EP1283956B1 - Fuel-injection system for internal combustion engines - Google Patents

Fuel-injection system for internal combustion engines Download PDF

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Publication number
EP1283956B1
EP1283956B1 EP01943031A EP01943031A EP1283956B1 EP 1283956 B1 EP1283956 B1 EP 1283956B1 EP 01943031 A EP01943031 A EP 01943031A EP 01943031 A EP01943031 A EP 01943031A EP 1283956 B1 EP1283956 B1 EP 1283956B1
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EP
European Patent Office
Prior art keywords
fuel
valve
valve piston
pressure pump
regulating valve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
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EP01943031A
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German (de)
French (fr)
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EP1283956A1 (en
Inventor
Martin Boehm
Rainer Haeberer
Helmut Clauss
Felix LANDHÄUSSER
Markus Rueckle
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP1283956A1 publication Critical patent/EP1283956A1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/34—Varying fuel delivery in quantity or timing by throttling of passages to pumping elements or of overflow passages, e.g. throttling by means of a pressure-controlled sliding valve having liquid stop or abutment
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails

Definitions

  • the invention relates to a fuel injection system for internal combustion engines according to the preamble of claim 1.
  • Such a fuel injection system is known from JP 602 287 33.
  • This fuel injection system has a high-pressure pump driven by the engine speed and a fuel metering unit associated therewith, which is based on an electromagnetically actuated control valve and by means of which the fuel quantity delivered by the high-pressure pump is adjustable.
  • the high pressure pump may be adapted to generate a required fuel pressure and flow rate in a manifold.
  • the fuel metering unit is disposed in the high pressure pump.
  • the output of the control valve opens into the low-pressure region of the high-pressure pump and the input of the control valve is connected to the pressure side of a prefeed pump.
  • the control valve has a by a compression spring to a closed position acted upon valve piston which is actuated by an anchor bolt of the electromagnet to an open position against the spring force.
  • a plurality of radial control openings are arranged, which are in operative connection with the suction side of the high-pressure pump.
  • the fuel injection system according to the invention with the features according to claim 1 has the advantage that targeted by the at least one specially shaped control opening in cooperation with the annular channel a certain throughput characteristic can be realized.
  • 10 denotes an electromagnet with integrated control valve 11.
  • the solenoid 10 has a magnetic coil 12, an armature 13 with anchor bolt 14 and a magnet pot 15 on. The latter encloses - in part - the magnetic coil 12 and the armature 13th
  • a plug-shaped power terminal 101 is provided in a connector housing 100 integrally connected to the magnet pot 15, a plug-shaped power terminal 101 is provided.
  • the assembly of solenoid 10 with integrated control valve 11 is integrated in a high-pressure fuel pump (not shown).
  • An encapsulation 17 ensures optimum heat transfer from the coil 12 to the housing 15.
  • Two sealing points 18, 19, together with the magnet coil 12, ensure that the magnet coil winding and contact points of the coil 12 are optimally protected against attack by corrosive media.
  • the control valve 11 has a valve housing 20, which merges into a flange-like widening 21, which also forms the end-side termination of the Eleketromagnetgepuruses 15.
  • a valve housing 20 which merges into a flange-like widening 21, which also forms the end-side termination of the Eleketromagnetgepuruses 15.
  • an axial bore 22 is formed, which is arranged coaxially with the anchor bolt 14 of the electromagnet 10.
  • the axial bore 22 receives a displaceable sleeve-shaped valve piston 23, in whose interior 24 a compression spring 25 is arranged.
  • the compression spring 25 is supported on the inside of the valve piston 23 and with its other end on a located in the axial bore 22 of the valve housing 20 securing element 26 from.
  • the valve piston 23 On the outside, the valve piston 23 is in contact with the front end of the anchor bolt 14.
  • the control valve 11 is sealed off from the fuel supply channel having a material of the (not shown) high-pressure pump by two sealing rings 27, 28.
  • the valve housing 20 has a plurality of radially arranged, preferably oppositely paired inlet openings 32, 33 which are in hydraulic operative connection with a (not shown) prefeed pump of the fuel injection system.
  • the inlet openings 32, 33 open into an annular channel 34 a.
  • radial control openings 35 are arranged, the channel 34 and the inlet openings 32, 33 cooperate with the ring by, depending on the position of the valve piston 23 (see., In each case in Fig. 1 and 2, respectively, two possible two piston positions indicated) - Release or close the inlet in the valve interior 22, 24.
  • the fuel which has reached the valve interior 22, 24 is discharged in the axial direction (arrow 31) through a stepped bore 36, which is hydraulically connected to the high-pressure pump inlet (low-pressure region of the high-pressure pump).
  • the bore 36 is incorporated in the already mentioned securing element 26, which forms the lower end of the valve housing 20.
  • Fig. 2 reveals the particular design of the control port 35, from which - in conjunction with the lifting movement of the valve piston 23 - the graph shown in FIG. 3 throughput characteristic results.
  • the control opening 35 preferably has an (upper) slot-shaped and a (lower) approximately rectangular area.
  • the upper end position (open position) of the valve piston 23 - see the right half of the figure in FIG. 2 (or in FIG. 1) - the widened rectangular area of the control opening 35 comes into play. This means maximum fuel flow rate through the valve 11.
  • This state is indicated in FIGS. 2 and 3 by an arrow 37 in each case.
  • control opening 35 As an alternative to the geometry of the control opening 35 shown in FIG. 2 and described above, however, different designs of the control opening 35 are still possible. For example, it is conceivable to make the control opening trapezoidal and thus allow others, e.g. to realize linear, throughput characteristics. The apparent from Fig. 3 throughput characteristic, however, is characterized by a stepped course.

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  • 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)

Description

Die Erfindung betrifft ein Kraftstoffeinspritzsystem für Brennkraftmaschinen nach der Gattung des Anspruchs 1.The invention relates to a fuel injection system for internal combustion engines according to the preamble of claim 1.

Ein solches Kraftstoffeinspritzsystem ist durch die JP 602 287 33 bekannt. Dieses Kraftstoffeinspritzsystem weist eine motordrehzahlabhängig angetriebene Hochdruckpumpe und eine dieser zugeordnete Kraftstoffzumesseinheit auf, die auf einem elektromagnetisch betätigten Regelventil basiert und durch die die durch die Hochdruckpumpe geförderte Kraftstoffmenge verstellbar ist. Die Hochdruckpumpe kann dazu vorgesehen sein, in einem Verteilerrohr einen benötigten Kraftstoffdruck und -durchsatz zu erzeugen. Die Kraftstoffzumesseinheit ist in der Hochdruckpumpe angeordnet. Der Ausgang des Regelventils mündet in den Niederdruckbereich der Hochdruckpumpe und der Eingang des Regelventils ist mit der Druckseite einer Vorförderpumpe verbunden. Das Regelventil weist einen durch eine Druckfeder zu einer Schließstellung hin beaufschlagten Ventilkolben auf, der durch einen Ankerbolzen des Elektromagneten zu einer Öffnungsstellung hin entgegen der Federkraft betätigbar ist. Im Ventilkolben sind mehrere radiale Steueröffnungen angeordnet, die mit der Saugseite der Hochdruckpumpe in Wirkverbindung stehen. Durch das Regelventil kann die Verbindung des Niederdruckbereichs der Hochdruckpumpe mit der Vorförderpumpe geöffnet und geschlossen werden, wobei jedoch keine definierte Durchsatzcharakteristik eingestellt werden kann.Such a fuel injection system is known from JP 602 287 33. This fuel injection system has a high-pressure pump driven by the engine speed and a fuel metering unit associated therewith, which is based on an electromagnetically actuated control valve and by means of which the fuel quantity delivered by the high-pressure pump is adjustable. The high pressure pump may be adapted to generate a required fuel pressure and flow rate in a manifold. The fuel metering unit is disposed in the high pressure pump. The output of the control valve opens into the low-pressure region of the high-pressure pump and the input of the control valve is connected to the pressure side of a prefeed pump. The control valve has a by a compression spring to a closed position acted upon valve piston which is actuated by an anchor bolt of the electromagnet to an open position against the spring force. In the valve piston, a plurality of radial control openings are arranged, which are in operative connection with the suction side of the high-pressure pump. Through the control valve, the connection of the low pressure region of the high-pressure pump can be opened and closed with the prefeed pump, but no defined flow rate characteristic can be adjusted.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Kraftstoffeinspritzsystem mit den Merkmalen gemäß Anspruch 1 hat demgegenüber den Vorteil, dass durch die wenigstens eine besonders geformte Steueröffnung in Zusammenwirkung mit dem Ringkanal gezielt eine bestimmte Durchsatzcharakteristik realisiert werden kann.The fuel injection system according to the invention with the features according to claim 1 has the advantage that targeted by the at least one specially shaped control opening in cooperation with the annular channel a certain throughput characteristic can be realized.

In den abhängigen Ansprüchen sind vorteilhafte Ausgestaltungen und Weiterbildungen des erfindungsgemäßen Kraftstoffeinspritzsystems angegeben.In the dependent claims advantageous refinements and developments of the fuel injection system according to the invention are given.

Zeichnungendrawings

Zur näheren Erläuterung der Erfindung dient ein Ausführungsbeispiel, das in der Zeichnung dargestellt und nachstehend detailliert beschrieben ist. Es zeigt:

  • Fig. leine Ausführungsform einer Kraftstoffzumesseinheit, im vertikalen Längsschnitt,
  • Fig. 2 die Einzelheit "A" aus Fig. 1 in gegenüber Fig. 1 vergrößerter Darstellung, und
  • Fig. 3 ein Diagramm, worin der Kraftstoffdurchsatz (Q) über dem Magnethub (I) aufgetragen ist.
For a more detailed explanation of the invention is an embodiment which is illustrated in the drawings and described in detail below. It shows:
  • Fig. Line embodiment of a Kraftstoffzumesseinheit, in vertical longitudinal section,
  • Fig. 2 shows the detail "A" of FIG. 1 in relation to FIG. 1 enlarged representation, and
  • Fig. 3 is a diagram in which the fuel flow rate (Q) is plotted against the Magnetethub (I).

Beschreibung des AusführungsbeispielsDescription of the embodiment

In Fig. 1 und - teilweise - auch in Fig. 2 bezeichnet 10 einen Elektromagneten mit integriertem Regelventil 11. Der Elektromagnet 10 weist eine Magnetspule 12, einen Anker 13 mit Ankerbolzen 14 und einen Magnettopf 15 auf. Letzerer umschliesst - teilweise - die Magnetspule 12 und den Anker 13.In Fig. 1 and - partially - also in Fig. 2, 10 denotes an electromagnet with integrated control valve 11. The solenoid 10 has a magnetic coil 12, an armature 13 with anchor bolt 14 and a magnet pot 15 on. The latter encloses - in part - the magnetic coil 12 and the armature 13th

In einem einstückig mit dem Magnettopf 15 verbundenen Steckergehäuse 100 ist ein steckerförmiger Stromanschluss 101 vorgesehen. Die Baueinheit Elektromagnet 10 mit integriertem Regelventil 11 ist in einer Kraftstoff-Hochdruckpumpe (nicht gezeigt) integriert. Durch eine Umspritzung 17 ist ein optimaler Wärmeübergang von der Spule 12 an das Gehäuse 15 gewährleistet. Zwei Abdichtstellen 18, 19 gewährleisten zusammen mit der Magnetspule 12, dass Magnetspulenwicklung und Kontaktstellen der Spule 12 vor Angriffen korrosiver Medien optimal geschützt sind.In a connector housing 100 integrally connected to the magnet pot 15, a plug-shaped power terminal 101 is provided. The assembly of solenoid 10 with integrated control valve 11 is integrated in a high-pressure fuel pump (not shown). An encapsulation 17 ensures optimum heat transfer from the coil 12 to the housing 15. Two sealing points 18, 19, together with the magnet coil 12, ensure that the magnet coil winding and contact points of the coil 12 are optimally protected against attack by corrosive media.

Das Regelventil 11 besitzt ein Ventilgehäuse 20, welches in eine flanschartige Verbreiterung 21 übergeht, die zugleich den stirnseitigen Abschluss des Eleketromagnetgehäuses 15 bildet. In dem Ventilgehäuse 20 ist eine Axialbohrung 22 ausgebildet, die koaxial zu dem Ankerbolzen 14 des Elektromagneten 10 angeordnet ist. Die Axialbohrung 22 nimmt einen verschieblichen hülsenförmigen Ventilkolben 23 auf, in dessen Innenraum 24 eine Druckfeder 25 angeordnet ist. Die Druckfeder 25 stützt sich innenseitig an dem Ventilkolben 23 und mit ihrem anderen Ende an einem in der Axialbohrung 22 des Ventilgehäuses 20 befindlichen Sicherungselement 26 ab. Aussenseitig steht der Ventilkolben 23 mit dem vorderen Ende des Ankerbolzens 14 in Anlage.The control valve 11 has a valve housing 20, which merges into a flange-like widening 21, which also forms the end-side termination of the Eleketromagnetgehäuses 15. In the valve housing 20, an axial bore 22 is formed, which is arranged coaxially with the anchor bolt 14 of the electromagnet 10. The axial bore 22 receives a displaceable sleeve-shaped valve piston 23, in whose interior 24 a compression spring 25 is arranged. The compression spring 25 is supported on the inside of the valve piston 23 and with its other end on a located in the axial bore 22 of the valve housing 20 securing element 26 from. On the outside, the valve piston 23 is in contact with the front end of the anchor bolt 14.

Das Regelventil 11 ist gegenüber dem einen Kraftstoff-Zulaufkanal aufweisenden Material der (nicht dargestellten) Hochdruckpumpe durch zwei Dichtringe 27, 28 abgedichtet.The control valve 11 is sealed off from the fuel supply channel having a material of the (not shown) high-pressure pump by two sealing rings 27, 28.

Zwei Pfeile 29, 30 kennzeichnen den Kraftstoffzulauf zu dem Regelventil 11, und ein Pfeil 31 markiert den Kraftstoffablauf aus dem Regelventil 11. Die Pfeile 29, 30, 31 markieren somit zugleich das bei der dargestellten Kraftstoff-Zumesseinrichtung gewählte sogenannte "umgekehrte" Durchströmprinzip. Hierfür weist das Ventilgehäuse 20 mehrere radial angeordnete, vorzugsweise gegenständig gepaarte Zulauföffnungen 32, 33 auf, die mit einer (nicht dargestellten) Vorförderpumpe des Kraftstoffeinspritzsystems in hydraulischer Wirkverbindung stehen. Die Zulauf öffnungen 32, 33 münden in einen Ringkanal 34 ein. Im Ventilkolben 23 sind radiale Steueröffnungen 35 angeordnet, die mit dem Ring kanal 34 und den Zulauföffnungen 32, 33 zusammenwirken, indem sie - je nach Stellung des Ventilkolbens 23 (vgl. hierzu die in Fig. 1 und 2 jeweils hälftig angedeuteten zwei möglichen Kolbenstellungen) - den Zulauf in den Ventilinnenraum 22, 24 freigeben oder verschliessen.Two arrows 29, 30 indicate the fuel supply to the control valve 11, and an arrow 31 marks the fuel flow from the control valve 11. The arrows 29, 30, 31 thus also mark the so-called selected in the fuel metering device shown "reverse" flow principle. For this purpose, the valve housing 20 has a plurality of radially arranged, preferably oppositely paired inlet openings 32, 33 which are in hydraulic operative connection with a (not shown) prefeed pump of the fuel injection system. The inlet openings 32, 33 open into an annular channel 34 a. In the valve piston 23 radial control openings 35 are arranged, the channel 34 and the inlet openings 32, 33 cooperate with the ring by, depending on the position of the valve piston 23 (see., In each case in Fig. 1 and 2, respectively, two possible two piston positions indicated) - Release or close the inlet in the valve interior 22, 24.

Der in den Ventilinnenraum 22, 24 gelangte Kraftstoff wird in Axialrichtung (Pfeil 31) durch eine abgesetzte Bohrung 36 abgeleitet, die mit dem Hochdruckpumpen-Zulauf (Niederdruckbereich der Hochdruckpumpe) hydraulisch verbunden ist. Die Bohrung 36 ist in dem bereits erwähnten Sicherungselement 26 eingearbeitet, das den unteren Abschluss des Ventilgehäuses 20 bildet.The fuel which has reached the valve interior 22, 24 is discharged in the axial direction (arrow 31) through a stepped bore 36, which is hydraulically connected to the high-pressure pump inlet (low-pressure region of the high-pressure pump). The bore 36 is incorporated in the already mentioned securing element 26, which forms the lower end of the valve housing 20.

Fig. 2 läßt die besondere Gestaltung der Steueröffnung 35 erkennen, aus der sich - im Zusammenwirken mit der Hubbewegung des Ventilkolbens 23 - die in Fig. 3 graphisch dargestellte Durchsatzcharakteristik ergibt. So weist die Steueröffnung 35 vorzugsweise einen (oberen) schlitzförmigen und einen (unteren) etwa rechteckförmigen Bereich auf. In der oberen Endstellung (Öffnungsstellung) desVentilkolbens 23 - siehe die rechte Bildhälfte in Figur 2 (bzw. in Fig. 1) - kommt der verbreiterte rechteckförmige Bereich der Steueröffnung 35 zum Tragen. Dies bedeutet maximaler Kraftstoffdurchsatz durch das Ventil 11. Dieser Zustand wird in Fig.2 und 3 jeweils durch einen Pfeil 37 kenntlich gemacht.Fig. 2 reveals the particular design of the control port 35, from which - in conjunction with the lifting movement of the valve piston 23 - the graph shown in FIG. 3 throughput characteristic results. Thus, the control opening 35 preferably has an (upper) slot-shaped and a (lower) approximately rectangular area. In the upper end position (open position) of the valve piston 23 - see the right half of the figure in FIG. 2 (or in FIG. 1) - the widened rectangular area of the control opening 35 comes into play. This means maximum fuel flow rate through the valve 11. This state is indicated in FIGS. 2 and 3 by an arrow 37 in each case.

Während der Abwärtsbewegung des Ventilkolbens 23 verringert sich der Durchsatz stetig (vgl. den linearen Kurvenabschnitt 38 in Fig. 3). In der unteren Endstellung (Schließstellung) des Ventilkolbens 23 schließlich (siehe linke Bildhälfte in Fig. 2 und 1) hat sich der Durchsatz auf Null reduziert (siehe Pfeile 39 in Fig. 2 und 3).During the downward movement of the valve piston 23, the throughput decreases steadily (compare the linear curve section 38 in Fig. 3). Finally, in the lower end position (closed position) of the valve piston 23 (see left half of the figures in FIGS. 2 and 1), the throughput has been reduced to zero (see arrows 39 in FIGS. 2 and 3).

Alternativ zu der in Fig. 2 dargestellten und oben beschriebenen Geometrie der Steueröffnung 35 sind jedoch durchaus noch andersartige Gestaltungen der Steueröffnung 35 möglich. So ist es etwa denkbar, die Steueröffnung trapezförmig zu gestalten und damit andere, z.B. lineare, Durchsatzcharakteristika zu realisieren. Die aus Fig. 3 ersichtliche Durchsatzcharakteristik dagegen zeichnet sich durch einen gestuften Verlauf aus.As an alternative to the geometry of the control opening 35 shown in FIG. 2 and described above, however, different designs of the control opening 35 are still possible. For example, it is conceivable to make the control opening trapezoidal and thus allow others, e.g. to realize linear, throughput characteristics. The apparent from Fig. 3 throughput characteristic, however, is characterized by a stepped course.

Claims (3)

  1. Fuel injection system for internal combustion engines, having a distributor pipe and a high-pressure pump which is driven as a function of the engine speed and serves to generate the fuel pressure and fuel throughput rate which is required in the distributor pipe in the respective operating state of the internal combustion engine, and, furthermore, having a fuel metering unit (10, 11) which is assigned to the high-pressure pump and is based on an electromagnetically actuated regulating valve (11), the fuel metering unit (10, 11) being arranged in the high-pressure pump, the outlet (36) of the regulating valve (11) opening into the low-pressure region of the high-pressure pump, and the inlet (32, 34) of the regulating valve (11) being connected to the delivery side of a prefeed pump, and the regulating valve (11) having a valve piston (23) which is acted on by a compression spring (25) and which can be actuated counter to a spring force of a compression spring (25) by an armature bolt (14) of an electromagnet (10), and at least one, preferably a plurality of radial control openings (35) being arranged in the valve piston (23), which radial control openings (35) communicate with the low-pressure region of the high-pressure pump, the regulating valve (11) having a valve housing (20) with an annular channel (34) and a plurality of radially arranged feed openings (32, 33) which are preferably arranged opposite one another in pairs and serve to feed fuel (29, 30) into the valve piston (23), in such a way that they communicate via the annular channel (34) with the control openings (35) of the valve piston (23), characterized in that the valve piston (23) is acted on by the compression spring (25) in the direction of its open position and can be moved by the electromagnet (10) in the direction of its closed position, and in that the control openings (35) have either an upper slot-shaped region axially towards the electromagnet (10) and a lower widened, approximately rectangular region towards the compression spring (25), or have a trapezoidal shape.
  2. Fuel injection system according to Claim 1, characterized in that the interior (24) of the valve piston (23) serves at the same time for the axial discharge of the fuel out of the regulating valve (11) in the direction (31) of the low-pressure region of the high-pressure pump.
  3. Fuel injection system according to Claim 1 or 2, characterized in that the control openings (35) are arranged at equal angular spacings on the circumference of the valve piston (23), preferably arranged opposite one another in pairs.
EP01943031A 2000-05-13 2001-05-08 Fuel-injection system for internal combustion engines Expired - Lifetime EP1283956B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10023621A DE10023621A1 (en) 2000-05-13 2000-05-13 Fuel injection system for internal combustion engine has valve piston with at least one, preferably several, radial control openings connected to suction side of high pressure pump
DE10023621 2000-05-13
PCT/DE2001/001732 WO2001088368A1 (en) 2000-05-13 2001-05-08 Fuel-injection system for internal combustion engines

Publications (2)

Publication Number Publication Date
EP1283956A1 EP1283956A1 (en) 2003-02-19
EP1283956B1 true EP1283956B1 (en) 2006-01-11

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Application Number Title Priority Date Filing Date
EP01943031A Expired - Lifetime EP1283956B1 (en) 2000-05-13 2001-05-08 Fuel-injection system for internal combustion engines

Country Status (9)

Country Link
US (1) US6626151B2 (en)
EP (1) EP1283956B1 (en)
JP (1) JP4638649B2 (en)
KR (1) KR100757225B1 (en)
CN (1) CN1262756C (en)
BR (1) BR0106435B1 (en)
DE (2) DE10023621A1 (en)
ES (1) ES2255559T3 (en)
WO (1) WO2001088368A1 (en)

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WO2003050441A1 (en) * 2001-12-11 2003-06-19 Kayaba Industry Co., Ltd. Solenoid-operated proportional flow control valve
DE10242219A1 (en) * 2002-09-12 2004-03-25 Robert Bosch Gmbh Fuel metering unit for injection system has valve with flat characteristic for idling/low load, steep characteristic for partial/full load; transition between characteristics can be differentiated
DE10247774B4 (en) * 2002-10-14 2005-09-29 Siemens Ag Flow control valve
DE10251014A1 (en) * 2002-11-02 2004-05-19 Robert Bosch Gmbh Fuel dispensing unit for fuel injection system for internal combustion engine has shutoff sleeve in interior of valve piston and valve piston and shutoff sleeve form shutoff device
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KR100757225B1 (en) 2007-09-11
EP1283956A1 (en) 2003-02-19
BR0106435B1 (en) 2009-08-11
KR20020032527A (en) 2002-05-03
DE50108673D1 (en) 2006-04-06
BR0106435A (en) 2002-04-16
ES2255559T3 (en) 2006-07-01
US20020134355A1 (en) 2002-09-26
WO2001088368A1 (en) 2001-11-22
JP2003533638A (en) 2003-11-11
CN1262756C (en) 2006-07-05
JP4638649B2 (en) 2011-02-23
US6626151B2 (en) 2003-09-30
DE10023621A1 (en) 2001-11-15
CN1380941A (en) 2002-11-20

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