EP1283956A1 - Fuel-injection system for internal combustion engines - Google Patents

Fuel-injection system for internal combustion engines

Info

Publication number
EP1283956A1
EP1283956A1 EP01943031A EP01943031A EP1283956A1 EP 1283956 A1 EP1283956 A1 EP 1283956A1 EP 01943031 A EP01943031 A EP 01943031A EP 01943031 A EP01943031 A EP 01943031A EP 1283956 A1 EP1283956 A1 EP 1283956A1
Authority
EP
European Patent Office
Prior art keywords
fuel
pressure pump
injection system
valve
pressure
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
EP01943031A
Other languages
German (de)
French (fr)
Other versions
EP1283956B1 (en
Inventor
Martin Boehm
Rainer Haeberer
Helmut Clauss
Felix LANDHÄUSSER
Markus Rueckle
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 EP1283956A1 publication Critical patent/EP1283956A1/en
Application granted granted Critical
Publication of EP1283956B1 publication Critical patent/EP1283956B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0017—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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.
  • the subject matter of the main patent is characterized by a fuel metering unit that is able to precisely meter the amount of fuel desired in the respective operating state of the internal combustion engine to the high-pressure pump of the CR system.
  • a fuel metering unit that is able to precisely meter the amount of fuel desired in the respective operating state of the internal combustion engine to the high-pressure pump of the CR system.
  • the main design elements of the main patent are radial control openings in the valve housing and an axial opening that leads to the interior of the sleeve-shaped valve piston.
  • the axial opening connects the Interior of the valve piston with a prefeed pump of the Kraftstoffeinspitzsystems, and the 'radially directed control openings of the valve housing of the high-pressure pump communicating with the low pressure region in hydraulic operative connection.
  • This flow principle is reversed in the other alternative, in that the axial opening is now hydraulically connected to the low-pressure region of the high-pressure pump, while the control openings are connected to the pressure side of the pre-feed pump and thus form the feed into the metering unit.
  • the object of the present invention is to further optimize the latter “reverse” flow principle.
  • valve piston is hydraulically centered in the valve housing over 360 °, in particular if a corresponding annular channel is formed in the valve housing (cf. claim 2). In this way, low-hysteresis and thus optimal sliding of the valve piston in the valve housing is made possible.
  • the invention also proves to be advantageous in terms of production engineering, since it is namely easier and less complex to incorporate the control openings in the valve piston (for example by laser cutting and subsequent deburring) than would be the case in the already expensive valve housing.
  • the application variance of the control openings therefore takes place in the valve piston and not in the cost-intensive valve housing.
  • Fig. 2 shows the ' detail "A" of Fig. 1 in an enlarged view compared to Fig. 1, and
  • Fig. 3 is a diagram in which the fuel flow (Q) is plotted against the magnetic stroke (I).
  • 10 denotes an electromagnet with an integrated control valve 11.
  • the electromagnet 10 has a magnet coil 12, an armature 13 with armature bolts 14 and a magnet pot 15. The latter encloses - partially - the magnet coil 12 and the armature
  • a plug-shaped power connection 101 is provided in a plug housing 100 which is connected in one piece to the magnet pot 15.
  • the electromagnet assembly 10 with integrated control valve 11 is integrated in a high-pressure fuel pump (not shown).
  • An encapsulation 17 ensures optimal heat transfer from the coil 12 to the housing 15.
  • Two sealing points 18, 19 together with the magnetic coil 12 ensure that the magnetic coil winding and contact points of the coil 12 are optimally protected against attacks by corrosive media.
  • the control valve 11 has a valve housing 20 which merges into a flange-like widening 21, which at the same time forms the end of the electromagnet housing 15 at the end.
  • An axial bore 22 is formed in the valve housing 20 and is arranged coaxially with the armature bolt 14 of the electromagnet 10.
  • the axial bore 22 receives a displaceable sleeve-shaped valve piston 23, in the interior 24 of which a compression spring 25 is arranged.
  • the compression spring 25 is supported on the inside on the valve piston 23 and with its other end on a securing element 26 located in the axial bore 22 of the valve housing 20.
  • 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 material of the high-pressure pump (not shown) that has a fuel inlet channel by two sealing rings 27, 28.
  • 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) feed pump of the fuel injection system.
  • the inlet openings 32, 33 open into an annular channel 34.
  • Radial control openings 35 are arranged in the valve piston 23, which cooperate with the ring channel 34 and the inlet openings 32, 33 by - depending on the position of the valve piston 23 (see here the two possible halves indicated in FIGS Piston positions) - open or close the inlet into the valve interior 22, 24.
  • the fuel that has entered the interior 22, 24 of the valve 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 area of the high-pressure pump).
  • the bore 36 is incorporated in the securing element 26 already mentioned, which forms the lower end of the valve housing 20.
  • Fig. 2 shows the special design of the control opening 35, from which - in cooperation with the lifting movement of the valve piston 23 - the throughput characteristic shown graphically in Fig. 3 results.
  • the control opening 35 preferably has an (upper) slit-shaped and an (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 state is indicated in FIGS. 2 and 3 by an arrow 37.
  • the throughput decreases continuously during the downward movement of the valve piston 23 (cf. the linear curve section 38 in FIG. 3).
  • the throughput has been reduced to zero (see arrows 39 in FIGS. 2 and 3).
  • 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. It is conceivable, for example, to design the control opening to be trapezoidal or to follow the characteristic of an e-function and thus others, e.g. to realize linear, throughput characteristics.
  • the throughput characteristic shown in FIG. 3, on the other hand, is characterized by a stepped course.

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 fuel-injection system for internal combustion engines, comprising a fuel-distribution pipe and a high-pressure pump that is driven in accordance with the engine speed. Said high-pressure pump generates the fuel pressure and throughput in the fuel-distribution pipe that is necessary in each operating state of the internal combustion engine. The fuel-injection system also comprises a fuel-metering unit assigned to the high-pressure pump. Said fuel-metering unit (10, 11) is based on an electromagnetically actuated control valve (11) and is positioned in the high-pressure pump. The outlet (36) of the control valve (11) opens into the low-pressure region of the high-pressure pump. The inlet (32, 34) of the control valve (11) is connected to the delivery side of a presupply pump. The control valve (11) has a valve plunger (23), which is spring-loaded (25) by pressure in the open position and which can be actuated by an armature pin (14) of the electromagnet (10) against the spring force in the closed position. The invention is characterized in that at least one, and preferably several radial control openings (35) are located in the valve plunger (23), said openings interacting with the induction side of the high-pressure pump.

Description

Kraftstoffeinspritzsystem für BrennkraftmaschinenFuel injection system for internal combustion engines
Stand der TechnikState of the art
Die Erfindung bezieht sich auf ein Kraftstoffeinspritzsystem für Brennkraftmaschinen nach dem Oberbegriff des Patentanspruchs 1.The invention relates to a fuel injection system for internal combustion engines according to the preamble of claim 1.
Der Gegenstand des Hauptpatents zeichnet sich durch eine Kraftstoffzumesseinheit aus, die in der Lage ist, der Hochdruckpumpe des CR-Systems die im jeweiligen Betriebszustand der Brennkraftmaschine gewünschte Kraftstoffmenge exakt zuzumessen. Durch eine derartige niederdruckseitige exakte Zumessung der benötigten Kraftstoffmenge zur Hochdruckpumpe werden komprimierte Überströmmengen von vornherein vermieden, was zu einem verbesserten Wirkungsgrad und somit zu Kraftstoffeinsparungen führt.The subject matter of the main patent is characterized by a fuel metering unit that is able to precisely meter the amount of fuel desired in the respective operating state of the internal combustion engine to the high-pressure pump of the CR system. Such an exact metering of the required fuel quantity to the high-pressure pump on the low-pressure side avoids compressed overflow quantities from the outset, which leads to improved efficiency and thus to fuel savings.
Wesentliche Konstruktionselemente sind beim Gegenstand des Hauptpatents radiale Steueröffnungen im Ventilgehäuse sowie eine Axialöffnung, die zum Innen-raum des hülsenförmigen - Ventilkolbens führt . Unter diesen konstruktiven Voraussetzungen lassen sich die oben angegebenen Vorzüge durch zwei alternative Durchströmprinzipien realisieren: So verbindet bei der einen Alternative die Axialöffnung den Innenraum des Ventilkolbens mit einer Vorförderpumpe des Kraftstoffeinspitzsystems, und die 'radial gerichteten Steueröffnungen des Ventilgehäuses stehen mit dem Niederdruckbereich der Hochdruckpumpe in hydraulischer Wirkverbindung. Dieses Durchströmprinzip wird bei der anderen Alternative umgekehrt, indem nun die Axialöffnung mit dem Niederdruckbereich der Hochdruckpumpe hydraulisch verbunden ist, während die Steueröffnungen mit der Druckseite der Vorförderpumpe verbunden sind und somit den Zulauf in die Zumesseinheit bilden.The main design elements of the main patent are radial control openings in the valve housing and an axial opening that leads to the interior of the sleeve-shaped valve piston. Under these design conditions, the advantages stated above can be realized by two alternative flow principles: In one alternative, the axial opening connects the Interior of the valve piston with a prefeed pump of the Kraftstoffeinspitzsystems, and the 'radially directed control openings of the valve housing of the high-pressure pump communicating with the low pressure region in hydraulic operative connection. This flow principle is reversed in the other alternative, in that the axial opening is now hydraulically connected to the low-pressure region of the high-pressure pump, while the control openings are connected to the pressure side of the pre-feed pump and thus form the feed into the metering unit.
Aufgabe der vorliegenden Erfindung ist es, das letztere "umgekehrte" Durchströmprinzip weiter zu optimieren.The object of the present invention is to further optimize the latter “reverse” flow principle.
Vorteile der ErfindungAdvantages of the invention
Erfindungsgemäß wird die Aufgabe bei einemAccording to the invention, the task at one
Kraftstoffeinpritzsystem der eingangs bezeichneten Gattung durch die kennzeichnenden Merkmale des Patentanspruchs 1 gelöst .Fuel injection system of the type described in the introduction solved by the characterizing features of patent claim 1.
Vorteilhafte Weiterbildungen der Erfindung sind den Patentansprüchen 2 - 7 zu entnehmen.Advantageous developments of the invention can be found in patent claims 2-7.
Ein wesentlicher Vorteil der Erfindung besteht darin, dass der Ventilkolben in dem Ventilgehäuse über 360° hydraulisch zentriert wird, insbesondere dann, wenn im Ventilgehäuse ein entsprechender Ringkanal ausgebildet ist (vgl. Patentanspruch 2) . Es wird auf diese Weise ein hysteresearmes und damit optimales Gleiten des Ventilkolbens im Ventilgehäuse ermöglicht.An important advantage of the invention is that the valve piston is hydraulically centered in the valve housing over 360 °, in particular if a corresponding annular channel is formed in the valve housing (cf. claim 2). In this way, low-hysteresis and thus optimal sliding of the valve piston in the valve housing is made possible.
Durch eine Anordnung der Steueröffnungen in gleichen Winkelabständen am Umfang des Ventilkolbens, vorzugsweise gegenständig gepaart, (vgl. Patentanspruch 4) wird ein optimaler hydraulischer Strömungskraft-Ausgleich erzielt.By arranging the control openings at equal angular intervals on the circumference of the valve piston, preferably paired oppositely, (see claim 4) an optimal hydraulic flow force compensation is achieved.
Auch in fertigungstechnischer Hinsicht erweist sich die Erfindung als vorteilhaft, da es nämlich einfacher und weniger aufwendig ist, die Steueröffnungen im Ventilkolben einzuarbeiten (etwa durch Laserschneiden und anschliessendes Entgraten) als dies im ohnehin kostenintensiven Ventilgehäuse der Fall wäre. Die Applikationsvarianz der Steueröffnungen findet also im Ventilkolben statt und nicht im kostenintensiven Ventilgehäuse .The invention also proves to be advantageous in terms of production engineering, since it is namely easier and less complex to incorporate the control openings in the valve piston (for example by laser cutting and subsequent deburring) than would be the case in the already expensive valve housing. The application variance of the control openings therefore takes place in the valve piston and not in the cost-intensive valve housing.
Zeichnungendrawings
Zur näheren Erläuterung der Erfindung dient ein Ausführungsbeispiel, das in der Zeichnung dargestellt und nachstehend detailliert beschrieben ist. Es zeigt:An exemplary embodiment, which is illustrated in the drawing and described in detail below, serves to explain the invention in more detail. It shows:
Fig. leine Ausführungsform einer Kraftstoffzumesseinheit , im vertikalen Längsschnitt,Leine embodiment of a fuel metering unit, in vertical longitudinal section,
Fig. 2 die 'Einzelheit "A" aus Fig. 1 in gegenüber Fig. 1 vergrößerter Darstellung, undFig. 2 shows the ' detail "A" of Fig. 1 in an enlarged view compared to Fig. 1, and
Fig. 3 ein Diagramm, worin der Kraftstoffdurchsatz (Q) über dem Magnethub (I) aufgetragen ist.Fig. 3 is a diagram in which the fuel flow (Q) is plotted against the magnetic stroke (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 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 FIG. 1 and - partly - in FIG. 2, 10 denotes an electromagnet with an integrated control valve 11. The electromagnet 10 has a magnet coil 12, an armature 13 with armature bolts 14 and a magnet pot 15. The latter encloses - partially - the magnet coil 12 and the armature A plug-shaped power connection 101 is provided in a plug housing 100 which is connected in one piece to the magnet pot 15. The electromagnet assembly 10 with integrated control valve 11 is integrated in a high-pressure fuel pump (not shown). An encapsulation 17 ensures optimal heat transfer from the coil 12 to the housing 15. Two sealing points 18, 19 together with the magnetic coil 12 ensure that the magnetic coil winding and contact points of the coil 12 are optimally protected against attacks 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 at the same time forms the end of the electromagnet housing 15 at the end. An axial bore 22 is formed in the valve housing 20 and is arranged coaxially with the armature bolt 14 of the electromagnet 10. The axial bore 22 receives a displaceable sleeve-shaped valve piston 23, in the interior 24 of which a compression spring 25 is arranged. The compression spring 25 is supported on the inside on the valve piston 23 and with its other end on a securing element 26 located in the axial bore 22 of the valve housing 20. 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 material of the high-pressure pump (not shown) that has a fuel inlet channel 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 ange-deuteten 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 indicates the fuel outflow 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) feed pump of the fuel injection system. The inlet openings 32, 33 open into an annular channel 34. Radial control openings 35 are arranged in the valve piston 23, which cooperate with the ring channel 34 and the inlet openings 32, 33 by - depending on the position of the valve piston 23 (see here the two possible halves indicated in FIGS Piston positions) - open or close the inlet into the valve interior 22, 24.
Der in den Venti1innenraum 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 that has entered the interior 22, 24 of the valve 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 area of the high-pressure pump). The bore 36 is incorporated in the securing element 26 already mentioned, 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 . 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) .Fig. 2 shows the special design of the control opening 35, from which - in cooperation with the lifting movement of the valve piston 23 - the throughput characteristic shown graphically in Fig. 3 results. For example, the control opening 35 preferably has an (upper) slit-shaped and an (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 throughput through the valve 11. This state is indicated in FIGS. 2 and 3 by an arrow 37. The throughput decreases continuously during the downward movement of the valve piston 23 (cf. 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 figure 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 oder der Charakteristik einer e-Funktion folgend 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. It is conceivable, for example, to design the control opening to be trapezoidal or to follow the characteristic of an e-function and thus others, e.g. to realize linear, throughput characteristics. The throughput characteristic shown in FIG. 3, on the other hand, is characterized by a stepped course.

Claims

Ansprüche Expectations
1. Kraftstoffeinspritzsystem für Brennkraftmaschinen mit einem Verteilerroh und einer motordrehzahlabhängig angetriebenen Hochdruckpumpe, die zur Erzeugung des beim jeweiligen Betriebszustand der Brennkraftmaschine im Verteilerrohr benötigten Kraftstoffdrucks und -durchsatzes dient, sowie ferner mit einer der Hochdruckpumpe zugeordneten Kraftstoffzumesseinheit, die auf einem elektromagnetisch betätigten Regelventil basiert, wobei die Kraftstoffzumesseinheit (10, 11) in der Hochdruckpumpe angeordnet ist, der Ausgang (36) des Regelventils (11) in den Niederdruckbereich der Hochdruckpumpe mündet und der Eingang (32, 34) des Regelventils (11) mit der Druckseite einer Vorförderpumpe verbunden ist, und wobei das Regelventil (11) einen - in Öffnungsstellung - druckfederbeaufschlagten (25) Ventilkolben (23) aufweist, der durch einen Ankerbolzen (14) des Elektromagneten (10) entgegen der Federkraft - in Schließstellung - betätigbar ist, dadurch gekennzeichnet, dass im Ventilkolben (23) mindestens eine, vorzugsweise mehrere radiale Steueröffnungen (35) angeordnet sind, die mit der Saugseite der Hochdruckpumpe in Wirkverbindung stehen.1.Fuel injection system for internal combustion engines with a distributor pipe and a high-pressure pump driven as a function of the engine speed, which is used to generate the fuel pressure and throughput required in the respective operating state of the internal combustion engine, and also with a fuel metering unit assigned to the high-pressure pump, which is based on an electromagnetically actuated control valve, wherein the fuel metering unit (10, 11) is arranged in the high pressure pump, the outlet (36) of the control valve (11) opens into the low pressure area of the high pressure pump and the inlet (32, 34) of the control valve (11) is connected to the pressure side of a pre-feed pump, and wherein the control valve (11) has a - in the open position - pressure spring-loaded (25) valve piston (23) which can be actuated by an anchor bolt (14) of the electromagnet (10) against the spring force - in the closed position -, characterized in that in the valve piston (23) at least one, preferably a plurality of radial control openings (35) are arranged which are operatively connected to the suction side of the high pressure pump.
2. Kraftstoffeinspritzsystem nach Anspruch 1, dadurch gekennzeichnet, dass das Ventilgehäuse (20) einen Ringkanal (34) und mehrere radial angeordnete, vorzugsweise gegenständig gepaarte, ZulaufÖffnungen (32, 33) aufweist, die dem KraftstoffZulauf (Pfeile 29, 30) in den Ventilkolben2. Fuel injection system according to claim 1, characterized in that the valve housing (20) has an annular channel (34) and a plurality of radially arranged, preferably oppositely paired, inlet openings (32, 33), which feed the fuel (arrows 29, 30) into the valve piston
(23) dienen, derart, dass sie mit den Steueröffnungen (35) des Ventilkolbens (23) über den Ringkanal (34) in Wirkverbindung stehen.(23) serve such that they are in operative connection with the control openings (35) of the valve piston (23) via the ring channel (34).
3. Kraftstoffeinspritzsystem nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass der Innenraum (24) des hülsenförmigen Ventilkolbens (23) zugleich zur axialen Ableitung des Kraftstoffs aus-_dem.-Regelventil (11) in Richtung (Pfeil 31) des Hochdruckpumpenzulaufs dient .3. Fuel injection system according to claim 1 or 2, characterized in that the interior (24) of the sleeve-shaped valve piston (23) also serves for the axial discharge of the fuel from the control valve (11) in the direction (arrow 31) of the high-pressure pump inlet.
4. Kraf stoffeinspritzsystem nach Anspruch 2 oder 3, dadurch gekennzeichnet, dass die Steueröffnungen (35) in gleichen Winkelabständen am Umfang des Ventilkolbens (23) , vorzugsweise gegenständig gepaart, angeordnet sind.4. Kraf material injection system according to claim 2 or 3, characterized in that the control openings (35) are arranged at equal angular intervals on the circumference of the valve piston (23), preferably paired in opposite directions.
5. Kraf stoffeinspritzsystem nach Anspruch 2, 3 oder 4, dadurch gekennzeichnet, dass die Steueröffnungen (35) einen (oberen) schlitzförmigen und einen (unteren) verbreiterten, etwa rechteckförmigen Bereich aufweisen (Fig. 2) .5. Kraf material injection system according to claim 2, 3 or 4, characterized in that the control openings (35) have an (upper) slit-shaped and a (lower) widened, approximately rectangular area (Fig. 2).
6. Kraftstoffeinspritzsystem nach Anspruch 2, 3 oder 4, dadurch gekennzeichnet dass die Steueröffnungen Trapezform aufweisen.6. Fuel injection system according to claim 2, 3 or 4, characterized in that the control openings have a trapezoidal shape.
7. Kraftstoffeinspritzsystem nach Anspruch 2, 3 oder 4, dadurch gekennzeichnet dass die Steueröffnungen der Charakteristik einer e-Funktion folgend ausgebildet sind. 7. Fuel injection system according to claim 2, 3 or 4, characterized in that the control openings are designed to follow the characteristic of an e-function.
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
DE10023621 2000-05-13
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
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 true EP1283956A1 (en) 2003-02-19
EP1283956B1 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)

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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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Publication number Publication date
US20020134355A1 (en) 2002-09-26
CN1380941A (en) 2002-11-20
JP4638649B2 (en) 2011-02-23
BR0106435A (en) 2002-04-16
BR0106435B1 (en) 2009-08-11
WO2001088368A1 (en) 2001-11-22
KR100757225B1 (en) 2007-09-11
DE10023621A1 (en) 2001-11-15
EP1283956B1 (en) 2006-01-11
DE50108673D1 (en) 2006-04-06
KR20020032527A (en) 2002-05-03
ES2255559T3 (en) 2006-07-01
CN1262756C (en) 2006-07-05
US6626151B2 (en) 2003-09-30
JP2003533638A (en) 2003-11-11

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