piston, which is arranged between a first axial region of the piston of a larger cross-section and a second axial region of the piston of stepped reduced cross-section, wherein the channel two Achsial Silvere has, adapted to the shape of the piston with respect to the gradation of the cross-sections and separated by a second annular surface 7.2 and wherein the recess is formed by the annular space 4.5 between the piston and the channel, which results when the annular surfaces of the piston and the Channels in the longitudinal direction have a distance L from each other.
  • the closing members 4.1, 6.1 are mechanically rigidly connected in the construction of FIG.
  • the push rod 10 encloses a magnetic coil 11 and carries an armature 12 made of iron, which is arranged in the magnetic field of the magnetic coil 11.
  • the magnetic coil 11 is acted upon by a power cable 15 with electrical voltage and actuated.
  • the push rod 10 and the armature 12 are penetrated by bores 15 in order to reduce the inertia and to improve the mobility when the cavities of the functional unit are filled with fuel as a whole. This may be convenient to avoid sealing problems over relatively moving parts.
  • a current loading of the electromagnet which can be done computer controlled, has a change in the distance between the armature 12 and the solenoid 11 result, which is used to selectively change the permeabilities of the pressure control valve 6 and the metering valve 4 as needed.
  • the solenoid 11 is effective in the design of FIG. 1 against the force of an acting on the slide 4.2 and / or the push rod 10 compression spring 13.
  • Solenoid 11 causes the compression spring a contact pressure of the closing member of the pressure control valve 6 to its valve seat and an opening of the total available passage cross section of the metering valve 4 of the intake 3.
  • the high pressure pump 2 is thereby supplied to the maximum extent with fuel and the rail 5 filled very quickly with fuel, in the rail has the necessary pressure to supply the connected internal combustion engine.
  • a Abregelung is initiated via the electromagnet, which consists in opening the pressure regulating valve at the same time to the extent necessary and close the metering valve.
  • the high-pressure pump is supplied with a correspondingly reduced amount of fuel, fed into the rail and derived therefrom in a correspondingly reduced extent.
  • the cross section of the discharge line is dimensioned so large that the maximum delivery volume of the high-pressure pump 3 can be returned as needed in total in the fuel reservoir 2. Overpressure-related damage is therefore no longer to be feared. In the rail thereby prevails at minimum drive power of the high pressure pump 2 at all speeds of the connected internal combustion engine always the operationally necessary, constant pressure.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

The invention relates to a device for supplying an internal combustion engine with fuel, comprising a fuel reservoir (1) and a high-pressure pump (2), which are connected through a suction line (3), a metering valve (4) which effects a change of the passage cross-section of the suction line (3), a rail (5) for receiving high-pressure fuel, and a pressure control valve (6) for controlling the pressure in the rail (4). The metering valve (4) and the pressure control valve (6) are combined in a common housing (7) and have opposite opening directions. The metering valve (4) and the pressure control valve (6) have closing members (4.1, 6.1) which are rigidly connected to each other and are movable on a coincident movement axis (14).

Description

Datum: 23.07.2008 Date: 23.07.2008
Anmelderin: Robert Bosch GmbH, 70442 StuttgartApplicant: Robert Bosch GmbH, 70442 Stuttgart
Titel: Vorrichtung zur Versorgung einer Verbrennungskraftmaschine mit TreibstoffTitle: Device for supplying an internal combustion engine with fuel
Beschreibungdescription
Technisches GebietTechnical area
Die Erfindung geht aus von einer Vorrichtung nach der Gattung des Anspruchs 1.The invention relates to a device according to the preamble of claim 1.
Stand der TechnikState of the art
Eine solche Vorrichtung ist aus der DE 102 47 564 A1 bekannt. Der Kraftstoff wird dabei dem Saugventil einer Hochdruckpumpe mit Hilfe einer Kraftstoffpumpe über eine Zumesseinheit in Abhängigkeit vom Bedarf dosiert zugeführt, wobei der Kraftstoff in der Hochdruckpumpe auf einen Druck von bis zu 1600 bar verdichtet und über ein Hochdruckventil in einen Hochdruckspeicher, das sogenannte Rail, eingespeist wird, an das die Einspritzdüsen einer Verbrennungskraftmaschine angeschlossen sind. Sie bewirken die eigentliche Einspritzung des zum Betrieb benötigten Kraftstoffs in die Brennräume der Verbrennungskraftmaschine. In Abhängigkeit von der Drehzahl benötigt eine Verbrennungskraftmaschine unterschiedlich große Kraftstoffmengen. Um bei allen Betriebszuständen hinreichende Kraftstoffmengen im Rail zur Verfügung zu haben, ist die Hochdruckpumpe auf den größtmöglichen Bedarf der zugehörigen Verbrennungskraftmaschine ausgelegt. Dies bedingt allerdings den Nachteil, dass im Teillastbereich unnötig große Kraftstoffmengen in das Rail gefördert und über ein Überdruckventil in das Kraftstoffreservoir zurück geleitet werden, was energetisch wenig befriedigend ist. Um diesen Nachteil zu vermeiden, wird die der Hochdruckpumpe zugeführte Kraftstoffmenge mit Hilfe der Zumesseinheit in Abhängigkeit vom jeweiligen Bedarf dosiert. Das Überdruckventil und die Zumessventil sind unabhängige, separate Funktionseinheiten. Dies erhöht das Risiko, dass im Rail ein Überdruck auftritt, und dass druckbedingte, mechanische Schäden an dem Rail, den Verbindungsleitungen und/oder der Zumesseinheit auftreten können.Such a device is known from DE 102 47 564 A1. The fuel is supplied to the suction valve of a high-pressure pump with the aid of a fuel pump via a metering unit depending on the needs metered, the fuel in the high-pressure pump to a pressure of up to 1600 bar compressed and a high pressure valve in one High-pressure accumulator, the so-called rail, is fed to which the injection nozzles of an internal combustion engine are connected. They bring about the actual injection of the fuel required for operation into the combustion chambers of the internal combustion engine. Depending on the speed of an internal combustion engine requires different amounts of fuel. In order to have sufficient fuel quantities available in the rail under all operating conditions, the high-pressure pump is designed to meet the greatest possible demand of the associated internal combustion engine. However, this entails the disadvantage that unnecessarily large amounts of fuel are conveyed into the rail in the partial load range and are conducted back into the fuel reservoir via a pressure relief valve, which is energetically less satisfactory. To avoid this disadvantage, the amount of fuel supplied to the high-pressure pump is metered with the aid of the metering unit as a function of the respective requirement. The pressure relief valve and the metering valve are independent, separate functional units. This increases the risk that overpressure will occur in the rail and that pressure-related mechanical damage to the rail, the connecting lines and / or the metering unit may occur.
Offenbarung der Erfindung Vorteile der ErfindungDisclosure of the Invention Advantages of the Invention
Die erfindungsgemäße Vorrichtung mit den Merkmalen gemäß Anspruch 1 hat den Vorteil, dass ein Druckregelventil und eine Zumesseinheit nicht mehr als selbständige und voneinander unabhängige Funktionseinheiten erforderlich sind, sondern einander in ihrer Wirkung unterstützen. Die gesamte Funktionseinheit ist daher äußerst robust und funktionssicher. Durch einen Überdruck bedingte Schäden im Bereich des RaIIs, der Leitungen und der Zumesseinheit können dadurch zuverlässig vermieden werden. In den abhängigen Ansprüchen sind vorteilhafte Ausgestaltungen und Weiterbildungen der erfindungsgemäßen Vorrichtung angegeben. Die Ausgestaltung nach Anspruch 2 hat den Vorteil, dass sich die beiden Ventile nicht in ihrer Wirkung zu beeinträchtigen vermögen und dass zumindest bei einem der Ventile im geschlossenen Zustand absolute Dichtheit gewährleistet ist.The device according to the invention with the features according to claim 1 has the advantage that a pressure control valve and a metering unit are no longer required as independent and independent functional units, but support each other in their effect. The entire functional unit is therefore extremely robust and reliable. Damage caused by overpressure in the area of the rail, the lines and the metering unit can thereby be reliably avoided. In the dependent claims advantageous refinements and developments of the device according to the invention are given. The embodiment according to claim 2 has the advantage that the two valves are not able to affect their effect and that absolute tightness is ensured at least in one of the valves in the closed state.
Die Ausgestaltung nach Anspruch 3 und 4 haben den Vorteil einer besonders guten Dauerhaltbarkeit und Verschleißarmut. Die Ausgestaltung nach Anspruch 5 hat den Vorteil, dass der Kolben in dem Zylinder verdreht werden kann, ohne dass ich eine Veränderung der Funktionssicherheit ergibt. Dies vereinfacht die Montage wesentlich. Die Ausgestaltung nach Anspruch 6 beschreibt eine Ausbildung, bei der ein Kolben von T-förmigem Profil in einem Zylinder von daran angepasstem, T- förmigem Profil aufgenommen ist, wobei sich die Ausnehmung als Ringzylinder öffnet, wenn der Kolben in dem Zylinder in Längsrichtung verschoben wird. Im selben Sinne verkleinert sich die Ausnehmung, wenn die Größe der Relativverschiebung vermindert wird. Die Bauform ist besonders einfach herzustellen und zu montieren. Wenn der Zylinder und der Kolben auf der ganzen Länge von übereinstimmendem Querschnitt sind, kann eine ähnliche Wirkung erzielt werden, wenn die Ausnehmung gemäß Anspruch 7 durch eine Ringnut und der Kolben gegebenenfalls von einer Ergänzungsbohrung quer durchdrungen ist. Am einfachsten lässt sich die starre Verbindung zwischen den Schließgliedern des Zumessventils und des Druckregelventils erzeugen, wenn die Schließglieder im Sinn des Anspruchs 8 durch eine Schubstange verbunden sind.The embodiment according to claim 3 and 4 have the advantage of particularly good durability and low wear. The embodiment according to claim 5 has the advantage that the piston can be rotated in the cylinder, without me giving a change in reliability. This simplifies the assembly significantly. The embodiment according to claim 6 describes an embodiment in which a piston of T-shaped profile is received in a cylinder of T-shaped profile adapted thereto, the recess opening as a ring cylinder when the piston is displaced in the cylinder in the longitudinal direction , In the same sense, the recess decreases when the size of the relative displacement is reduced. The design is particularly easy to manufacture and assemble. If the cylinder and the piston over the entire length of matching cross-section, a similar effect can be achieved if the recess according to claim 7 is penetrated by an annular groove and the piston optionally from a supplementary bore transversely. The simplest way to produce the rigid connection between the closing members of the metering valve and the pressure control valve, when the closing members are connected in the sense of claim 8 by a push rod.
Die Ausgestaltung nach Anspruch 9 lässt sich willkürlich sehr genau ansteuern und damit die Kraftstoffversorgung einer Verbrennungskraftmaschine sehr genau und optimal steuern. Die Ausgestaltung nach Anspruch 10 bietet dabei den Vorteil, dass der Ringmagnet nur in einer Richtung wirksam sein muss. Die genaue Ansteuerung vereinfacht sich dadurch erheblich. Zeichnung Mehrere Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen: Fig. 1 den grundsätzlichen Aufbau einer erfindungsgemäßen Vorrichtung Fig. 2 einen Ausschnitt aus Fig. 1 bei dem der Kolben des Zumessventils von einer Ringnut umschlossen ist, die mit den Mündungen der Ansaugleitung in Deckung bringbar ist.The embodiment according to claim 9 can be arbitrarily controlled very accurately and thus control the fuel supply of an internal combustion engine very accurately and optimally. The embodiment according to claim 10 offers the advantage that the ring magnet must be effective only in one direction. The exact control simplifies considerably. DRAWING Several exemplary embodiments of the invention are shown in the drawing and explained in more detail in the following description. 1 shows the basic structure of a device according to the invention, FIG. 2 shows a detail of FIG. 1 in which the piston of the metering valve is surrounded by an annular groove which can be brought into coincidence with the openings of the intake line.
Fig. 3 einen Ausschnitt aus Fig. 1 , bei der der Kolben und der ihn aufnehmende Zylinder einen abgestuft verminderten Querschnitt haben, wobei sich ein den Kolben umschließender hohlzylindrischer Raum ergibt, die mit den Mündungen der Ansaugleitung in Deckung bringbar ist, wenn der Kolben gegenüber dem Zylinder in Längsrichtung verschoben wird.Fig. 3 shows a detail of Fig. 1, wherein the piston and the cylinder receiving it have a stepped reduced cross-section, wherein the piston enclosing a hollow cylindrical space results, which can be brought into line with the mouths of the intake line, when the piston opposite the cylinder is displaced in the longitudinal direction.
Beschreibung der AusführungsbeispieleDescription of the embodiments
In den Figuren bezeichnen übereinstimmende Bezugszeichen funktionell übereinstimmende Gegenstände. Die in Fig. 1 gezeigte Vorrichtung dient zur Versorgung einer Verbrennungskraftmaschine mit Treibstoff. Sie umfasst ein Kraftstoffreservoir 1 und eine Hochdruckpumpe 2, die durch eine Ansaugleitung 3 verbunden sind, ein Zumessventil 4, das eine Veränderung des Durchtrittsquerschnittes der Ansaugleitung 3 bewirkt, ein Rail 5 zur Aufnahme von hochdruckbeaufschlagtem Kraftstoff und ein Druckregelventil 6 zur Regulierung des Druckes in dem Rail 5.In the figures, corresponding reference numerals designate functionally matching objects. The device shown in Fig. 1 is used to supply an internal combustion engine with fuel. It comprises a fuel reservoir 1 and a high-pressure pump 2, which are connected by a suction line 3, a metering valve 4, which causes a change in the passage cross-section of the intake passage 3, a rail 5 for receiving hochdruckbeaufschlagtem fuel and a pressure control valve 6 for regulating the pressure in the Rail 5.
Das Zumessventil 4 und das Druckregelventil 6 sind in einem gemeinsamen Gehäuse 7 vereint und haben entgegengesetzte Öffnungsrichtungen, wobei das Zumessventil 4 und das Druckregelventil 6 Schließglieder 4.1 , 6.1 haben, die starr miteinander verbunden und auf einer übereinstimmenden Bewegungsachse 14 nur gleichgerichtet und gemeinsam verschiebbar sind. Nur eines der Schließglieder 6.1 , nämlich dasjenige des Druckregelventils 6, ist an unmittelbar einen Ventilsitz 6.2 anlegbar, während das andere als anschlagloser Schieber 4.2 gestaltet ist. Beide Ventile zeichnen sich dadurch jeweils durch eine besonders gute Funktionssicherheit aus. Das an den Ventilsitz 6.2 anpressbare Schließglied 6.1 des Druckregelventils 6 ist eine Kugel. Es lässt sich demgemäss sehr einfach herstellen und zeichnet sich durch eine besonders hohe Verschleißarmut und Funktionssicherheit aus. Die Durchlässigkeit des Druckregelventils 6 wird durch den jeweiligen Abstand der Kugel von dem zugehörigen Ventilsitz 6.2 bestimmt. Der Schieber 4.2 des Zumessventils 4 ist durch einen in einem Kanal des Gehäuses 7 aufgenommenen, in Längsrichtung verschiebbaren Kolben gebildet, wobei das Gehäuse 7 innerhalb der Längserstreckung des Kolbens von einer Querbohrung 7.1 quer durchdrungen ist und wobei der Kolben mit einer Steuerkante 4.3 dichtend vor die kanalseitigen Eintrittsöffnungen der Querbohrung 7.1 schiebbar ist. In Abhängigkeit von der jeweiligen Lage der Steuerkante 4.3 des Kolbens vor den kanalseitigen Eintrittsöffnungen wird deren Durchtrittsquerschnitt und damit zugleich der Durchtrittsquerschnitt der Ansaugleitung 3 verändert.The metering valve 4 and the pressure regulating valve 6 are combined in a common housing 7 and have opposite opening directions, the metering valve 4 and the pressure regulating valve 6 have closing members 4.1, 6.1, the rigidly connected to each other and on a matching movement axis 14 are only rectified and jointly displaced. Only one of the closing members 6.1, namely that of the pressure regulating valve 6, can be applied directly to a valve seat 6.2, while the other is designed as a stopless slider 4.2. Both valves are characterized by a particularly good reliability. The pressable to the valve seat 6.2 closing member 6.1 of the pressure control valve 6 is a ball. Accordingly, it is very easy to manufacture and is characterized by a particularly low wear and reliability. The permeability of the pressure control valve 6 is determined by the respective distance of the ball from the associated valve seat 6.2. The slide 4.2 of the metering valve 4 is formed by a longitudinally displaceable in a channel of the housing 7, longitudinally displaceable piston, wherein the housing 7 is penetrated within the longitudinal extent of the piston of a transverse bore 7.1 transverse and wherein the piston with a control edge 4.3 sealingly in front of the Channel-side inlet openings of the transverse bore 7.1 is slidable. Depending on the respective position of the control edge 4.3 of the piston in front of the channel-side inlet openings whose passage cross section and thus at the same time the passage cross section of the intake pipe 3 is changed.
Der Kolben ist zum Öffnen der Querbohrung 7.1 mit zumindest einer Ausnehmung versehen, die in Deckung mit den kanalseitigen Eintrittsöffnungen der Querbohrung 7.1 bringbar ist. Die Steuerkante 4.3 ist dabei durch die Kante gebildet, in der sich die Querbohrung und die Mantelfläche des Kolbens gegenseitig begrenzen.The piston is provided to open the transverse bore 7.1 with at least one recess which can be brought into coincidence with the channel-side inlet openings of the transverse bore 7.1. The control edge 4.3 is formed by the edge, in which the transverse bore and the lateral surface of the piston limit each other.
Fig. 2 zeigt eine erste Bauform, bei der der Kolben zur Bildung der Ausnehmung von einer radial nach außen offenen Ringnut 4.4 umschlossen und/oder von einer mit der Querbohrung 7.1 in Deckung bringbaren Ergänzungsbohrung quer durchdrungen ist. Die Steuerkante 4.3 ist dabei durch eine die Mantelfläche des Kolbens begrenzende Kreisringsfläche gebildet.Fig. 2 shows a first design in which the piston is enclosed to form the recess of a radially outwardly open annular groove 4.4 and / or is penetrated transversely by a can be brought into coincidence with the transverse bore 7.1 supplementary bore. The control edge 4.3 is included formed by a circumferential surface of the piston bounding annular surface.
Fig. 3 zeigt eine zweite Bauform, bei der die Steuerkante 4.3 eine erste Kreisringsfläche des Kolbens radial außenseitig begrenzt, die zwischen einem ersten Axialbereich des Kolbens eines größeren Querschnittes und einem zweiten Axialbereich des Kolbens von abgestuft verringertem Querschnitt angeordnet ist, wobei der Kanal zwei Achsialbereiche aufweist, die hinsichtlich der Abstufung der Querschnitte an die Gestalt des Kolbens angepasst und durch eine zweite Kreisringsfläche 7.2 getrennt sind und wobei die Ausnehmung durch den Ringraum 4.5 zwischen dem Kolben und dem Kanal gebildet ist, der sich ergibt, wenn die Kreisringflächen des Kolbens und des Kanals in Längsrichtung einen Abstand L von einander haben. Die Schließglieder 4.1 , 6.1 sind bei der Bauform nach Fig. 1 durch eine Schubstange 10 mechanisch starr verbunden. Dies erübrigt eine besondere Justierung. Die Schubstange 10 umschließt eine Magnetspule 11 und trägt einen Anker 12 aus Eisen, der in dem Magnetfeld der Magnetspule 11 angeordnet ist. Die Magnetspule 11 ist durch ein Stromkabel 15 mit elektrischer Spannung beaufschlag- und betätigbar. Die Schubstange 10 und der Anker 12 sind von Bohrungen 15 durchdrungen, um die Trägheitsmarse zu vermindern und die Beweglichkeit zu verbessern, wenn die Hohlräume der Funktionseinheit insgesamt mit Kraftstoff gefüllt sind. Dies kann zweckmäßig sein, um Abdichtungsprobleme gegenüber relativ bewegten Teilen zu vermeiden. Eine Strombeaufschlagung des Elektromagneten, die computergesteuert erfolgen kann, hat eine Veränderung des Abstandes zwischen dem Anker 12 und der Magnetspule 11 zur Folge, die dazu genutzt wird, die Durchlässigkeiten des Druckregelventils 6 und des Zumessventils 4 nach Bedarf gezielt zu verändern. Die Magnetspule 11 ist bei der Bauform nach Fig. 1 gegen die Kraft einer an dem Schieber 4.2 und/oder der Schubstange 10 angreifenden Druckfeder 13 wirksam. Bei unbeschalteter Magnetspule 11 bewirkt die Druckfeder eine Anpressung des Schließglieds des Druckregelventils 6 an seinen Ventilsitz und eine Öffnung des insgesamt verfügbaren Durchtrittsquerschnittes des Zumessventils 4 der Ansaugleitung 3. Die Hochdruckpumpe 2 wird dadurch im größtmöglichen Maße mit Kraftstoff versorgt und das Rail 5 sehr schnell mit Kraftstoff gefüllt, der in dem Rail den notwendigen Druck zur Versorgung der angeschlossenen Verbrennungskraftmaschine aufweist. Ist dieser Druck erreicht, dann wird über den Elektromagneten eine Abregelung eingeleitet, die darin besteht, zugleich das Druckregelventil im erforderlichen Maße zu öffnen und das Zumessventil zu schließen. Der Hochdruckpumpe wird eine entsprechend reduzierte Menge des Kraftstoffs zugeführt, in das Rail eingespeist und daraus in entsprechend vermindertem Umfang abgeleitet. Der Querschnitt der Entlastungsleitung ist so groß bemessen, dass das maximale Fördervolumen der Hochdruckpumpe 3 bei Bedarf insgesamt darüber in das Kraftstoffreservoir 2 zurückgeleitet werden kann. Überdruckbedingte Schäden sind daher nicht mehr zu befürchten. In dem Rail herrscht dadurch bei minimaler Antriebsleistung der Hochdruckpumpe 2 bei allen Drehzahlen der angeschlossenen Verbrennungskraftmaschine immer der betriebsnotwendige, konstante Druck. Fig. 3 shows a second design in which the control edge 4.3 radially outwardly defines a first annular surface of the piston, which is arranged between a first axial region of the piston of a larger cross-section and a second axial region of the piston of stepped reduced cross-section, wherein the channel two Achsialbereiche has, adapted to the shape of the piston with respect to the gradation of the cross-sections and separated by a second annular surface 7.2 and wherein the recess is formed by the annular space 4.5 between the piston and the channel, which results when the annular surfaces of the piston and the Channels in the longitudinal direction have a distance L from each other. The closing members 4.1, 6.1 are mechanically rigidly connected in the construction of FIG. 1 by a push rod 10. This eliminates a special adjustment. The push rod 10 encloses a magnetic coil 11 and carries an armature 12 made of iron, which is arranged in the magnetic field of the magnetic coil 11. The magnetic coil 11 is acted upon by a power cable 15 with electrical voltage and actuated. The push rod 10 and the armature 12 are penetrated by bores 15 in order to reduce the inertia and to improve the mobility when the cavities of the functional unit are filled with fuel as a whole. This may be convenient to avoid sealing problems over relatively moving parts. A current loading of the electromagnet, which can be done computer controlled, has a change in the distance between the armature 12 and the solenoid 11 result, which is used to selectively change the permeabilities of the pressure control valve 6 and the metering valve 4 as needed. The solenoid 11 is effective in the design of FIG. 1 against the force of an acting on the slide 4.2 and / or the push rod 10 compression spring 13. At undeclared Solenoid 11 causes the compression spring a contact pressure of the closing member of the pressure control valve 6 to its valve seat and an opening of the total available passage cross section of the metering valve 4 of the intake 3. The high pressure pump 2 is thereby supplied to the maximum extent with fuel and the rail 5 filled very quickly with fuel, in the rail has the necessary pressure to supply the connected internal combustion engine. If this pressure is reached, then a Abregelung is initiated via the electromagnet, which consists in opening the pressure regulating valve at the same time to the extent necessary and close the metering valve. The high-pressure pump is supplied with a correspondingly reduced amount of fuel, fed into the rail and derived therefrom in a correspondingly reduced extent. The cross section of the discharge line is dimensioned so large that the maximum delivery volume of the high-pressure pump 3 can be returned as needed in total in the fuel reservoir 2. Overpressure-related damage is therefore no longer to be feared. In the rail thereby prevails at minimum drive power of the high pressure pump 2 at all speeds of the connected internal combustion engine always the operationally necessary, constant pressure.

Claims

Ansprüche: Claims:
1 . Vorrichtung zur Versorgung einer Verbrennungskraftmaschine mit Treibstoff, umfassend ein Kraftstoffreservoir (1 ) und eine1 . Apparatus for supplying an internal combustion engine with fuel, comprising a fuel reservoir (1) and a
Hochdruckpumpe (2), die durch eine Ansaugleitung (3) verbunden sind, ein Zumessventil (4), das eine Veränderung des Durchtrittsquerschnittes der Ansaugleitung (3) bewirkt, einem Rail (5) zur Aufnahme von hochdruckbeaufschlagtem Kraftstoff und ein Druckregelventil (6) zur Regulierung des Druckes in dem Rail (5), dadurch gekennzeichnet, dass das Zumessventil (4) und das Druckregelventil (6) in einem gemeinsamen Gehäuse (7) vereint sind und entgegengesetzte Öffnungsrichtungen haben und dass das Zumessventil (4) und das Druckregelventil (6) Schließglieder (4.1 , 6.1 ) haben, die starr miteinander verbunden und auf einer übereinstimmendenHigh pressure pump (2), which are connected by a suction line (3), a metering valve (4), which causes a change in the passage cross section of the intake passage (3), a rail (5) for receiving high pressure fuel and a pressure control valve (6) Regulation of the pressure in the rail (5), characterized in that the metering valve (4) and the pressure regulating valve (6) are united in a common housing (7) and have opposite opening directions and that the metering valve (4) and the pressure regulating valve (6 ) Have closing links (4.1, 6.1), which are rigidly connected to each other and on a matching
Bewegungsachse (14) verschiebbar sind.Movement axis (14) are displaceable.
2. Vorrichtung nach Anspruch 1 , dadurch gekennzeichnet, dass nur eines der Schließglieder (6.1 ) an einen Ventilsitz (6.2) anlegbar und das andere als anschlagloser Schieber (4.2) gestaltet ist. 2. Apparatus according to claim 1, characterized in that only one of the closing members (6.1) to a valve seat (6.2) can be applied and the other designed as an impact-free slide (4.2).
3. Vorrichtung nach Anspruch 2, dadurch gekennzeichnet, dass das an den Ventilsitz (6.2) anpressbare Schließglied (6.1 ) eine Kugel ist. 3. A device according to claim 2, characterized in that the valve seat (6.2) can be pressed against the closing member (6.1) is a ball.
4. Vorrichtung nach Anspruch 2, dadurch gekennzeichnet, dass der Schieber (4.2) durch einen in einem Kanal des Gehäuses (7) aufgenommenen, in Längsrichtung verschiebbaren Kolben gebildet ist, dass das Gehäuse (7) innerhalb der Längserstreckung des Kolbens von einer Querbohrung (7.1 ) quer durchdrungen ist und dass der Kolben mit einer Steuerkante (4.3) dichtend vor die kanalseitigen Austrittsöffnungen der Querbohrung (7.1 ) schiebbar ist. 4. The device according to claim 2, characterized in that the slide (4.2) by a in a channel of the housing (7) received, longitudinally displaceable piston is formed, that the housing (7) within the longitudinal extent of the piston of a transverse bore ( 7.1) is penetrated transversely and that the piston with a control edge (4.3) sealingly in front of the channel-side outlet openings of the transverse bore (7.1) is slidable.
5. Vorrichtung nach Anspruch 4, dadurch gekennzeichnet, dass die Steuerkante (4.3) eine radial nach außen offene Ringnut (4.4) des Kolbens begrenzt und den Kolben nach Art einer Kreisringfläche ganz umschließt. 5. Apparatus according to claim 4, characterized in that the control edge (4.3) defines a radially outwardly open annular groove (4.4) of the piston and the piston in the manner of a circular ring surface completely encloses.
6. Vorrichtung nach Anspruch 4, dadurch gekennzeichnet, dass die Steuerkante (4.3) eine erste Kreisringsfläche des Kolbens radial außenseitig begrenzt, die zwischen einem ersten Axialbereich des Kolbens eines größeren Querschnittes und einem zweiten Axialbereich von abgestuft verringertem Querschnitt angeordnet ist, dass der Kanal zwei Achsialbereiche aufweist, die hinsichtlich der Abstufung der6. The device according to claim 4, characterized in that the control edge (4.3) radially outwardly limits a first annular surface of the piston, which is arranged between a first axial region of the piston of a larger cross-section and a second axial region of stepped reduced cross-section that the channel two Achsialbereiche, with respect to the gradation of
Querschnitte an die Gestalt des Kolbens angepasst und durch eine zweite Kreisringsfläche (7.2) getrennt sind, dass die Ausnehmung durch den Ringraum (4.5) zwischen dem Kolben und dem Kanal gebildet ist, der sich ergibt, wenn die Kreisringflächen (4.3, 7.2) des Kolbens und des Kanals in Längsrichtung einen Abstand L von einander haben.Cross-sections adapted to the shape of the piston and separated by a second annular surface (7.2), that the recess through the annular space (4.5) between the piston and the channel is formed, which results when the annular surfaces (4.3, 7.2) of the piston and the channel in the longitudinal direction have a distance L from each other.
7. Vorrichtung nach Anspruch 5, dadurch gekennzeichnet, dass der Kolben zur Bildung der Ausnehmung von einer Ringnut (4.4) umschlossen und/oder von einer mit der Querbohrung (7.1 ) in Deckung bringbaren Ergänzungsbohrung quer durchdrungen ist. 7. The device according to claim 5, characterized in that the piston for forming the recess of an annular groove (4.4) enclosed and / or is penetrated transversely by a transverse bore (7.1) engageable with the supplementary bore.
8. Vorrichtung nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, dass die Schließglieder (4.1 , 6.1 ) durch eine Schubstange (10) starr verbunden sind.8. Device according to one of claims 1 to 7, characterized in that the closing members (4.1, 6.1) are rigidly connected by a push rod (10).
9. Vorrichtung nach Anspruch 8, dadurch gekennzeichnet, dass die Schubstange (10) eine Magnetspule (1 1 ) umschließt und einen Anker (12) trägt, der in dem Magnetfeld der Magnetspule (1 1 ) angeordnet ist.9. Apparatus according to claim 8, characterized in that the push rod (10) encloses a magnetic coil (1 1) and carries an armature (12) which is arranged in the magnetic field of the magnetic coil (1 1).
10.Vorrichtung nach Anspruch 9, dadurch gekennzeichnet, dass die Magnetspule (1 1 ) gegen die Kraft einer an dem Schieber (4.2) und/oder der Schubstange (10) angreifenden Druckfeder (13) wirksam ist. 10.Vorrichtung according to claim 9, characterized in that the magnetic coil (1 1) against the force of a on the slide (4.2) and / or the push rod (10) acting compression spring (13) is effective.
EP09780160.9A 2008-08-20 2009-07-06 Device for supplying an internal combustion engine with fuel Not-in-force EP2321519B1 (en)

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Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010043092A1 (en) * 2010-10-29 2012-05-03 Robert Bosch Gmbh Pressure control valve
GB201100480D0 (en) * 2011-01-12 2011-02-23 Delphi Technologies Holding Valve assembly
CN104214031A (en) * 2014-08-05 2014-12-17 中国第一汽车股份有限公司无锡油泵油嘴研究所 Common rail pump metering valve
CN106121890B (en) * 2016-07-26 2017-05-10 北京理工大学 Rail pressure regulating valve for common-rail system

Family Cites Families (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3531936A (en) 1968-12-20 1970-10-06 Bendix Corp Integrating fluid meter with phase lead
JPS50219B1 (en) * 1970-04-24 1975-01-07
US4213741A (en) 1978-10-13 1980-07-22 The Bendix Corporation Variable flow ejector
JPS6065271A (en) * 1983-09-19 1985-04-15 Nippon Soken Inc Fuel injector of internal-combustion engine
US5207203A (en) * 1992-03-23 1993-05-04 General Motors Corporation Fuel system
US5558068A (en) * 1994-05-31 1996-09-24 Zexel Corporation Solenoid valve unit for fuel injection apparatus
JP2681617B2 (en) * 1995-01-09 1997-11-26 株式会社ゼクセル Solenoid valve unit for fuel injection device
DE19625698B4 (en) * 1996-06-27 2005-09-22 Robert Bosch Gmbh Injection device for the combined injection of fuel and additional fluid
DE19646581A1 (en) * 1996-11-12 1998-05-14 Bosch Gmbh Robert Fuel injection system
JP3704878B2 (en) * 1997-04-03 2005-10-12 いすゞ自動車株式会社 Fuel injection system
IT1296144B1 (en) * 1997-11-18 1999-06-09 Elasis Sistema Ricerca Fiat ADJUSTABLE DOSING VALVE FOR ONE FUEL INJECTOR FOR INTERNAL COMBUSTION ENGINES.
WO2000050764A1 (en) * 1999-02-24 2000-08-31 Siemens Aktiengesellschaft Regulating mechanism for controlling increasing pressure of fuel for a fuel injector
DE10247564A1 (en) 2002-10-11 2004-04-22 Robert Bosch Gmbh Operating common rail fuel injection system for combustion engine involves driving pressure regulating valve if fuel quantity less than threshold so defined leakage occurs at pressure regulating valve
DE10332484A1 (en) * 2003-07-17 2005-02-10 Robert Bosch Gmbh Fuel injection system for internal combustion engines
GB0417034D0 (en) * 2004-07-30 2004-09-01 Goodrich Control Sys Ltd Pressure regulator
JP4404056B2 (en) * 2006-02-08 2010-01-27 株式会社デンソー Fuel injection device for internal combustion engine
FR2897116B1 (en) * 2006-02-08 2013-04-26 Denso Corp FUEL INJECTION SYSTEM FOR INTERNAL COMBUSTION ENGINE
JP5250751B2 (en) * 2006-10-11 2013-07-31 セミコンダクター・コンポーネンツ・インダストリーズ・リミテッド・ライアビリティ・カンパニー Voltage generation circuit
ATE531928T1 (en) * 2006-11-16 2011-11-15 Fiat Ricerche FUEL ADJUSTMENT AND FUEL FILTER DEVICE FOR A HIGH PRESSURE PUMP

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2010020464A1 *

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EP2321519B1 (en) 2013-06-26
US8464692B2 (en) 2013-06-18
CN102124203A (en) 2011-07-13
RU2501968C2 (en) 2013-12-20
CN102124203B (en) 2013-09-18
KR101574823B1 (en) 2015-12-04
DE102008041384A1 (en) 2010-02-25
KR20110042081A (en) 2011-04-22
JP2012500359A (en) 2012-01-05
WO2010020464A1 (en) 2010-02-25
US20110192377A1 (en) 2011-08-11
RU2011110113A (en) 2012-09-27
JP5599399B2 (en) 2014-10-01

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