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EP3353411B1 - Valve, in particular suction valve, in a high-pressure pump of a fuel injection system - Google Patents

Valve, in particular suction valve, in a high-pressure pump of a fuel injection system Download PDF

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Publication number
EP3353411B1
EP3353411B1 EP16754216.6A EP16754216A EP3353411B1 EP 3353411 B1 EP3353411 B1 EP 3353411B1 EP 16754216 A EP16754216 A EP 16754216A EP 3353411 B1 EP3353411 B1 EP 3353411B1
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EP
European Patent Office
Prior art keywords
valve
pump
valve element
contact
actuating element
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.)
Active
Application number
EP16754216.6A
Other languages
German (de)
French (fr)
Other versions
EP3353411A1 (en
Inventor
Achim Koehler
Stefan Kolb
Hans Heber
Tobias Reiser
Namik Karaosmanoglu
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 EP3353411A1 publication Critical patent/EP3353411A1/en
Application granted granted Critical
Publication of EP3353411B1 publication Critical patent/EP3353411B1/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
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically
    • F02M59/367—Pump inlet valves of the check valve type being open when actuated
    • 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
    • F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
    • F02M63/0035—Poppet valves, i.e. having a mushroom-shaped valve member that moves perpendicularly to the plane of the valve seat
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/04—Fuel-injection apparatus having means for avoiding effect of cavitation, e.g. erosion
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger

Definitions

  • the invention relates to a valve, in particular a suction valve, in a high-pressure pump of a fuel injection system, with the features of the preamble of claim 1. Furthermore, the invention relates to a pump, in particular a high-pressure pump of a fuel injection system, in which the suction valve is used.
  • a high-pressure pump of a fuel injection system with a suction valve is through DE 10 2010 027 745 A1 known.
  • the suction valve has a valve element which is movable between an open and a closed position and which is at least indirectly in contact with an actuating element. By the actuating element, an actuating force can be transmitted to the valve element.
  • the high-pressure pump has a pump housing with a housing part, in which a pump piston is mounted in a cylinder bore, which limits a pump working chamber in the cylinder bore.
  • the pump working chamber can be connected via the suction valve with a fuel inlet and connected via a check valve with a high-pressure accumulator.
  • the actuating element can be designed as a magnet armature or acts as a combination of the magnet armature with an intermediate element on the valve element, in particular a pressed intermediate element.
  • the armature is part of an electromagnetic actuator, which also includes a magnetic coil. When the solenoid is energized, a magnetic field is formed whereby the armature moves relative to the solenoid against a spring force to close the working air gap.
  • the DE 10 2010 004 137 A shows a fuel injection valve with a housing and an actuator, which comprises a valve element.
  • the embodiment of the suction valve according to the invention with the features of claim 1 has the advantage that an improved expression of the structural elements is achieved, which reduces and / or prevents damage to the surfaces of the two elements by cavitation and resulting cavitation bubbles.
  • An annular arrangement of the region of the mechanical contact about an approximately centrally located region of the cavitation combines the described advantage of claim 1 with the advantage of a higher load capacity due to lower surface pressure and a resulting lower wear in the contact region and, consequently, a longer service life of the high-pressure pump ,
  • a trough-shaped recess on the actuating element and the valve element it is possible to avoid contact of the two elements in the zone of cavitation targeted by geometric shape and size of the trough-shaped recess.
  • the actuating element of the valve element is not formed directly by the armature, but that an intermediate element is used, which is positively connected to the armature.
  • the actuator can thus either have only the armature or it knows the elements magnet armature and intermediate element.
  • an intermediate element makes it possible to select a material for the intermediate element which is better suited for the stresses in the contact region to the valve element than the material of the magnet armature, in particular with regard to the mating intermediate element to the valve element and / or to the surrounding fuel.
  • a trough-shaped recess on the actuating element and the valve element is such that a different shape of both recesses takes place.
  • a further level of detailing this different shape provides that the respective recesses in the edge region of your cross-sectional dimension do not run off congruent, in particular by one of the two recesses in the edge region is formed larger.
  • Fig. 1 shows a sectional view of a high-pressure pump 1 shown schematically , which is designed as a high-pressure fuel pump and is preferably installed in a common-rail injection system.
  • the high pressure pump 1 is provided by a fuel low pressure system having at least one tank, a filter and a low pressure pump, provided fuel in a high-pressure accumulator, from which the fuel stored there is taken from fuel injectors for injection into the associated combustion chambers of an internal combustion engine.
  • the high-pressure pump 1 has a pump housing 3 with a camshaft space 5 .
  • a camshaft 7 with a trained example as a double cam cam 9 in.
  • the camshaft 7 is arranged in two on both sides of the cam 9 and designed as a radial bearing bearings in the form of a arranged in the pump housing 3 housing bearing 11 and a flange bearing 13, in one with the pump housing 3 connected flange 15, which closes the camshaft space 5 close to the environment, stored.
  • the flange 15 has a through opening through which a drive-side end portion 17 of the camshaft 7 protrudes.
  • the drive-side end portion 17 has, for example, a cone on which a drive wheel is placed and secured.
  • the drive wheel is formed for example as a pulley or gear.
  • the drive wheel is driven by the internal combustion engine directly or indirectly, for example via a belt drive or a gear transmission.
  • a tappet guide 19 is further inserted, in which a roller 21 having a roller tappet 23 is inserted.
  • the roller 21 runs on the cam 9 of the camshaft 7 during a rotational movement of the same and the roller tappet 23 is thus in the tappet guide 19 translationally moved up and down.
  • the roller tappet 23 cooperates with a pump piston 18 , which is also arranged to be movable up and down in a translatable manner in a cylinder bore 29 formed in a pump cylinder head 27 .
  • a plunger spring 33 is arranged, which is supported on the one hand to the pump cylinder head 27 and on the other hand to the roller tappet 23 and ensures a permanent contact of the roller 21 on the cam 9 in the direction of the camshaft 7 ,
  • a pump working space 35 is formed in extension of the pump piston 18 , in which via the electro-magnetic controllable suction valve 2 fuel is introduced.
  • the introduction of the fuel takes place during a downward movement of the pump piston 18, while at an upward movement of the pump piston 18 in the pump chamber 35 befindaji fuel is conveyed via a high-pressure outlet 39 with an inserted outlet valve 16 via a further high-pressure line in the high-pressure accumulator.
  • the high-pressure pump 1 is fuel-lubricated as a whole, the fuel is conveyed by the low pressure system in the camshaft space 5 , which is fluidly connected to the suction valve 2 .
  • This electro-magnetic controllable suction valve 2 and its functionality will be described below.
  • the electro-magnetically controllable suction valve 2 is opened and a connection of the pump working chamber 35 with the Fuel inlet 26 prepared so that the pump working chamber 35 via the suction valve 2 fuel is supplied.
  • the fuel supplied to the pump working chamber 35 is compressed and fed to a high-pressure accumulator (not shown) via the high-pressure valve 16 arranged in the high-pressure outlet 39 .
  • the suction valve 2 is closed when fuel delivery is to take place, and seals the pump working chamber 35 from the fuel inlet 26 from.
  • FIG. 2 attached to the high pressure pump 1 electromagnetically controllable suction valve 2, has a piston-shaped valve element 14 which is acted upon in the closing direction by the spring force of a spring 12, which is therefore hereinafter referred to as closing spring 12 .
  • the piston-shaped valve element 14 has a shaft 25, in particular a cylindrically shaped shaft 25, and an enlarged head 34 .
  • the pump cylinder head 27 has a valve seat 36 in the contact region to the closed valve element 14 .
  • the piston-shaped valve element 14 is guided via the shaft 25 in a bore 38 in the pump cylinder head 27 and has the enlarged diameter in relation to the shaft 25 head 34 .
  • a sealing surface 37 is formed, which comes to rest in the closed position of the valve element 14 on the valve seat 36 in the pump cylinder head 27 .
  • the pump working space 35 is disconnected from the fuel inlet 26 and no fuel can flow back.
  • FIG. 2 In addition, the elements of an electromagnetic actuator are shown: This has a magnet armature 10 with a cylindrical outer contour and a central bore 32 . A strong compression spring 4 is also embedded in this central bore 32 of the armature 10 , which exerts an axial force on the armature 10 to the valve element 14 out. The magnet armature 10 is also guided in a liftable axially movable in a carrier element 40 . In the radial direction, the magnet armature 10 surrounds a magnetic coil 6, which forms a magnetic field when energized and thus can exert a magnetic force on the magnet armature 10 .
  • the valve member 14 is directly or via an intermediate element 8 in contact with the armature 10, wherein both elements are not connected to each other in the axial direction, but are held together only by magnetic forces and spring forces in abutment.
  • the intermediate element 8 is introduced into the magnet armature 10 , in particular the intermediate element 8 can be pressed into the magnet armature 10 , so that a frictional connection is achieved.
  • the magnet armature 10 taken alone or the combination of the magnet armature 10 with the intermediate element 8 form an actuating element 8, 10.
  • the strong compression spring 4 acts on the intermediate element 8 and the armature 10. The strong compression spring ensures in the de-energized state that the intermediate element 8 acts on the valve element 14 and holds it in the open position.
  • the closing spring 12 counteracts, but since the strong compression spring 4 has a higher spring force, the valve element 14 is held in the open state.
  • the armature 10 moves against the force of the compression spring 4 away from the valve member 14 to close the working air gap 28 .
  • the moving away of the intermediate element 8 loses the frictional contact to the valve member 14 whereby the valve member 14 moves toward the closed state by the force of the closing spring 12th In the fully closed state of the valve element 14 , this rests with the sealing surface 37 on the valve seat 36 of the and seals the pump working chamber 35 from the fuel inlet 26 from.
  • Fig. 3 section III shown shows the detailed contact area between the intermediate element 8 and the valve element 14. Both elements have mutually facing end faces, which may be at least partially in mechanical contact with each other.
  • Fig. 3 It can be seen that the regions of the mechanical contact 24 between the valve element 14 and the actuating element 8, 10 and the zone 22, in which cavitation can occur, are spatially separated from one another. This is achieved in that the mechanical contact between the actuating element 8, 10 and the valve element 14 is interrupted approximately centrally, since there is the zone 22 , can arise in the cavitation, and that the region of the mechanical contact 24 instead by means of an annular Contact area is arranged around the central zone of cavitation. This separation of the areas of mechanical contact 24 and the zone of cavitation 22 can be achieved by means of a trough-shaped recess 20 . This trough-shaped recess 20 is located in the two elements 8 and 14th
  • a further specification of the area of the mechanical contact is given by a spherical shaping of the contact contour 30 . Since the valve element 14 and the actuating element 8, 10 are guided and supported by different elements, it can lead to positioning errors of both elements to each other, resulting from angular errors or by a Desaxtechnik. This spherical shape of one or both surfaces of each of the valve element 14 and the actuating element 8, 10, which are in contact with each other, allows a tangential contact in the entire position error tolerance range and thus there is an always annular contact surface between the two elements 8 and 14. Through this annular contact surface Surface pressure and wear are reduced and the load capacity is increased by axial forces.
  • the respective shape of the trough-shaped recesses is different in the actuating element 8, 10 and in the valve element 14 , in particular, that the respective recesses are not formed congruent.
  • This shaping of the respective recesses of the actuating element 8, 10 and of the valve element 14 may be so represented that the respective recesses in the edge region of their cross-sectional dimension do not converge congruently, in particular that one of the two recesses has a larger cross section in the edge region.

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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 Ventil, insbesondere ein Saugventil, in einer Hochdruckpumpe eines Kraftstoffeinspritzsystems, mit den Merkmalen des Oberbegriffs des Anspruchs 1. Ferner betrifft die Erfindung ein Pumpe, insbesondere eine Hochdruckpumpe eines Kraftstoffeinspritzsystems, in der das Saugventil eingesetzt ist.The invention relates to a valve, in particular a suction valve, in a high-pressure pump of a fuel injection system, with the features of the preamble of claim 1. Furthermore, the invention relates to a pump, in particular a high-pressure pump of a fuel injection system, in which the suction valve is used.

Stand der TechnikState of the art

Eine Hochdruckpumpe eines Kraftstoffeinspritzsystems mit einem Saugventil ist durch die DE 10 2010 027 745 A1 bekannt. Das Saugventil weist ein Ventilelement auf, das zwischen einer Öffnungs- und einer Schließstellung beweglich ist und das mit einem Betätigungselement zumindest mittelbar in Kontakt ist. Durch das Betätigungselement kann eine Betätigungskraft auf das Ventilelement übertragen werden. Die Hochdruckpumpe weist ein Pumpengehäuse mit einem Gehäuseteil auf, in dem in einer Zylinderbohrung ein Pumpenkolben hubbweweglich angebracht ist, der in der Zylinderbohrung einen Pumpenarbeitsraum begrenzt. Der Pumpenarbeitsraum ist über das Saugventil mit einem Kraftstoffzulauf verbindbar und über ein Rückschlagventil mit einem Hochdruckspeicher verbindbar. Das Betätigungselement kann als Magnetanker ausgeführt sein oder als eine Kombination des Magnetankers mit einem Zwischenelement auf das Ventilelement wirkt, insbesondere eines eingepressten Zwischenelements. Der Magnetanker ist Teil eines elektromagnetischen Aktors, der außerdem eine Magnetspule umfasst. Bei Bestromung der Magnetspule bildet sich ein Magnetfeld aus wodurch sich der Magnetanker relativ zur Magnetspule gegen eine Federkraft bewegt um den Arbeitsluftspalt zu schließen.A high-pressure pump of a fuel injection system with a suction valve is through DE 10 2010 027 745 A1 known. The suction valve has a valve element which is movable between an open and a closed position and which is at least indirectly in contact with an actuating element. By the actuating element, an actuating force can be transmitted to the valve element. The high-pressure pump has a pump housing with a housing part, in which a pump piston is mounted in a cylinder bore, which limits a pump working chamber in the cylinder bore. The pump working chamber can be connected via the suction valve with a fuel inlet and connected via a check valve with a high-pressure accumulator. The actuating element can be designed as a magnet armature or acts as a combination of the magnet armature with an intermediate element on the valve element, in particular a pressed intermediate element. The armature is part of an electromagnetic actuator, which also includes a magnetic coil. When the solenoid is energized, a magnetic field is formed whereby the armature moves relative to the solenoid against a spring force to close the working air gap.

Die aus der DE 10 2010 027 745 A1 bekannte Hochdruckpumpe eines Kraftstoffeinspritzsystems mit Saugventil, bei der alle vorangehend beschriebenen Elemente mit Kraftstoff umgeben sind, weist gewisse Nachteile auf. Im Kontaktbereich des Ventilelements und des Betätigungselements, die in axialer Richtung nicht miteinander verbunden sind, sondern nur durch magnetische Kräfte und Federkräfte in Anlage miteinander gehalten werden, kann eine relativ schnelle Wegbewegung des Betätigungselements vom Ventilelement, durch die Bestromung der Magnetspule, zwischen beiden Elementen zu einem Kontaktverlust und aufgrund des umspülenden Kraftstoffs zu Kavitation im Kontaktbereich führen, insbesondere in Form von Kaviationsblasen.The from the DE 10 2010 027 745 A1 known high-pressure pump of a fuel injection system with a suction valve, in which all the elements described above are surrounded by fuel, has certain disadvantages. In the contact region of the valve element and the actuating element, which are not connected to each other in the axial direction, but only by magnetic forces and spring forces in abutment with each other, a relatively fast movement of the actuator from the valve element, by the energization of the magnetic coil, between the two elements a contact loss and due to the circulating fuel lead to cavitation in the contact area, in particular in the form of cavitation bubbles.

Bei einer Implosion dieser Kavitationsblase können nun die Oberflächen der im Bereich der Kavitation befindlichen Flächen der Elemente beschädigt werden, was zu einer Funktionsbeeinträchtigung oder gar zu einer Verringerung der Lebensdauer des Saugventils und schlussendlich der Hochdruckpumpe führen kann.In the case of an implosion of this cavitation bubble, the surfaces of the surfaces of the elements located in the region of the cavitation can now be damaged, which can lead to a functional impairment or even to a reduction in the service life of the suction valve and ultimately of the high-pressure pump.

Die DE 10 2010 004 137 A zeigt ein Kraftstoffeinspritzventil mit einem Gehäuse und einer Betätigungsvorrichtung, die ein Ventilelement umfasst.The DE 10 2010 004 137 A shows a fuel injection valve with a housing and an actuator, which comprises a valve element.

Offenbarung der ErfindungDisclosure of the invention Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Ausgestaltung des Saugventils mit den Merkmalen aus Anspruch 1 hat den Vorteil, dass eine verbesserte Ausprägung der konstruktiven Elemente erreicht wird, die eine Schädigung der Oberflächen der beiden Element durch Kavitation und daraus resultierenden Kavitationsblasen verringert und/oder verhindert.The embodiment of the suction valve according to the invention with the features of claim 1 has the advantage that an improved expression of the structural elements is achieved, which reduces and / or prevents damage to the surfaces of the two elements by cavitation and resulting cavitation bubbles.

Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen des im Anspruch 1 angegebenen Saugventils möglich.The measures listed in the dependent claims advantageous developments of the suction valve specified in claim 1 are possible.

Durch eine ringförmige Anordnung des Bereichs des mechanischen Kontaktes um einen annähernd zentral gelegenen Bereich der Kavitation verbindet man den beschriebenen Vorteil des Anspruch 1 mit dem Vorteil einer höheren Belastbarkeit durch geringere Flächenpressung und einem daraus resultierenden geringeren Verschleiß im Kontaktbereich und damit einhergehend einer höheren Lebensdauer der Hochdruckpumpe.An annular arrangement of the region of the mechanical contact about an approximately centrally located region of the cavitation combines the described advantage of claim 1 with the advantage of a higher load capacity due to lower surface pressure and a resulting lower wear in the contact region and, consequently, a longer service life of the high-pressure pump ,

Speziell durch eine muldenförmige Aussparung am Betätigungselement und am Ventilelement ist es möglich, gezielt durch geometrische Ausformung und Größe der muldenförmigen Ausparung einen Kontakt der beiden Elemente in der Zone der Kavitation zu vermeiden.Specifically, by a trough-shaped recess on the actuating element and the valve element, it is possible to avoid contact of the two elements in the zone of cavitation targeted by geometric shape and size of the trough-shaped recess.

Außerdem kann durch eine ballige Ausformung der Kontaktkontur des Betätigungselementes und/oder Ventilelements dafür gesorgt werden, dass ein tangentialer Kontakt im gesamten Lagefehlertoleranzbereich gewährleistet wird und Winkelfehler und Desaxierungen zwischen Betätigungselement und Ventilelement ausgeglichen werden können.In addition, it can be ensured by a spherical shaping of the contact contour of the actuating element and / or valve element that a tangential contact in the entire position error tolerance range is guaranteed and angle errors and Desaxierungen between actuator and valve element can be compensated.

Ferner ist es möglich, dass das Betätigungselement des Ventilelements nicht direkt durch den Magnetanker ausgebildet ist, sondern dass ein Zwischenelement verwendet wird, welches formschlüssig mit dem Magnetanker verbunden ist. Das Betätigungselement kann somit entweder nur den Magnetanker aufweisen oder es weißt die Elemente Magnetankers und Zwischenelement auf.Further, it is possible that the actuating element of the valve element is not formed directly by the armature, but that an intermediate element is used, which is positively connected to the armature. The actuator can thus either have only the armature or it knows the elements magnet armature and intermediate element.

Durch die Verwendung eines Zwischenelementes wird es ermöglicht ein Material für das Zwischenelement auszuwählen, dass für die Belastungen im Kontaktbereich zum Ventilelement besser geeignet ist als das Material des Magnetankers, insbesondere im Hinblick auf die Paarung Zwischenelement zum Ventilelement und/oder zum umgebenden Kraftstoff.The use of an intermediate element makes it possible to select a material for the intermediate element which is better suited for the stresses in the contact region to the valve element than the material of the magnet armature, in particular with regard to the mating intermediate element to the valve element and / or to the surrounding fuel.

In Weiterbildung der Erfindung ist eine muldenförmige Aussparung am Betätigungselement und am Ventilelement so geartet, dass eine unterschiedlich Ausformung beider Aussparungen erfolgt. Eine weitere Detaillierungsebene dieser unterschiedlichen Ausformung sieht vor, dass die jeweiligen Aussparungen im Randbereich Ihrer Querschnittsausdehnung nicht deckungsgleich auslaufen, insbesondere indem eine der beiden Ausparungen im Randbereich größer ausgeformt ist. Der Vorteil dieser spezifischen Ausgestaltung ist es, dass die Wahrscheinlichkeit eines wandgerichteten Blasenkollapses reduziert werden kann.In a further development of the invention, a trough-shaped recess on the actuating element and the valve element is such that a different shape of both recesses takes place. A further level of detailing this different shape provides that the respective recesses in the edge region of your cross-sectional dimension do not run off congruent, in particular by one of the two recesses in the edge region is formed larger. The advantage of this specific embodiment is that the likelihood of a wall-directed bubble collapse can be reduced.

Zeichnungdrawing

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen:

Figur 1
eine Pumpe in einem Längsschnitt,
Figur 2
einen in Figur 1 mit II bezeichneten Ausschnitt der Pumpe in vergrößerter Darstellung mit einem Saugventil,
Figur 3
einen in Figur 2 mit III bezeichneten Ausschnitt des Saugventils in vergrößerter Darstellung.
An embodiment of the invention is illustrated in the drawing and explained in more detail in the following description. Show it:
FIG. 1
a pump in a longitudinal section,
FIG. 2
one in FIG. 1 with II designated section of the pump in an enlarged view with a suction valve,
FIG. 3
one in FIG. 2 With III designated section of the suction valve in an enlarged view.

Ausführliche Beschreibung der ZeichnungenDetailed description of the drawings

Fig. 1 zeigt eine Schnittdarstellung einer schematisch dargestellten Hochdruckpumpe 1, die als Kraftstoffhochdruckpumpe ausgebildet ist und vorzugsweise bei einem Common-Rail-Einspritzsystem verbaut ist. Mittels der Hochdruckpumpe 1 wird von einem Kraftstoffniederdrucksystem, das zumindest einen Tank, einen Filter und eine Niederdruckpumpe aufweist, bereitgestellter Kraftstoff in einen Hochdruckspeicher gefördert, aus dem der dort gespeicherte Kraftstoff von Kraftstoffinjektoren zur Einspritzung in zugeordnete Brennräume einer Brennkraftmaschine entnommen wird. Die Zubringung des Kraftstoffes zum Pumpenarbeitsraum erfolgt über ein elektro-magnetisches ansteuerbares Saugventil 2, wobei das elektromagnetisch ansteuerbare Saugventil nachfolgend noch erläutert wird, an der Hochdruckpumpe verbaut ist. Fig. 1 shows a sectional view of a high-pressure pump 1 shown schematically , which is designed as a high-pressure fuel pump and is preferably installed in a common-rail injection system. By means of the high pressure pump 1 is provided by a fuel low pressure system having at least one tank, a filter and a low pressure pump, provided fuel in a high-pressure accumulator, from which the fuel stored there is taken from fuel injectors for injection into the associated combustion chambers of an internal combustion engine. The delivery of the fuel to the pump working space via an electro-magnetic controllable suction valve 2, wherein the electromagnetically controllable suction valve will be explained below, is installed on the high-pressure pump.

Die Hochdruckpumpe 1 weist ein Pumpengehäuse 3 mit einem Nockenwellenraum 5 auf. In den Nockenwellenraum 5 ragt eine Nockenwelle 7 mit einem beispielsweise als Doppelnocken ausgebildeten Nocken 9 hinein. Die Nockenwelle 7 ist in zwei beidseits des Nockens 9 angeordnete und als Radiallager ausgebildeten Lagern in Form eines in dem Pumpengehäuse 3 angeordneten Gehäuselagers 11 und eines Flanschlagers 13, das in einem mit dem Pumpengehäuse 3 verbundenen Flansch 15, der den Nockenwellenraum 5 zur Umgebung hin dicht abschließt, gelagert. Der Flansch 15 weist eine durchgehende Öffnung auf, durch die ein antriebsseitiger Endabschnitt 17 der Nockenwelle 7 hindurch ragt. Der antriebsseitige Endabschnitt 17 weist beispielsweise eine Konus auf, auf den ein Antriebsrad aufgesetzt und gesichert ist. Das Antriebsrad ist beispielsweise als Riemenrad oder Zahnrad ausgebildet. Das Antriebsrad wird von der Brennkraftmaschine direkt oder indirekt beispielsweise über einen Riementrieb oder ein Zahnradgetriebe angetrieben.The high-pressure pump 1 has a pump housing 3 with a camshaft space 5 . In the camshaft space 5 protrudes a camshaft 7 with a trained example as a double cam cam 9 in. The camshaft 7 is arranged in two on both sides of the cam 9 and designed as a radial bearing bearings in the form of a arranged in the pump housing 3 housing bearing 11 and a flange bearing 13, in one with the pump housing 3 connected flange 15, which closes the camshaft space 5 close to the environment, stored. The flange 15 has a through opening through which a drive-side end portion 17 of the camshaft 7 protrudes. The drive-side end portion 17 has, for example, a cone on which a drive wheel is placed and secured. The drive wheel is formed for example as a pulley or gear. The drive wheel is driven by the internal combustion engine directly or indirectly, for example via a belt drive or a gear transmission.

In das Pumpengehäuse 3 ist weiterhin eine Stößelführung 19 eingelassen, in die ein eine Laufrolle 21 aufweisender Rollenstößel 23 eingesetzt ist. Die Laufrolle 21 läuft auf dem Nocken 9 der Nockenwelle 7 bei einer Drehbewegung derselben ab und der Rollenstößel 23 wird somit in der Stößelführung 19 translatorisch auf und ab bewegt. Dabei wirkt der Rollenstößel 23 mit einem Pumpenkolben 18 zusammen, der in einer in einem Pumpenzylinderkopf 27 ausgebildeten Zylinderbohrung 29 ebenfalls translatorisch auf und ab bewegbar angeordnet ist.In the pump housing 3 , a tappet guide 19 is further inserted, in which a roller 21 having a roller tappet 23 is inserted. The roller 21 runs on the cam 9 of the camshaft 7 during a rotational movement of the same and the roller tappet 23 is thus in the tappet guide 19 translationally moved up and down. In this case, the roller tappet 23 cooperates with a pump piston 18 , which is also arranged to be movable up and down in a translatable manner in a cylinder bore 29 formed in a pump cylinder head 27 .

In einem von der Stößelführung 19 und der Pumpenbohrung 29 gebildeten Stößelfederraum 31 ist eine Stößelfeder 33 angeordnet, die sich einerseits an dem Pumpenzylinderkopf 27 und andererseits an dem Rollenstößel 23 abstützt und eine dauerhafte Anlage der Laufrolle 21 auf dem Nocken 9 in Richtung der Nockenwelle 7 sicherstellt. In dem Pumpenzylinderkopf 27 ist in Verlängerung des Pumpenkolbens 18 ein Pumpenarbeitsraum 35 gebildet, in den über das elektro-magnetisches ansteuerbares Saugventil 2 Kraftstoff eingebracht wird. Die Einbringung des Kraftstoffs erfolgt bei einer Abwärtsbewegung des Pumpenkolbens 18, während bei einer Aufwärtsbewegung des Pumpenkolbens 18 in dem Pumpenarbeitsraum 35 befindlicher Kraftstoff über einen Hochdruckauslass 39 mit einem eingesetzten Auslassventil 16 über eine weiterführende Hochdruckleitung in den Hochdruckspeicher gefördert wird. Die Hochdruckpumpe 1 ist insgesamt kraftstoffgeschmiert, wobei der Kraftstoff von dem Niederdrucksystem in den Nockenwellenraum 5 gefördert wird, der mit dem Saugventil 2 strömungsverbunden ist. Dieses elektro-magnetisches ansteuerbare Saugventil 2 und dessen Funktionalität wird im Folgenden beschrieben.
Im Saugbetrieb der Hochdruckpumpe 1 ist das elektro-magnetisch ansteuerbare Saugventil 2 geöffnet und eine Verbindung des Pumpenarbeitsraums 35 mit dem Kraftstoffzulauf 26 hergestellt, so dass dem Pumpenarbeitsraum 35 über das Saugventil 2 Kraftstoff zugeführt wird. Im Förderbetrieb der Hochdruckpumpe 1 wird der dem Pumpenarbeitsraum 35 zugeführte Kraftstoff verdichtet und über das in dem Hochdruckauslass 39 angeordnete Hochdruckventil 16 einem Hochdruckspeicher (nicht dargestellt) zugeführt. Im Verdichtungsbetrieb der Hochdruckpumpe 1, bei dem sich der Pumpenkolben 18 aufwärts bewegt, ist das Saugventil 2 geschlossen, wenn eine Kraftstoffförderung erfolgen soll, und dichtet den Pumpenarbeitsraum 35 gegenüber dem Kraftstoffzulauf 26 ab.In one of the plunger guide 19 and the pump bore 29 formed plunger spring chamber 31 , a plunger spring 33 is arranged, which is supported on the one hand to the pump cylinder head 27 and on the other hand to the roller tappet 23 and ensures a permanent contact of the roller 21 on the cam 9 in the direction of the camshaft 7 , In the pump cylinder head 27 , a pump working space 35 is formed in extension of the pump piston 18 , in which via the electro-magnetic controllable suction valve 2 fuel is introduced. The introduction of the fuel takes place during a downward movement of the pump piston 18, while at an upward movement of the pump piston 18 in the pump chamber 35 befindlicher fuel is conveyed via a high-pressure outlet 39 with an inserted outlet valve 16 via a further high-pressure line in the high-pressure accumulator. The high-pressure pump 1 is fuel-lubricated as a whole, the fuel is conveyed by the low pressure system in the camshaft space 5 , which is fluidly connected to the suction valve 2 . This electro-magnetic controllable suction valve 2 and its functionality will be described below.
In the suction operation of the high-pressure pump 1 , the electro-magnetically controllable suction valve 2 is opened and a connection of the pump working chamber 35 with the Fuel inlet 26 prepared so that the pump working chamber 35 via the suction valve 2 fuel is supplied. In the delivery mode of the high-pressure pump 1 , the fuel supplied to the pump working chamber 35 is compressed and fed to a high-pressure accumulator (not shown) via the high-pressure valve 16 arranged in the high-pressure outlet 39 . In the compression operation of the high pressure pump 1, in which the pump piston 18 moves upward, the suction valve 2 is closed when fuel delivery is to take place, and seals the pump working chamber 35 from the fuel inlet 26 from.

Das in Fig. 2 dargestellte, an die Hochdruckpumpe 1 angebaute elektromagnetisch ansteuerbare Saugventil 2, weist ein kolbenförmiges Ventilelement 14 auf, welches in Schließrichtung von der Federkraft einer Feder 12 beaufschlagt wird, die daher nachfolgend als Schließfeder 12 bezeichnet wird. Das kolbenförmige Ventilelement 14 weist einen Schaft 25, insbesondere einen zylindrisch geformten Schaft 25, und einen vergrößerten Kopf 34 auf. Zudem weist der Pumpenzylinderkopf 27 im Kontakbereich zum geschlossenen Ventilelement 14 einen Ventilsitz 36 auf. Das kolbenförmige Ventilelement 14 ist über den Schaft 25 in einer Bohrung 38 in dem Pumpenzylinderkopf 27 geführt und weist den im Durchmesser gegenüber dem Schaft 25 vergrößerten Kopf 34 auf. An diesem vergrößerten Kopf 34 des Ventilelements 14 ist eine Dichtfläche 37 ausgebildet, die in Schließstellung des Ventilelements 14 an dem Ventilsitz 36 im Pumpenzylinderkopf 27 zur Anlage kommt. Dadurch ist der Pumpenarbeitsraum 35 vom Kraftstoffzulauf 26 getrennt und es kann kein Kraftstoff zurückströmen.This in Fig. 2 shown, attached to the high pressure pump 1 electromagnetically controllable suction valve 2, has a piston-shaped valve element 14 which is acted upon in the closing direction by the spring force of a spring 12, which is therefore hereinafter referred to as closing spring 12 . The piston-shaped valve element 14 has a shaft 25, in particular a cylindrically shaped shaft 25, and an enlarged head 34 . In addition, the pump cylinder head 27 has a valve seat 36 in the contact region to the closed valve element 14 . The piston-shaped valve element 14 is guided via the shaft 25 in a bore 38 in the pump cylinder head 27 and has the enlarged diameter in relation to the shaft 25 head 34 . At this enlarged head 34 of the valve element 14 , a sealing surface 37 is formed, which comes to rest in the closed position of the valve element 14 on the valve seat 36 in the pump cylinder head 27 . As a result, the pump working space 35 is disconnected from the fuel inlet 26 and no fuel can flow back.

In Fig. 2 werden zudem die Elemente eines elektromagnetischen Aktors dargestellt: Dieser weist einen Magnetanker 10 mit einer zylindrischen Außenkontur und einer zentrale Bohrung 32 auf. Eine starke Druckfeder 4 ist zudem in diese zentrale Bohrung 32 des Magnetankers 10 eingelassen, die eine axiale Kraft auf den Magnetanker 10 zum Ventilelement 14 hin ausübt. Der Magnetanker 10 wird zudem hubbeweglich in einem Trägerelement 40 axial geführt. In radialer Richtung umgibt den Magnetanker 10 eine Magnetspule 6, die bei Bestromung ein Magnetfeld ausbildet und somit eine magnetische Kraft auf den Magnetanker 10 ausüben kann.In Fig. 2 In addition, the elements of an electromagnetic actuator are shown: This has a magnet armature 10 with a cylindrical outer contour and a central bore 32 . A strong compression spring 4 is also embedded in this central bore 32 of the armature 10 , which exerts an axial force on the armature 10 to the valve element 14 out. The magnet armature 10 is also guided in a liftable axially movable in a carrier element 40 . In the radial direction, the magnet armature 10 surrounds a magnetic coil 6, which forms a magnetic field when energized and thus can exert a magnetic force on the magnet armature 10 .

Das Ventilelement 14 steht direkt oder über ein Zwischenelement 8 in Kontakt mit dem Magnetanker 10, wobei beide Elemente in axialer Richtung nicht miteinander verbunden sind, sondern nur durch magnetische Kräfte und Federkräfte in Anlage miteinander gehalten werden. Das Zwischenelement 8 ist in den Magnetanker 10 eingebracht, insbesondere kann das Zwischenelement 8 in den Magnetanker 10 einpresst sein, so dass eine kraftschlüssige Verbindung erzielt wird. Der Magnetanker 10 für sich genommen oder die Kombination des Magnetankers 10 mit dem Zwischenelement 8 bilden ein Betätigungselement 8, 10. In axialer Richtung wirkt die starke Druckfeder 4 auf das Zwischenelement 8 und den Magnetanker 10. Die starke Druckfeder sorgt in unbestromten Zustand dafür, dass das Zwischenelement 8 auf das Ventilelement 14 wirkt und es in geöffneter Position hält. Dem wirkt zwar die Schließfeder 12 entgegen, da jedoch die starke Druckfeder 4 eine höhere Federkraft besitzt wird das Ventilelement 14 in geöffnetem Zustand gehalten. Durch eine Bestromung des Magnetankers 10 mittels der Magnetspule 6 bewegt sich der Magnetanker 10 gegen die Kraft der Druckfeder 4 vom Ventilelement 14 weg, um den Arbeitsluftspalt 28 zu schließen. Durch das Wegbewegen verliert das Zwischenelement 8 den kraftschlüssigen Kontakt zum Ventilelement 14 wodurch sich das Ventilelement 14 durch die Kraft der Schließfeder 12 in Richtung geschlossener Zustand bewegt. In vollständig geschlossenem Zustand des Ventilelements 14 liegt dieses mit der Dichtfläche 37 am Ventilsitz 36 des an und dichtet den Pumpenarbeitsraum 35 gegenüber dem Kraftstoffzulauf 26 ab.The valve member 14 is directly or via an intermediate element 8 in contact with the armature 10, wherein both elements are not connected to each other in the axial direction, but are held together only by magnetic forces and spring forces in abutment. The intermediate element 8 is introduced into the magnet armature 10 , in particular the intermediate element 8 can be pressed into the magnet armature 10 , so that a frictional connection is achieved. The magnet armature 10 taken alone or the combination of the magnet armature 10 with the intermediate element 8 form an actuating element 8, 10. In the axial direction, the strong compression spring 4 acts on the intermediate element 8 and the armature 10. The strong compression spring ensures in the de-energized state that the intermediate element 8 acts on the valve element 14 and holds it in the open position. Although the closing spring 12 counteracts, but since the strong compression spring 4 has a higher spring force, the valve element 14 is held in the open state. By energizing the armature 10 by means of the magnetic coil 6 , the armature 10 moves against the force of the compression spring 4 away from the valve member 14 to close the working air gap 28 . By the moving away of the intermediate element 8 loses the frictional contact to the valve member 14 whereby the valve member 14 moves toward the closed state by the force of the closing spring 12th In the fully closed state of the valve element 14 , this rests with the sealing surface 37 on the valve seat 36 of the and seals the pump working chamber 35 from the fuel inlet 26 from.

Der in Fig. 3 dargestellte Auschnitt III zeigt den detaillierten Kontaktbereich zwischen dem Zwischelement 8 und dem Ventilelement 14. Beide Elemente haben einander zugewandte Stirnseiten, die zumindest teilweise miteinander in mechanischem Kontakt stehen können. In Fig. 3 ist zu erkennen, dass die Bereiche des mechanischen Kontakts 24 zwischen dem Ventilelement 14 und dem Betätigungselement 8, 10 und die Zone 22, in der Kavitation auftreten kann, räumlich voneinander getrennt sind. Dies wird dadurch erreicht, dass der mechanische Kontakt zwischen dem Betätigungselement 8, 10 und dem Ventilelement 14 annähernd zentral unterbrochen ist, da hier die Zone 22 vorhanden ist, in der Kavitation entstehen kann, und dass der Bereich des mechanischen Kontaktes 24 stattdessen mittels einer ringförmigen Kontaktfläche um die zentrale Zone der Kavitation angeordnet ist. Diese Trennung der Bereiche des mechanischen Kontaktes 24 und der Zone der Kavitation 22 kann mittels einer muldenförmigen Aussparung 20 erzielt werden. Diese muldenförmige Aussparung 20 befindet sich in den beiden Elementen 8 und 14.The in Fig. 3 section III shown shows the detailed contact area between the intermediate element 8 and the valve element 14. Both elements have mutually facing end faces, which may be at least partially in mechanical contact with each other. In Fig. 3 It can be seen that the regions of the mechanical contact 24 between the valve element 14 and the actuating element 8, 10 and the zone 22, in which cavitation can occur, are spatially separated from one another. This is achieved in that the mechanical contact between the actuating element 8, 10 and the valve element 14 is interrupted approximately centrally, since there is the zone 22 , can arise in the cavitation, and that the region of the mechanical contact 24 instead by means of an annular Contact area is arranged around the central zone of cavitation. This separation of the areas of mechanical contact 24 and the zone of cavitation 22 can be achieved by means of a trough-shaped recess 20 . This trough-shaped recess 20 is located in the two elements 8 and 14th

Eine weitere Spezifizierung des Bereichs des mechanischen Kontaktes ist durch eine ballige Ausformung der Kontaktkontur 30 gegeben. Da das Ventilelement 14 und des Betätigungselement 8, 10 durch unterschiedliche Elemente geführt und gelagert sind, kann es zu Positionierungsfehlern beider Elemente zueinander kommen, die sich durch Winkelfehler oder durch eine Desaxierung ergeben. Diese ballige Ausformung einer oder beider Flächen jeweils des Ventilelements 14 und des Betätigungselements 8, 10, die miteinander in Kontakt stehen, ermöglicht einen tangentialen Kontakt im gesamten Lagefehlertoleranzbereich und somit besteht eine stets ringförmige Kontaktfläche zwischen den beiden Elementen 8 und 14. Durch diese ringförmige Kontaktfläche werden Flächenpressung und Verschleiss reduziert und die Belastbarkeit durch axiale Kräft erhöht.A further specification of the area of the mechanical contact is given by a spherical shaping of the contact contour 30 . Since the valve element 14 and the actuating element 8, 10 are guided and supported by different elements, it can lead to positioning errors of both elements to each other, resulting from angular errors or by a Desaxierung. This spherical shape of one or both surfaces of each of the valve element 14 and the actuating element 8, 10, which are in contact with each other, allows a tangential contact in the entire position error tolerance range and thus there is an always annular contact surface between the two elements 8 and 14. Through this annular contact surface Surface pressure and wear are reduced and the load capacity is increased by axial forces.

Die jeweilige Gestalt der muldenförmigen Aussparungen ist im Betätigungselement 8, 10 und im Ventilelement 14 jeweils unterschiedlich geartet, insbesondere dass die jeweiligen Aussparungen nicht deckungsgleich ausgeformt sind. Diese Ausformung der jeweiligen Aussparungen des Betätigungselements 8, 10 und des Ventilelements 14 kann sich so darstellen, dass die jeweiligen Aussparungen im Randbereich Ihrer Querschnittsausdehnung nicht deckungsgleich auslaufen, insbesondere dass eine der beiden Aussparungen im Randbereich einen größeren Querschnitt aufweist.The respective shape of the trough-shaped recesses is different in the actuating element 8, 10 and in the valve element 14 , in particular, that the respective recesses are not formed congruent. This shaping of the respective recesses of the actuating element 8, 10 and of the valve element 14 may be so represented that the respective recesses in the edge region of their cross-sectional dimension do not converge congruently, in particular that one of the two recesses has a larger cross section in the edge region.

Claims (6)

  1. Valve, in particular suction valve (2), in a high-pressure pump of a fuel injection system, which has a valve element (14) which is movable between an open position and a closed position, with an actuating element (8, 10) which is at least indirectly in mechanical contact with the valve element (14) and by means of which an actuating force can be transmitted to the valve element (14), wherein, in the region of the mechanical contact between valve element (14) and actuating element (8, 10), the mechanical contact (24) between valve element (14) and actuating element (8, 10) is interrupted in a zone (22) in which cavitation can occur, wherein a mechanical contact between the two elements in the zone (22) in which cavitation can occur is avoided by means of a trough-shaped recess (20) on the actuating element (8, 10) and on the valve element (14), and wherein a trough-shaped recess (20) is provided in each case in the actuating element (8, 10) and in the valve element (14), characterized in that the respective recesses are formed differently, in particular not congruently.
  2. Valve according to Claim 1, characterized in that the zone in the region of contact in which cavitation can occur is arranged approximately centrally, and the region of mechanical contact (24) is arranged around the zone (22) of cavitation by means of an annular contact surface.
  3. Valve according to Claim 1, characterized in that the actuating element (8, 10) and/or the valve element (14) are/is of crowned form in the region of contact.
  4. Valve according to Claim 1, characterized in that a solenoid armature (10), or a solenoid armature (10) and an intermediate element (8) connected thereto, forms the actuating element (8, 10).
  5. Valve according to Claim 1, characterized in that the respective recesses (20) do not run out congruently in the edge region of their cross-sectional extent, in particular in that one of the two recesses has a larger cross section in the edge region.
  6. Pump, in particular high-pressure pump of a fuel injection system having a suction valve (2), characterized in that the suction valve (2) is designed according to at least one of the preceding claims.
EP16754216.6A 2015-09-21 2016-08-02 Valve, in particular suction valve, in a high-pressure pump of a fuel injection system Active EP3353411B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015218054.9A DE102015218054A1 (en) 2015-09-21 2015-09-21 Valve, in particular suction valve, in a high-pressure pump of a fuel injection system
PCT/EP2016/068379 WO2017050470A1 (en) 2015-09-21 2016-08-02 Valve, in particular suction valve, in a high-pressure pump of a fuel injection system

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EP3353411A1 EP3353411A1 (en) 2018-08-01
EP3353411B1 true EP3353411B1 (en) 2019-10-09

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DE (1) DE102015218054A1 (en)
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JP7019816B2 (en) * 2018-07-27 2022-02-15 日立Astemo株式会社 Fuel pump

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Publication number Priority date Publication date Assignee Title
DE19915686A1 (en) * 1999-04-07 2000-10-12 Delphi Tech Inc Switching valve
DE10148861A1 (en) * 2001-10-04 2003-04-24 Bosch Gmbh Robert Fuel injector, for an IC motor common rail fuel injection system, has a centered ball between the valve piston and jet needle with conical recesses at their ends against the ball
US7866575B2 (en) * 2009-01-12 2011-01-11 GM Global Technology Operations LLC Pressure actuated fuel injector
DE102010027745A1 (en) 2010-04-14 2011-10-20 Robert Bosch Gmbh high pressure pump
FR2973092B1 (en) * 2011-03-25 2016-09-02 Bosch Gmbh Robert SHUTTERING DEVICE, PRESSURE REGULATOR COMPRISING SUCH A DEVICE, DIESEL INJECTION DEVICE COMPRISING SUCH A REGULATOR, DIESEL ENGINE AND VEHICLE COMPRISING SUCH AN ENGINE
DE102012218593A1 (en) * 2012-10-12 2014-04-17 Continental Automotive Gmbh Valve for a pump

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DE102015218054A1 (en) 2017-03-23
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