[go: up one dir, main page]

EP1759115B1 - High pressure pump for a fuel injection device of an internal combustion engine - Google Patents

High pressure pump for a fuel injection device of an internal combustion engine Download PDF

Info

Publication number
EP1759115B1
EP1759115B1 EP05726501A EP05726501A EP1759115B1 EP 1759115 B1 EP1759115 B1 EP 1759115B1 EP 05726501 A EP05726501 A EP 05726501A EP 05726501 A EP05726501 A EP 05726501A EP 1759115 B1 EP1759115 B1 EP 1759115B1
Authority
EP
European Patent Office
Prior art keywords
cone angle
valve member
pump
sealing surface
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
Application number
EP05726501A
Other languages
German (de)
French (fr)
Other versions
EP1759115A1 (en
Inventor
Achim Koehler
Sascha Ambrock
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 EP1759115A1 publication Critical patent/EP1759115A1/en
Application granted granted Critical
Publication of EP1759115B1 publication Critical patent/EP1759115B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/462—Delivery valves
    • 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
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • 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 is based on a high-pressure pump for a fuel injection device of an internal combustion engine according to the preamble of claim 1.
  • Such a high-pressure pump is through the DE 198 60 672 A1 known.
  • This high-pressure pump has at least one pump element with a pump piston driven in a stroke movement, which delimits a pump working space.
  • fuel is drawn in from a fuel feed via an inlet valve, and during the delivery stroke of the pump piston, fuel is expelled from the pump working space into a high-pressure region via an outlet valve.
  • the inlet valve has a valve member with a sealing surface with which it cooperates with a valve seat to control the connection of the pump working space to the fuel inlet.
  • the sealing surface and the seat surface of the valve seat are each frusto-conical, but have different cone angles.
  • the valve member is acted upon by the pressure prevailing in the pump working chamber in the closing direction and by the pressure prevailing in the fuel inlet in the opening direction. It results in the known high-pressure pump line contact between the sealing surface of the valve member and the seat surface of the valve seat, which during the operating time of the high pressure pump due to wear the Position of the line contact changes, resulting in a change of the opening pressure of the intake valve, since it changes the size of the pressure applied to the fuel inlet surface of the valve member. As a result, the filling of the pump working space is deteriorated with fuel, so that the delivery characteristic of the high-pressure pump is impaired.
  • a high-pressure pump which comprises an inlet valve, the valve member having a frusto-conical portion and a cylindrical portion, whereby a protruding edge is formed, which rests against a sealing surface of a valve seat with a frusto-conical portion of the valve member different cone angle.
  • the edge is formed at an acute angle and there is also a change in the opening pressure of the inlet valve and thus an impairment of the delivery characteristics of the high-pressure pump during the operating life of the high pressure pump due to wear.
  • the high-pressure pump according to the invention with the features of claim 1 has the advantage that the opening pressure of the inlet valve changes only slightly over the service life of the high-pressure pump, so that the delivery characteristics of the high-pressure pump remains at least substantially the same over the operating period.
  • FIG. 1 a high-pressure pump for a fuel injection device of an internal combustion engine
  • FIG. 2 an inlet valve of the high pressure pump in an enlarged view in a longitudinal section according to a first embodiment
  • FIG. 3 the inlet valve according to a second embodiment.
  • a high pressure pump 10 is shown for a fuel injector of an internal combustion engine, which is preferably a self-igniting internal combustion engine.
  • fuel is conveyed under high pressure in a memory 12, is taken from the fuel for injection to the internal combustion engine.
  • the high-pressure pump 10 is supplied by a feed pump 14 fuel.
  • the high-pressure pump 10 has at least one pump element 16 which has a pump piston 20 driven at least indirectly by a drive shaft 18 of the high-pressure pump 10 in a lifting movement.
  • the pump piston 20 is tightly guided in a cylinder bore 22 extending at least approximately radially to the drive shaft 18 and delimits a pump working space 24 in the outer end region of the cylinder bore 22 facing away from the drive shaft 18.
  • the drive shaft 18 has a cam or a shaft section 26 eccentric to its axis of rotation 19 , via which during the rotational movement of the drive shaft 18, the lifting movement of the pump piston 20 is effected.
  • the pump working chamber 24 can be connected to the inlet pump 30, which opens into the pump working chamber 24 and is designed as a check valve, with a fuel feed from the feed pump 14.
  • the pump working chamber 24 can also be connected to the accumulator 12 via a discharge valve 32, which opens out of the pump working chamber 24 and is designed as a check valve, with a fuel outlet.
  • the pump piston 20 in the cylinder bore 22 moves radially inwards, so that the volume of the pump working chamber 24 is increased.
  • the inlet valve 30 is inserted, for example, into a bore 34 of a housing part 36 of the high-pressure pump 10 which adjoins the cylinder bore 22 radially outward.
  • the bore 34 is formed larger in diameter relative to the cylinder bore 22.
  • the housing part 36 may for example be a cylinder head, which is connected to another housing part in which the drive shaft 18 is mounted, or a housing part, in which the drive shaft 18 is mounted.
  • In the bore 34 opens near the cylinder bore 22 facing end portion, for example, approximately radially to the axis of the bore 34, a fuel inlet channel 38 which is connected to the feed pump 14.
  • the inlet valve 30 has a valve housing 40 in which a diameter-stepped bore 42 is present.
  • the bore 42 has a small-diameter portion 43, a section 44 which adjoins the section 43 to the pump working chamber 24 with a larger diameter and a section 45 adjoining the section 44 to the pump working chamber 24.
  • the inlet valve 30 has a piston-shaped valve member 46, which is displaceably guided in the bore section 43 with a cylindrical shaft 47.
  • the valve member 46 also has an adjoining the shaft 47, enlarged in diameter relative to the shaft 47 head 48, wherein at the transition from the head 48 to the shaft 47, a sealing surface 49,50 on the valve member 46 is arranged.
  • the sealing surface has two successively arranged in the direction of the longitudinal axis 51 of the valve member 44 sections 49,50, each of which may be at least approximately conical, however have different cone angles.
  • the pump chamber 24 facing away from the first portion 49 of the sealing surface has a cone angle ⁇ 1 and adjoining the pump working chamber 24 second portion 50 of the sealing surface has a cone angle ⁇ 2, which is smaller than the cone angle ⁇ 1.
  • the head 48 of the valve member 46 faces the pump working chamber 24.
  • the shaft 47 of the valve member 46 protrudes with its end facing away from the head 48 out of the bore portion 43 and at this engages a prestressed closing spring 52.
  • At least one inlet channel 53 is introduced, which opens into the bore portion 44.
  • a plurality, for example, three over the circumference of the valve housing 40 evenly distributed feed channels 53 are provided.
  • the bore portion 45 is formed such that its diameter widens away from the bore portion 44 toward the pump working space 24.
  • the lateral surface of the bore portion 45 forms a seat surface of a valve seat, is at least approximately conical and has a constant cone angle ⁇ 3.
  • the cone angle ⁇ 3 is greater than the cone angle ⁇ 2 but smaller than the cone angle ⁇ 1.
  • the two sections 49,50 of the sealing surface of the valve member 46 include an obtuse angle between them.
  • the difference ⁇ between the cone angle ⁇ 1 of the portion 49 of the sealing surface on the valve member 46 and the cone angle ⁇ 3 of the seat surface 45 is preferably between about 0.1 ° and 20 °.
  • the difference ⁇ between the cone angle ⁇ 2 of Section 50 of the sealing surface on the valve member 46 and the cone angle ⁇ 3 of the seat surface 45 is preferably between about 0.1 ° and 90 °.
  • the angle ⁇ between the second portion 50 of the sealing surface of the valve member 46 and the longitudinal axis 51 of the valve member 46 is greater than 0 ° and less than 90 °.
  • the arranged within the edge 54 of the first portion 49 of the sealing surface of the valve member 46 is acted upon by the pressure prevailing in the fuel inlet 38,53 pressure, by which a force in the opening direction is generated on the valve member 46.
  • the pump chamber 24 facing the end face of the head 48 of the valve member 46 is acted upon by the pressure prevailing in the pump working chamber 24, by which a force in the closing direction is generated on the valve member 46.
  • a force in the closing direction is generated on the valve member 46 by the closing spring 52.
  • the edge 54 is pressed slightly flat as a result of wear, whereby the pressure applied to the pressure prevailing in the fuel inlet surface of the first portion 49 of the sealing surface of the valve member 46 is slightly reduced, so that the opening pressure, which is the pressure difference between the in the fuel inlet prevailing pressure and the pressure prevailing in the pump working chamber 24 at which the inlet valve 30 opens slightly increases.
  • the inlet valve 30 opens when the force prevailing in the fuel inlet 38,51 pressure acting on the portion 49 of the sealing surface of the valve member 46 in the opening direction on the valve member 46 generated force is greater than the sum of the through in the pump working chamber 24 prevailing pressure on the valve member 46 generated force and the force generated by the closing spring 52 is.
  • the pump piston 20 is generated by this in the pump working chamber 24, an increased pressure through which the inlet valve 30 is closed.
  • the intake valve 30 is shown according to a second embodiment.
  • the inlet valve 30 in this case has the valve housing 40, in which the bore 42 is formed with the sections 43,44 and 45.
  • the bore section 45 forming the seating surface of the valve seat does not have a constant cone angle, but has a first section 45a with a cone angle ⁇ 4 and a second section 45b with a cone angle ⁇ 5.
  • the cone angle ⁇ 5 of the second portion 45b is greater than the cone angle ⁇ 4 of the first portion 45a.
  • the valve member 46 has the shaft 47 guided in the section 43 of the bore 42 and the pump working chamber 24 facing head 48, wherein at the transition from the shaft 47 to the head 48, the conical sealing surface 49 is arranged, which has a constant cone angle ⁇ 6.
  • the cone angle ⁇ 4 of the first portion 45a of the seat is smaller than the cone angle ⁇ 6 of the sealing surface 49 of the valve member 46 and the cone angle ⁇ 5 of the second portion 45b of the seat is greater than the cone angle ⁇ 6 of the sealing surface 49 of the valve member 46.
  • the difference ⁇ between the cone angle ⁇ 4 of the first portion 45a of the seat and the cone angle ⁇ 6 of the sealing surface 49 of the valve member 46 is preferably between about 0.1 ° and 90 °.
  • the difference ⁇ between the cone angle ⁇ 5 of the second portion 45b of the seat surface and the cone angle ⁇ 6 of the sealing surface 49 of the valve member 46 is preferably between about 0.1 ° and 20 °.
  • the angle ⁇ between the second portion 45b of the seating surface and the longitudinal axis 51 of the valve member 46 is greater than 0 ° and less than 90 °.
  • a protruding Edge 54 formed at which the valve member 46 comes into abutment with its sealing surface 49 in its closed position.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Details Of Reciprocating Pumps (AREA)

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine nach der Gattung des Anspruchs 1.The invention is based on a high-pressure pump for a fuel injection device of an internal combustion engine according to the preamble of claim 1.

Eine solche Hochdruckpumpe ist durch die DE 198 60 672 A1 bekannt. Diese Hochdruckpumpe weist wenigstens ein Pumpenelement auf mit einem in einer Hubbewegung angetriebenen Pumpenkolben, der einen Pumpenarbeitsraum begrenzt. Beim Saughub des Pumpenkolbens wird über ein Einlassventil Kraftstoff aus einem Kraftstoffzulauf angesaugt und beim Förderhub des Pumpenkolbens wird über ein Auslassventil Kraftstoff aus dem Pumpenarbeitsraum in einen Hochdruckbereich verdrängt. Das Einlassventil weist ein Ventilglied mit einer Dichtfläche auf, mit der es mit einem Ventilsitz zur Steuerung der Verbindung des Pumpenarbeitsraums mit dem Kraftstoffzulauf zusammenwirkt. Die Dichtfläche und die Sitzfläche des Ventilsitzes sind jeweils kegelstumpfförmig ausgebildet, weisen jedoch unterschiedliche Kegelwinkel auf. Das Ventilglied ist durch den im Pumpenarbeitsraum herrschenden Druck in Schließrichtung und durch den im Kraftstoffzulauf herrschenden Druck in Öffnungsrichtung beaufschlagt. Es ergibt sich bei der bekannten Hochdruckpumpe eine Linienberührung zwischen der Dichtfläche des Ventilglieds und der Sitzfläche des Ventilsitzes, wobei sich während der Betriebsdauer der Hochdruckpumpe infolge von Verschleiß die Lage der Linienberührung ändert, was zu einer Änderung des öffnungsdrucks des Einlassventils führt, da sich dabei die Größe der vom Druck im Kraftstoffzulauf beaufschlagten Fläche des Ventilglieds ändert. Hierdurch wird die Befüllung des Pumpenarbeitsraums mit Kraftstoff verschlechtert, so dass die Fördercharakteristik der Hochdruckpumpe beeinträchtigt ist.Such a high-pressure pump is through the DE 198 60 672 A1 known. This high-pressure pump has at least one pump element with a pump piston driven in a stroke movement, which delimits a pump working space. During the suction stroke of the pump piston, fuel is drawn in from a fuel feed via an inlet valve, and during the delivery stroke of the pump piston, fuel is expelled from the pump working space into a high-pressure region via an outlet valve. The inlet valve has a valve member with a sealing surface with which it cooperates with a valve seat to control the connection of the pump working space to the fuel inlet. The sealing surface and the seat surface of the valve seat are each frusto-conical, but have different cone angles. The valve member is acted upon by the pressure prevailing in the pump working chamber in the closing direction and by the pressure prevailing in the fuel inlet in the opening direction. It results in the known high-pressure pump line contact between the sealing surface of the valve member and the seat surface of the valve seat, which during the operating time of the high pressure pump due to wear the Position of the line contact changes, resulting in a change of the opening pressure of the intake valve, since it changes the size of the pressure applied to the fuel inlet surface of the valve member. As a result, the filling of the pump working space is deteriorated with fuel, so that the delivery characteristic of the high-pressure pump is impaired.

Durch die US-A-2003/0029423 ist eine Hochdruckpumpe bekannt, die ein Einlassventil aufweist, dessen Ventilglied einen kegelstumpfförmigen Abschnitt und einen zylindrischen Abschnitt aufweist, wodurch eine hervorstehende Kante gebildet ist, die an einer Dichtfläche eines Ventilsitzes mit einem zum kegelstumpfförmigen Abschnitt des Ventilglieds unterschiedlichen Kegelwinkel anliegt. Die Kante ist dabei spitzwinklig ausgebildet und es ergibt sich während der Betriebsdauer der Hochdruckpumpe infolge von Verschleiß ebenfalls eine Änderung des Öffnungsdrucks des Einlassventils und damit eine Beeinträchtigung der Fördercharakteristik der Hochdruckpumpe.By the US-A-2003/0029423 a high-pressure pump is known which comprises an inlet valve, the valve member having a frusto-conical portion and a cylindrical portion, whereby a protruding edge is formed, which rests against a sealing surface of a valve seat with a frusto-conical portion of the valve member different cone angle. The edge is formed at an acute angle and there is also a change in the opening pressure of the inlet valve and thus an impairment of the delivery characteristics of the high-pressure pump during the operating life of the high pressure pump due to wear.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Hochdruckpumpe mit den Merkmalen gemäß Anspruch 1 hat demgegenüber den Vorteil, dass sich der Öffnungsdruck des Einlassventils über die Betriebsdauer der Hochdruckpumpe nur wenig ändert, so dass die Fördercharakteristik der Hochdruckpumpe auch über die Betriebsdauer zumindest im wesentlichen gleich bleibt.The high-pressure pump according to the invention with the features of claim 1 has the advantage that the opening pressure of the inlet valve changes only slightly over the service life of the high-pressure pump, so that the delivery characteristics of the high-pressure pump remains at least substantially the same over the operating period.

In den abhängigen Ansprüchen sind vorteilhafte Ausgestaltungen und Weiterbildungen der erfindungsgemäßen Hochdruckpumpe angegeben.In the dependent claims advantageous refinements and developments of the high pressure pump according to the invention are given.

Zeichnungdrawing

Zwei Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 eine Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine, Figur 2 ein Einlassventil der Hochdruckpumpe in vergrößerter Darstellung in einem Längsschnitt gemäß einem ersten Ausführungsbeispiel und Figur 3 das Einlassventil gemäß einem zweiten Ausführungsbeispiel.Two embodiments of the invention are illustrated in the drawing and explained in more detail in the following description. Show it FIG. 1 a high-pressure pump for a fuel injection device of an internal combustion engine, FIG. 2 an inlet valve of the high pressure pump in an enlarged view in a longitudinal section according to a first embodiment and FIG. 3 the inlet valve according to a second embodiment.

Beschreibung der AusführungsbeispieleDescription of the embodiments

In Figur 1 ist eine Hochdruckpumpe 10 für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine dargestellt, die vorzugsweise eine selbstzündende Brennkraftmaschine ist. Durch die Hochdruckpumpe 10 wird Kraftstoff unter Hochdruck in einen Speicher 12 gefördert, aus dem Kraftstoff zur Einspritzung an der Brennkraftmaschine entnommen wird. Der Hochdruckpumpe 10 wird durch eine Förderpumpe 14 Kraftstoff zugeführt. Die Hochdruckpumpe 10 weist wenigstens ein Pumpenelement 16 auf, das einen zumindest mittelbar durch eine Antriebswelle 18 der Hochdruckpumpe 10 in einer Hubbewegung angetriebenen Pumpenkolben 20 aufweist. Der Pumpenkolben 20 ist in einer zumindest annähernd radial zur Antriebswelle 18 verlaufenden Zylinderbohrung 22 dicht geführt und begrenzt in dem der Antriebswelle 18 abgewandten äusseren Endbereich der Zylinderbohrung 22 einen Pumpenarbeitsraum 24. Die Antriebswelle 18 weist einen Nocken oder einen zu ihrer Drehachse 19 exzentrischen Wellenabschnitt 26 auf, über den bei der Drehbewegung der Antriebswelle 18 die Hubbewegung des Pumpenkolbens 20 bewirkt wird. Der Pumpenarbeitsraum 24 ist über ein in den Pumpenarbeitsraum 24 öffnendes, als Rückschlagventil ausgebildetes Einlassventil 30 mit einem Kraftstoffzulauf von der Förderpumpe 14 her verbindbar. Der Pumpenarbeitsraum 24 ist außerdem über ein aus dem Pumpenarbeitsraum 24 öffnendes, als Rückschlagventil ausgebildetes Auslassventil 32 mit einem Kraftstoffablauf zum Speicher 12 hin verbindbar. Beim Saughub bewegt sich der Pumpenkolben 20 in der Zylinderbohrung 22 radial nach innen, so dass das Volumen des Pumpenarbeitsraums 24 vergrößert wird. Beim Saughub des Pumpenkolbens 20 ist wegen der dabei bestehenden Druckdifferenz das Einlassventil 30 geöffnet, da von der Förderpumpe 14 ein höherer Druck erzeugt wird als der im Pumpenarbeitsraum 24 herrschende Druck, so dass von der Förderpumpe 14 geförderter Kraftstoff in den Pumpenarbeitsraum 24 angesaugt wird. Das Auslassventil 32 ist beim Saughub des Pumpenkolbens 20 geschlossen, da im Speicher 12 ein höherer Druck als im Pumpenarbeitsraum 24 herrscht.In FIG. 1 a high pressure pump 10 is shown for a fuel injector of an internal combustion engine, which is preferably a self-igniting internal combustion engine. By the high pressure pump 10 fuel is conveyed under high pressure in a memory 12, is taken from the fuel for injection to the internal combustion engine. The high-pressure pump 10 is supplied by a feed pump 14 fuel. The high-pressure pump 10 has at least one pump element 16 which has a pump piston 20 driven at least indirectly by a drive shaft 18 of the high-pressure pump 10 in a lifting movement. The pump piston 20 is tightly guided in a cylinder bore 22 extending at least approximately radially to the drive shaft 18 and delimits a pump working space 24 in the outer end region of the cylinder bore 22 facing away from the drive shaft 18. The drive shaft 18 has a cam or a shaft section 26 eccentric to its axis of rotation 19 , via which during the rotational movement of the drive shaft 18, the lifting movement of the pump piston 20 is effected. The pump working chamber 24 can be connected to the inlet pump 30, which opens into the pump working chamber 24 and is designed as a check valve, with a fuel feed from the feed pump 14. The pump working chamber 24 can also be connected to the accumulator 12 via a discharge valve 32, which opens out of the pump working chamber 24 and is designed as a check valve, with a fuel outlet. During the suction stroke, the pump piston 20 in the cylinder bore 22 moves radially inwards, so that the volume of the pump working chamber 24 is increased. When suction stroke of the pump piston 20, the inlet valve 30 is opened because of the existing pressure difference, as of the feed pump 14, a higher pressure is generated than the pressure prevailing in the pump working chamber 24, so that funded by the feed pump 14 fuel is sucked into the pump working chamber 24. The exhaust valve 32 is at the suction stroke of Pump piston 20 is closed, as in the memory 12, a higher pressure than in the pump working chamber 24 prevails.

Nachfolgend wird das Einlassventil 30 anhand der Figur 2 näher beschrieben, in der das Einlassventil 30 gemäß einem ersten Ausführungsbeispiel dargestellt ist. Das Einlassventil 30 ist beispielsweise in eine sich radial nach aussen an die Zylinderbohrung 22 anschliessende Bohrung 34 eines Gehäuseteils 36 der Hochdruckpumpe 10 eingesetzt. Die Bohrung 34 ist dabei im Durchmesser gegenüber der Zylinderbohrung 22 größer ausgebildet. Das Gehäuseteil 36 kann beispielsweise ein Zylinderkopf sein, der mit einem anderen Gehäuseteil, in dem die Antriebswelle 18 gelagert ist, verbunden ist oder ein Gehäuseteil sein, in dem auch die Antriebswelle 18 gelagert ist. In die Bohrung 34 mündet nahe deren der Zylinderbohrung 22 zugewandtem Endbereich beispielsweise etwa radial zur Achse der Bohrung 34 ein Kraftstoffzulaufkanal 38, der mit der Förderpumpe 14 verbunden ist. Das Einlassventil 30 weist ein Ventilgehäuse 40 auf, in dem eine im Durchmesser gestufte Bohrung 42 vorhanden ist. Die Bohrung 42 weist einen im Durchmesser kleinen Abschnitt 43 auf, einen sich an den Abschnitt 43 zum Pumpenarbeitsraum 24 anschließenden Abschnitt 44 mit größerem Durchmesser und einen sich an den Abschnitt 44 zum Pumpenarbeitsraum 24 hin anschließenden Abschnitt 45 auf. Das Einlassventil 30 weist ein kolbenförmiges Ventilglied 46 auf, das mit einem zylindrischen Schaft 47 im Bohrungsabschnitt 43 verschiebbar geführt ist. Das Ventilglied 46 weist außerdem einen an den Schaft 47 anschließenden, im Durchmesser gegenüber dem Schaft 47 vergrößerten Kopf 48 auf, wobei am Übergang vom Kopf 48 zum Schaft 47 eine Dichtfläche 49,50 am Ventilglied 46 angeordnet ist. Die Dichtfläche weist zwei in Richtung der Längsachse 51 des Ventilglieds 44 nacheinander angeordnete Abschnitte 49,50 auf, die jeweils zumindest annähernd kegelförmig ausgebildet sein, jedoch voneinander verschiedene Kegelwinkel aufweisen. Der dem Pumpenarbeitsraum 24 abgewandte erste Abschnitt 49 der Dichtfläche weist einen Kegelwinkel α1 auf und der sich zum Pumpenarbeitsraum 24 anschließende zweite Abschnitt 50 der Dichtfläche weist einen Kegelwinkel α2 auf, der kleiner ist als der Kegelwinkel α1. Der Kopf 48 des Ventilglieds 46 weist zum Pumpenarbeitsraum 24. Der Schaft 47 des Ventilglieds 46 ragt mit seinem dem Kopf 48 abgewandten Ende aus dem Bohrungsabschnitt 43 heraus und an diesem greift eine vorgespannte Schließfeder 52 an.Hereinafter, the intake valve 30 will be described with reference to FIG FIG. 2 described in more detail, in which the inlet valve 30 is shown according to a first embodiment. The inlet valve 30 is inserted, for example, into a bore 34 of a housing part 36 of the high-pressure pump 10 which adjoins the cylinder bore 22 radially outward. The bore 34 is formed larger in diameter relative to the cylinder bore 22. The housing part 36 may for example be a cylinder head, which is connected to another housing part in which the drive shaft 18 is mounted, or a housing part, in which the drive shaft 18 is mounted. In the bore 34 opens near the cylinder bore 22 facing end portion, for example, approximately radially to the axis of the bore 34, a fuel inlet channel 38 which is connected to the feed pump 14. The inlet valve 30 has a valve housing 40 in which a diameter-stepped bore 42 is present. The bore 42 has a small-diameter portion 43, a section 44 which adjoins the section 43 to the pump working chamber 24 with a larger diameter and a section 45 adjoining the section 44 to the pump working chamber 24. The inlet valve 30 has a piston-shaped valve member 46, which is displaceably guided in the bore section 43 with a cylindrical shaft 47. The valve member 46 also has an adjoining the shaft 47, enlarged in diameter relative to the shaft 47 head 48, wherein at the transition from the head 48 to the shaft 47, a sealing surface 49,50 on the valve member 46 is arranged. The sealing surface has two successively arranged in the direction of the longitudinal axis 51 of the valve member 44 sections 49,50, each of which may be at least approximately conical, however have different cone angles. The pump chamber 24 facing away from the first portion 49 of the sealing surface has a cone angle α1 and adjoining the pump working chamber 24 second portion 50 of the sealing surface has a cone angle α2, which is smaller than the cone angle α1. The head 48 of the valve member 46 faces the pump working chamber 24. The shaft 47 of the valve member 46 protrudes with its end facing away from the head 48 out of the bore portion 43 and at this engages a prestressed closing spring 52.

Im Ventilgehäuse 40 ist wenigstens ein Zulaufkanal 53 eingebracht, der in den Bohrungsabschnitt 44 mündet. Vorzugsweise sind mehrere, beispielsweise drei über den Umfang des Ventilgehäuses 40 gleichmäßig verteilte Zulaufkanäle 53 vorgesehen. Der Bohrungsabschnitt 45 ist derart ausgebildet, dass sich dessen Durchmesser vom Bohrungsabschnitt 44 weg zum Pumpenarbeitsraum 24 hin erweitert. Die Mantelfläche des Bohrungsabschnitts 45 bildet dabei eine Sitzfläche eines Ventilsitzes, ist zumindest annähernd kegelförmig ausgebildet und weist einen konstanten Kegelwinkel α3 auf. Der Kegelwinkel α3 ist größer als der Kegelwinkel α2 aber kleiner als der Kegelwinkel α1. Am Übergang zwischen dem ersten Abschnitt 49 und dem zweiten Abschnitt 50 der Dichtfläche ist am Ventilglied 46 eine zur Sitzfläche 45 hin hervorstehende Kante 54 gebildet, mit der das Ventilglied 46 in seiner Schließstellung an der Sitzfläche 45 zur Anlage kommt und dadurch der Pumpenarbeitsraum 24 vom Kraftstoffzulauf mit den Zulaufkanälen 53 getrennt ist. Die beiden Abschnitte 49,50 der Dichtfläche des Ventilglieds 46 schließen einen stumpfen Winkel zwischen sich ein. Die Differenz Δα zwischen dem Kegelwinkel α1 des Abschnitts 49 der Dichtfläche am Ventilglied 46 und dem Kegelwinkel α3 der Sitzfläche 45 beträgt vorzugsweise zwischen etwa 0,1° und 20°. Die Differenz Δα zwischen dem Kegelwinkel α2 des Abschnitts 50 der Dichtfläche am Ventilglied 46 und dem Kegelwinkel α3 der Sitzfläche 45 beträgt vorzugsweise zwischen etwa 0,1° und 90°. Der Winkel β zwischen dem zweiten Abschnitt 50 der Dichtfläche des Ventilglieds 46 und der Längsachse 51 des Ventilglieds 46 ist größer als 0° und kleiner als 90°.In the valve housing 40 at least one inlet channel 53 is introduced, which opens into the bore portion 44. Preferably, a plurality, for example, three over the circumference of the valve housing 40 evenly distributed feed channels 53 are provided. The bore portion 45 is formed such that its diameter widens away from the bore portion 44 toward the pump working space 24. The lateral surface of the bore portion 45 forms a seat surface of a valve seat, is at least approximately conical and has a constant cone angle α3. The cone angle α3 is greater than the cone angle α2 but smaller than the cone angle α1. At the transition between the first portion 49 and the second portion 50 of the sealing surface on the valve member 46 to the seat 45 projecting edge 54 is formed, with which the valve member 46 comes into abutment in its closed position on the seat surface 45 and thereby the pump working chamber 24 from the fuel inlet is separated with the inlet channels 53. The two sections 49,50 of the sealing surface of the valve member 46 include an obtuse angle between them. The difference Δα between the cone angle α1 of the portion 49 of the sealing surface on the valve member 46 and the cone angle α3 of the seat surface 45 is preferably between about 0.1 ° and 20 °. The difference Δα between the cone angle α2 of Section 50 of the sealing surface on the valve member 46 and the cone angle α3 of the seat surface 45 is preferably between about 0.1 ° and 90 °. The angle β between the second portion 50 of the sealing surface of the valve member 46 and the longitudinal axis 51 of the valve member 46 is greater than 0 ° and less than 90 °.

Die innerhalb der Kante 54 angeordnete Fläche des ersten Abschnitts 49 der Dichtfläche des Ventilglieds 46 ist von dem im Kraftstoffzulauf 38,53 herrschenden Druck beaufschlagt, durch den eine Kraft in Öffnungsrichtung auf das Ventilglied 46 erzeugt wird. Die dem Pumpenarbeitsraum 24 zugewandte Stirnfläche des Kopfes 48 des Ventilglieds 46 ist von dem im Pumpenarbeitsraum 24 herrschenden Druck beaufschlagt, durch den eine Kraft in Schließrichtung auf das Ventilglied 46 erzeugt wird. Außerdem wird durch die Schließfeder 52 eine Kraft in Schließrichtung auf das Ventilglied 46 erzeugt. Während der Betriebsdauer der Hochdruckpumpe wird die Kante 54 infolge von Verschleiß etwas flach gedrückt, wobei sich die von dem im Kraftstoffzulauf herrschenden Druck beaufschlagte Fläche des ersten Abschnitts 49 der Dichtfläche des Ventilglieds 46 geringfügig verkleinert, so dass der Öffnungsdruck, das ist die Druckdifferenz zwischen dem im Kraftstoffzulauf herrschenden Druck und dem im Pumpenarbeitsraum 24 herrschenden Druck, bei der das Einlassventil 30 öffnet, geringfügig zunimmt.The arranged within the edge 54 of the first portion 49 of the sealing surface of the valve member 46 is acted upon by the pressure prevailing in the fuel inlet 38,53 pressure, by which a force in the opening direction is generated on the valve member 46. The pump chamber 24 facing the end face of the head 48 of the valve member 46 is acted upon by the pressure prevailing in the pump working chamber 24, by which a force in the closing direction is generated on the valve member 46. In addition, a force in the closing direction is generated on the valve member 46 by the closing spring 52. During the period of operation of the high-pressure pump, the edge 54 is pressed slightly flat as a result of wear, whereby the pressure applied to the pressure prevailing in the fuel inlet surface of the first portion 49 of the sealing surface of the valve member 46 is slightly reduced, so that the opening pressure, which is the pressure difference between the in the fuel inlet prevailing pressure and the pressure prevailing in the pump working chamber 24 at which the inlet valve 30 opens slightly increases.

Beim Saughub des Pumpenkolbens 20 öffnet das Einlassventil 30, wenn die durch den im Kraftstoffzulauf 38,51 herrschenden Druck, der auf den Abschnitt 49 der Dichtfläche des Ventilglieds 46 wirkt, in Öffnungsrichtung auf das Ventilglied 46 erzeugte Kraft größer ist als die Summe der durch den im Pumpenarbeitsraum 24 herrschenden Druck auf das Ventilglied 46 erzeugten Kraft und die durch die Schließfeder 52 erzeugte Kraft ist. Beim Förderhub des Pumpenkolbens 20 wird durch diesen im Pumpenarbeitsraum 24 ein erhöhter Druck erzeugt, durch den das Einlassventil 30 geschlossen wird.When the suction stroke of the pump piston 20, the inlet valve 30 opens when the force prevailing in the fuel inlet 38,51 pressure acting on the portion 49 of the sealing surface of the valve member 46 in the opening direction on the valve member 46 generated force is greater than the sum of the through in the pump working chamber 24 prevailing pressure on the valve member 46 generated force and the force generated by the closing spring 52 is. At the delivery stroke of the Pump piston 20 is generated by this in the pump working chamber 24, an increased pressure through which the inlet valve 30 is closed.

In Figur 3 ist das Einlassventil 30 gemäß einem zweiten Ausführungsbeispiel dargestellt. Das Einlassventil 30 weist dabei das Ventilgehäuse 40 auf, in dem die Bohrung 42 mit den Abschnitten 43,44 und 45 ausgebildet ist. Abweichend zum ersten Ausführungsbeispiel weist der die Sitzfläche des Ventilsitzes bildende Bohrungsabschnitt 45 keinen konstanten Kegelwinkel auf, sondern einen ersten Abschnitt 45a mit einem Kegelwinkel α4 und einen zweiten Abschnitt 45b mit einem Kegelwinkel α5. Der Kegelwinkel α5 des zweiten Abschnitts 45b ist größer als der Kegelwinkel α4 des ersten Abschnitts 45a. Das Ventilglied 46 weist den im Abschnitt 43 der Bohrung 42 geführten Schaft 47 und den zum Pumpenarbeitsraum 24 weisenden Kopf 48 auf, wobei am Übergang vom Schaft 47 zum Kopf 48 die kegelförmige Dichtfläche 49 angeordnet ist, die einen konstanten Kegelwinkel α6 aufweist. Der Kegelwinkel α4 des ersten Abschnitts 45a der Sitzfläche ist kleiner als der Kegelwinkel α6 der Dichtfläche 49 des Ventilglieds 46 und der Kegelwinkel α5 des zweiten Abschnitts 45b der Sitzfläche ist größer als der Kegelwinkel α6 der Dichtfläche 49 des Ventilglieds 46. Die Differenz Δα zwischen dem Kegelwinkel α4 des ersten Abschnitts 45a der Sitzfläche und dem Kegelwinkel α6 der Dichtfläche 49 des Ventilglieds 46 beträgt vorzugsweise zwischen etwa 0,1° und 90°. Die Differenz Δα zwischen dem Kegelwinkel α5 des zweiten Abschnitts 45b der Sitzfläche und dem Kegelwinkel α6 der Dichtfläche 49 des Ventilglieds 46 beträgt vorzugsweise zwischen etwa 0,1° und 20°. Der Winkel β zwischen dem zweiten Abschnitt 45b der Sitzfläche und der Längsachse 51 des Ventilglieds 46 ist größer als 0° und kleiner als 90°. Am Übergang zwischen den beiden Abschnitten 45a,45b der Sitzfläche ist eine hervorstehende Kante 54 gebildet, an der das Ventilglied 46 in seiner Schließstellung mit seiner Dichtfläche 49 zur Anlage kommt.In FIG. 3 the intake valve 30 is shown according to a second embodiment. The inlet valve 30 in this case has the valve housing 40, in which the bore 42 is formed with the sections 43,44 and 45. Notwithstanding the first exemplary embodiment, the bore section 45 forming the seating surface of the valve seat does not have a constant cone angle, but has a first section 45a with a cone angle α4 and a second section 45b with a cone angle α5. The cone angle α5 of the second portion 45b is greater than the cone angle α4 of the first portion 45a. The valve member 46 has the shaft 47 guided in the section 43 of the bore 42 and the pump working chamber 24 facing head 48, wherein at the transition from the shaft 47 to the head 48, the conical sealing surface 49 is arranged, which has a constant cone angle α6. The cone angle α4 of the first portion 45a of the seat is smaller than the cone angle α6 of the sealing surface 49 of the valve member 46 and the cone angle α5 of the second portion 45b of the seat is greater than the cone angle α6 of the sealing surface 49 of the valve member 46. The difference Δα between the cone angle α4 of the first portion 45a of the seat and the cone angle α6 of the sealing surface 49 of the valve member 46 is preferably between about 0.1 ° and 90 °. The difference Δα between the cone angle α5 of the second portion 45b of the seat surface and the cone angle α6 of the sealing surface 49 of the valve member 46 is preferably between about 0.1 ° and 20 °. The angle β between the second portion 45b of the seating surface and the longitudinal axis 51 of the valve member 46 is greater than 0 ° and less than 90 °. At the transition between the two sections 45a, 45b of the seat is a protruding Edge 54 formed at which the valve member 46 comes into abutment with its sealing surface 49 in its closed position.

Claims (6)

  1. High-pressure pump for a fuel injection device of an internal combustion engine, with at least one pump element (16) which has a pump piston (20) which is driven in a lifting movement and which delimits a pump working space (24), into which fuel is sucked in from a fuel inflow (38, 53) via an inlet valve (30) during the suction stroke of the pump piston (20) and out of which fuel is displaced into a high-pressure region (12) during the conveying stroke of the pump piston (20), the inlet valve (30) having a valve member (46) which cooperates by means of a sealing surface (49, 50; 49) with a valve seat (45; 45a, 45b) for controlling the connection of the pump working space (24) to the fuel inflow (38, 53), the valve member (46) being acted upon in the opening direction by the pressure prevailing in the fuel inflow (38, 53) and in the closing direction by the pressure prevailing in the pump working space (24), and the sealing surface (49, 50; 49) of the valve member (46) and the seat surface (45; 45a, 45b) of the valve seat being in each case of at least approximately conical design, characterized in that the sealing surface (49, 50) of the valve member (46) or the seat surface (45a, 45b) of the valve seat has two portions (49, 50; 45a, 45b) with first and second cone angles (α1, α2; α4, α5) different from one another, in that the other surface, namely the seat surface (45) or the sealing surface (49), has a constant third cone angle (α3; α6) different from the first and the second cone angle (α1, α2; α4, α5), and in that, at the transition between the two portions (49, 50; 45a, 45b), a projecting edge (54) is formed, against which the surface (45; 49) with the constant cone angle (α3; α6) comes to bear.
  2. High-pressure pump according to Claim 1, characterized in that the difference between the first and second cone angles (α1, α2; α4, α5) and the third cone angle (α3; α6) amounts to between about 0.1° and 90°, preferably to between about 0.1° and 20°.
  3. High-pressure pump according to Claim 1 or 2, characterized in that the two portions (49, 50) with the cone angles (α1, α2) different from one another are arranged on the sealing surface of the valve member (46), in that the first portion (49) is arranged so as to face the fuel inflow (38, 53) and has the first cone angle (α1), and in that the second portion (50) is arranged so as to face the pump working space (24) and has the second cone angle (α2) which is smaller than the first cone angle (α1).
  4. High-pressure pump according to Claim 3, characterized in that the first cone angle (α1) of the first portion (49) of the sealing surface of the valve member (46) is larger than the constant third cone angle (α3) of the seat surface (45), and in that the second cone angle (α2) of the second portion (50) of the sealing surface of the valve member (46) is smaller than the constant third cone angle (α3) of the seat surface (45).
  5. High-pressure pump according to Claim 1 or 2, characterized in that the two portions (45a, 45b) with cone angles (α4, α5) different from one another are arranged on the seat surface, and the first portion (45a) is arranged so as to face the fuel inflow (38, 53) and has the first cone angle (α4), and in that the second portion (45b) is arranged so as to face the pump working space (24) and has the second cone angle (α5) which is larger than the first cone angle (α4).
  6. High-pressure pump according to Claim 5, characterized in that the first cone angle (α4) of the first portion (45a) of the seat surface is smaller than the constant third cone angle (α6) of the sealing surface (49) of the valve member (46), and in that the second cone angle (α5) of the second portion (45b) of the seat surface is larger than the constant third cone angle (α6) of the sealing surface (49) of the valve member (46).
EP05726501A 2004-06-16 2005-04-18 High pressure pump for a fuel injection device of an internal combustion engine Expired - Lifetime EP1759115B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004028998A DE102004028998A1 (en) 2004-06-16 2004-06-16 High-pressure pump for a fuel injection device of an internal combustion engine
PCT/EP2005/051692 WO2005124146A1 (en) 2004-06-16 2005-04-18 High pressure pump for a fuel injection device of an internal combustion engine

Publications (2)

Publication Number Publication Date
EP1759115A1 EP1759115A1 (en) 2007-03-07
EP1759115B1 true EP1759115B1 (en) 2009-11-04

Family

ID=34967363

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05726501A Expired - Lifetime EP1759115B1 (en) 2004-06-16 2005-04-18 High pressure pump for a fuel injection device of an internal combustion engine

Country Status (8)

Country Link
US (1) US20070221162A1 (en)
EP (1) EP1759115B1 (en)
JP (1) JP2006523806A (en)
KR (1) KR20070020074A (en)
CN (1) CN100473822C (en)
DE (2) DE102004028998A1 (en)
ES (1) ES2333344T3 (en)
WO (1) WO2005124146A1 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4163706B2 (en) * 2005-09-07 2008-10-08 三菱電機株式会社 Fuel injection device
DE102007044357A1 (en) * 2007-06-21 2008-12-24 Robert Bosch Gmbh Control valve for a fuel injection valve
DE102008043217A1 (en) * 2008-10-28 2010-04-29 Robert Bosch Gmbh High-pressure fuel pump for an internal combustion engine

Family Cites Families (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US596607A (en) * 1898-01-04 Sample-exhibiting book
US5419587A (en) * 1993-07-14 1995-05-30 Wallace Computer Services, Inc. Personalized envelope assembly for printed publication and method
US5566979A (en) * 1994-12-05 1996-10-22 Ong; Bon S. Document holder insert
US5661895A (en) * 1995-07-25 1997-09-02 Outboard Marine Corporatin Method of controlling the magnetic gap length and the initial stroke length of a pressure surge fuel pump
US5700136A (en) * 1996-07-23 1997-12-23 Sturman Industries Digital pump with bypass inlet valve
JP2807214B2 (en) * 1996-07-30 1998-10-08 忠男 宇野 Forgery prevention structure in passport and its manufacturing method
US6135503A (en) * 1997-11-21 2000-10-24 Giesecke & Devrient Gmbh Identification document
EP0999360A1 (en) * 1998-11-05 2000-05-10 Siemens Aktiengesellschaft Fluid metering control valve
GB2352780A (en) * 1999-03-23 2001-02-07 Nachi Fujikoshi Corp High pressure plunger pump
JP3685317B2 (en) * 2000-02-18 2005-08-17 株式会社デンソー Fuel injection pump
DE10139054C1 (en) * 2001-08-08 2003-01-30 Bosch Gmbh Robert Operating method for direct fuel injection engine has controlled inlet valve with variable opening duration controlling fuel quantity supplied to common-rail for fuel injection valves
ITTO20011039A1 (en) * 2001-10-30 2003-04-30 Ct Studi Componenti Per Veicol SUCTION VALVE FOR A HIGH PRESSURE PUMP, IN PARTICULAR FOR FUEL OF AN ENDOTHERMAL ENGINE.
DE10233452B4 (en) * 2002-07-24 2006-08-17 Ovd Kinegram Ag Individualized security document
DE10242591A1 (en) * 2002-09-13 2004-03-25 Robert Bosch Gmbh Fuel injection system for internal combustion engine has arrangement for carrying away leaks between pressure side of high pressure fuel pump and low pressure region of fuel injection system
DE102004008840A1 (en) * 2004-02-20 2005-09-01 Bundesdruckerei Gmbh Method for producing document of value, e.g. passport, involves formation of laminate cover with surrounding sealed edge, by covering security insert and transponder unit with at least one laminate layer
US7040981B2 (en) * 2004-03-11 2006-05-09 Canadian Bank Note Company, Limited Laminate sheet for security booklets and method for making same
US7296782B2 (en) * 2004-10-01 2007-11-20 Halkey-Roberts Corporation Dome check valve
DE102004055495A1 (en) * 2004-11-17 2006-05-24 Bundesdruckerei Gmbh Personnel document in booklet form

Also Published As

Publication number Publication date
DE502005008446D1 (en) 2009-12-17
EP1759115A1 (en) 2007-03-07
US20070221162A1 (en) 2007-09-27
DE102004028998A1 (en) 2006-01-05
JP2006523806A (en) 2006-10-19
ES2333344T3 (en) 2010-02-19
CN1969124A (en) 2007-05-23
CN100473822C (en) 2009-04-01
KR20070020074A (en) 2007-02-16
WO2005124146A1 (en) 2005-12-29

Similar Documents

Publication Publication Date Title
EP2032850B1 (en) High pressure pump in particular for a fuel injection device on an internal combustion engine
EP1727983B1 (en) High-pressure pump, in particular for a fuel-injection device in an internal combustion engine
EP1697631B1 (en) Valve, in particular for a high-pressure pump of a fuel-injection device for an internal combustion engine
EP1697636B1 (en) High-pressure pump, in particular for a fuel-injection device of an internal combustion engine
EP1141539B1 (en) Piston pump for high-pressure fuel generation
EP1636488B1 (en) Check valve, especially for a high pressure pump of a fuel injection device for an internal combustion engine
EP1966481B1 (en) High-pressure pump, in particular for a fuel injection device of an internal combustion engine
EP1357283B1 (en) Fuel injection system for internal combustion engine
DE10117600C1 (en) High-pressure fuel pump for a fuel system of a direct-injection internal combustion engine, fuel system and internal combustion engine
EP1736662B1 (en) Check valve, especially for a high pressure pump of a fuel injection device for an internal combustion engine
EP1784571B1 (en) High-pressure pump for a fuel injection device of an internal combustion engine
WO2005124153A1 (en) High-pressure pump for a fuel injection device of an internal combustion engine
EP1759115B1 (en) High pressure pump for a fuel injection device of an internal combustion engine
EP1716332A1 (en) High pressure pump, in particular for a fuel injection device in an internal combustion engine
EP1537334B1 (en) Pump, especially for a fuel injection device for an internal combustion engine
DE102004027825A1 (en) High-pressure pump, especially for fuel injection device for internal combustion engine, has smallest throughflow cross-section region downstream of sealing surface when valve element in open position
EP1671028A1 (en) Valve for controlling a connection in a high-pressure liquid system, particularly a fuel injection device for an internal combustion engine
EP3061967B1 (en) Pump, in particular high-pressure fuel pump
DE10355028A1 (en) High pressure pump especially for vehicle has the piston rod and cam follower made in one piece and spring loaded to press onto the drive cam
EP1284360B1 (en) Fuel injection device for an internal combustion engine
EP1383999B1 (en) Fuel injection device for an internal combustion engine
DE102020206991A1 (en) High pressure fuel pump and high pressure seal for use in a high pressure fuel pump
WO2006048371A1 (en) Fuel injection device for an internal combustion engine
DE10244550A1 (en) Fuel injection device for IC engines has symmetrical pressure valve piston with journal at both ends, and guide collars between them, with intermediate recess

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20070116

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE ES FR IT

17Q First examination report despatched

Effective date: 20070405

DAX Request for extension of the european patent (deleted)
RBV Designated contracting states (corrected)

Designated state(s): DE ES FR IT

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE ES FR IT

REF Corresponds to:

Ref document number: 502005008446

Country of ref document: DE

Date of ref document: 20091217

Kind code of ref document: P

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2333344

Country of ref document: ES

Kind code of ref document: T3

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20100805

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: ES

Payment date: 20120423

Year of fee payment: 8

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20130424

Year of fee payment: 9

Ref country code: FR

Payment date: 20130523

Year of fee payment: 9

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20141231

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20140430

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20140418

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20150526

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20140419

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20220627

Year of fee payment: 18

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502005008446

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20231103