EP4033087B1 - Valve for metering a fluid - Google Patents

Valve for metering a fluid Download PDF

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Publication number
EP4033087B1
EP4033087B1 EP22157406.4A EP22157406A EP4033087B1 EP 4033087 B1 EP4033087 B1 EP 4033087B1 EP 22157406 A EP22157406 A EP 22157406A EP 4033087 B1 EP4033087 B1 EP 4033087B1
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EP
European Patent Office
Prior art keywords
armature
fluid channel
longitudinal axis
face
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.)
Active
Application number
EP22157406.4A
Other languages
German (de)
French (fr)
Other versions
EP4033087A1 (en
Inventor
Stefan Cerny
Murat Ucal
Jochen Rose
Andreas Glaser
Matthias Boee
Axel Heinstein
Nico HERRMANN
Martin Buehner
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
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Filing date
Publication date
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Publication of EP4033087A1 publication Critical patent/EP4033087A1/en
Application granted granted Critical
Publication of EP4033087B1 publication Critical patent/EP4033087B1/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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means
    • F02M51/0625—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures
    • F02M51/0664—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a cylindrically or partly cylindrically shaped armature, e.g. entering the winding; having a plate-shaped or undulated armature entering the winding
    • F02M51/0685—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a cylindrically or partly cylindrically shaped armature, e.g. entering the winding; having a plate-shaped or undulated armature entering the winding the armature and the valve being allowed to move relatively to each other or not being attached to each other
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
    • B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
    • B05B1/00—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means
    • B05B1/30—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to control volume of flow, e.g. with adjustable passages
    • B05B1/3033—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to control volume of flow, e.g. with adjustable passages the control being effected by relative coaxial longitudinal movement of the controlling element and the spray head
    • B05B1/304—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to control volume of flow, e.g. with adjustable passages the control being effected by relative coaxial longitudinal movement of the controlling element and the spray head the controlling element being a lift valve
    • B05B1/3046—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to control volume of flow, e.g. with adjustable passages the control being effected by relative coaxial longitudinal movement of the controlling element and the spray head the controlling element being a lift valve the valve element, e.g. a needle, co-operating with a valve seat located downstream of the valve element and its actuating means, generally in the proximity of the outlet orifice
    • B05B1/3053—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to control volume of flow, e.g. with adjustable passages the control being effected by relative coaxial longitudinal movement of the controlling element and the spray head the controlling element being a lift valve the valve element, e.g. a needle, co-operating with a valve seat located downstream of the valve element and its actuating means, generally in the proximity of the outlet orifice the actuating means being a solenoid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means
    • F02M51/0625—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures
    • F02M51/0664—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a cylindrically or partly cylindrically shaped armature, e.g. entering the winding; having a plate-shaped or undulated armature entering the winding
    • F02M51/0671—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a cylindrically or partly cylindrically shaped armature, e.g. entering the winding; having a plate-shaped or undulated armature entering the winding the armature having an elongated valve body attached thereto
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1893—Details of valve member ends not covered by groups F02M61/1866 - F02M61/188
    • 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
    • F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
    • F02M2200/304—Fuel-injection apparatus having mechanical parts, the movement of which is damped using hydraulic 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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/008—Arrangement of fuel passages inside of injectors

Definitions

  • the invention relates to a valve for metering a fluid, in particular a fuel injection valve for internal combustion engines.
  • the invention relates to the field of injectors for fuel injection systems in motor vehicles, in which fuel is preferably injected directly into the combustion chambers of an internal combustion engine.
  • a valve for metering fluid is known.
  • the known valve has an electromagnet for actuating a valve needle that controls an orifice.
  • the electromagnet is used to actuate an armature that can be moved on a valve needle.
  • the armature has a bore adjacent to the valve needle, which forms a spring receptacle for a pre-stroke spring.
  • the document JP 2015 218 664 A shows a fuel injection valve having an armature with an inclined bore.
  • the oblique bore extends in the longitudinal direction between a spring seat and a needle space.
  • the oblique bore extends radially outwards in the fuel flow direction.
  • the valve according to the invention with the features of claim 1 has the advantage that an improved design and mode of operation are made possible.
  • improved guidance between the armature and the valve needle, in particular a damping and calming of the armature, and at the same time an advantageous conduction of the fluid through an armature chamber can take place.
  • the armature that serves as the magnet armature is not firmly connected to the valve needle, but is mounted in a cantilevered manner between stops.
  • a stop can be formed on a stop element, which can be realized as a stop sleeve and/or a stop ring.
  • the stop element can also be formed in one piece with the valve needle.
  • the anchor is held in place by a spring Position of rest adjusted to a stationary stop with respect to the valve needle, so that the armature rests there.
  • the entire free travel of the armature is then available as an acceleration path, with the spring being shortened during acceleration.
  • the armature free travel can be specified via the axial play between the armature and the two stops.
  • a guide length between the armature and the valve needle can be increased by configuring the spring receptacle with an annular groove that is not adjacent to the valve needle.
  • the spring seat can advantageously be designed close to the longitudinal axis, i.e. at a small radial distance from the longitudinal axis, in order to enable the fluid to be advantageously introduced from the first region of the armature chamber into the spring seat with a corresponding design of the valve.
  • the resulting situation has the advantage of a low adhesion effect when the armature is released from the respective stop element during an actuation process, it also means that the damping desired for damping an impact or for calming the armature is reduced. Especially when the valve is closing, this can mean that, in relation to the desired control times, it takes too long to settle the armature sufficiently. In view of possibly very short pause times, for example less than 1.2 ms, as may be desired in the case of multiple injection, there are considerable disadvantages in a straight flow bore through the armature designed close to the valve needle.
  • a proposed fluid channel can advantageously allow fluid to be conducted through the armature space and at the same time an impairment of a damping behavior can be reduced, which is particularly advantageous for calming the armature when the valve closes.
  • a specification or setting of the desired damping can be achieved largely unaffected by the passage of the fluid through the armature.
  • a further development in which a point of a first opening of the fluid channel that is radially at most far outside of the longitudinal axis is closer to the longitudinal axis than a point of a second opening of the fluid channel that is radially at most far outside of the longitudinal axis, has the advantage that on the first end face of the Anchor advantageously a longitudinal axis near introduction of the fluid into the fluid channel, while on the second end face of the armature relocation of the opening of the fluid channel is possible in an area further away from the valve needle.
  • the maximum internal point of the second opening of the fluid channel can be located radially outside of a stop surface of the second stop element.
  • claim 3 has the advantage, among other things, that the ability to manufacture the fluid channel by means of a bore is made possible or improved.
  • a measure that is advantageous for this is specified in claim 4 .
  • the development according to claim 5 has the advantage that, on the one hand, the fluid channel can be configured in a way that is favorable in terms of flow technology.
  • an optimization with regard to a tilting angle with which an axis of the oblique bore is tilted relative to the longitudinal axis can be implemented in an advantageous manner, the tilting angle being, for example, given specifications for the opening on the second end face of the armature can be kept optimally small.
  • the cross section available for the passage of the fluid along the coaxial direction over the entire course through the armature can be enlarged as a result of the design of the oblique bore, if this makes sense in the respective application.
  • a combination of an armature free travel spring located in the armature can be implemented with an armature which has a fluid channel running radially outwards, in particular an inclined bore.
  • This combination makes it possible for a maximally large damping surface to be realized between a stop element and the armature.
  • a reduction in the damping area can be avoided by overlapping with the corresponding opening.
  • the configuration of a valve preferably provides for a plurality of fluid channels, which are preferably implemented instead of conventional through-flow bores, the functioning of the valve can be significantly influenced, in particular significantly improved damping.
  • two to ten fluid channels, in particular two to six fluid channels can be implemented.
  • Such fluid channels can at least partially include the spring receptacle together. This can also improve the flow behavior.
  • an embodiment with only a single fluid channel or a combination with at least one proposed fluid channel with at least one conventional through hole is also conceivable.
  • an embodiment can thus be implemented in which, with respect to a stop surface on the relevant stop element, there is no longer any overlapping between the relevant opening or the relevant openings of the at least one fluid channel and the stop surface on the stop element. This means that the maximum damping surface is available.
  • valve 1 shows a valve 1 for metering a fluid in a partial, schematic sectional view according to a first embodiment.
  • the valve 1 can be embodied in particular as a fuel injection valve 1 .
  • a preferred application is a fuel injection system in which such fuel injectors 1 are designed as high-pressure injectors 1 and are used for direct injection of fuel into associated combustion chambers of the internal combustion engine. Liquid or gaseous fuels can be used as the fuel. Accordingly, the valve 1 is suitable for metering liquid or gaseous fluids.
  • the valve 1 has a housing (valve housing) 2 in which an inner pole 3 is arranged in a stationary manner.
  • a valve needle 5 arranged within the housing 2 in this exemplary embodiment is guided along a longitudinal axis 4 with respect to the housing 2 .
  • An armature (magnetic armature) 6 is arranged on the valve needle 5 .
  • a stop element 7 and a further stop element 8 are also arranged on the valve needle 5 .
  • Stop surfaces 7', 8' are formed on stop elements 7, 8.
  • the armature 6 can be moved between the stop elements 7, 8 relative to the valve needle 5 when it is actuated along the longitudinal axis 4, with an armature free path 9 being predetermined.
  • the longitudinal axis 4 can be referred to here as the longitudinal axis 4 of the valve needle 5 or as the longitudinal axis 4 of the armature 5 .
  • the armature 6, the inner pole 3 and a magnet coil (not shown) are components of an electromagnetic actuator 10.
  • a valve closing body 11 is formed on the valve needle 5 and interacts with a valve seat surface 12 to form a sealing seat.
  • the armature 6 When the armature 6 is actuated, it is accelerated in the direction of the inner pole 3 . If the armature 6 hits the stop 7' of the stop element 7 and thereby actuates the valve needle 5, then fuel can be injected via the opened sealing seat and at least one nozzle opening 13 into a space, in particular a combustion chamber.
  • the valve 1 has a restoring spring 14, which moves the valve needle 5 via the stop element 7 into its initial position, in which the sealing seat is closed.
  • the armature 6 is based on a cylindrical basic shape 20 with a through hole 21 , the armature 6 being guided on the through hole 21 on the valve needle 5 .
  • the basic shape 20 of the armature 6 has a length 24 between a first face 22 of the armature 6 facing the inner pole 3 and a second face 23 of the armature 6 facing away from the inner pole 3 .
  • the armature 6 is arranged in an armature space 16 .
  • the first end face 22 adjoins a first region 17 of the armature space 16 .
  • the second end face 23 adjoins a second area 18 of the armature space 16 .
  • fuel can be conducted through the armature over at least part of its length 24 through at least one fluid channel 15 .
  • the armature 6 has a spring mount 25 .
  • the fluid channel 15 includes the spring mount 25 here.
  • the spring seat 25 on the end face 22 of the armature 6 is open.
  • a spring support surface 26 on which a spring 27 partially arranged in the spring seat 25 is supported is formed by the bottom 26 of the spring seat 25 .
  • the spring 27 is also supported on the stop surface 7 ′ of the stop 7 .
  • the spring 27 is designed with ground spring ends 43, 44 in this exemplary embodiment. This results in an even better edition. Furthermore, there is reduced wear and a more even introduction of force into the armature 6 on the spring support surface 26 on the one hand and on the stop 7′ of the stop element 7 on the other hand.
  • a guide bar 28 is formed on the armature 6 .
  • the guide length of the armature 6 on the valve needle 5 is equal to the length 24 of the armature 6 between its end faces 22, 23.
  • valve needle 5 is guided with respect to the longitudinal axis 4 or with respect to the housing 2 via the stop element 7 .
  • the valve needle 5 can additionally or alternatively also be guided via the armature 6 .
  • the outside 32 of the armature 6 extends at least partially to the inside 33 of the housing 2.
  • an annular gap can then be realized between the stop element 7 and the inner pole 3.
  • the fluid channel 15 has an inclined bore 50 .
  • the fluid channel 15 preferably has precisely one oblique bore 50 .
  • the fluid channel 15 then leads via the inclined bore 50 and at least part 51 of the spring mount 25.
  • a direction 19 which is coaxial with respect to the longitudinal axis 4 and which is oriented from the first end face 22 to the second end face 23, in an orientation opposite to an opening direction 52 in which the valve needle 5 is actuated when the valve 1 is opened.
  • the oblique bore 50 is designed in the armature 6 in such a way that it runs radially outwards along the coaxial direction 19, i.e. away from the longitudinal axis 4, with an angle of inclination in the plane of the drawing between the coaxial direction 19 and an axis 53 of the oblique bore 50 54 results.
  • the design of the oblique bore 50 is not limited to the axis 53 lying in the same plane as the longitudinal axis 4 of the valve needle 5, as is the case in the exemplary embodiment shown with the plane defined by the plane of the drawing.
  • the oblique bore 50 in this embodiment runs from the first end face 22 of the armature 6 to the second end face 23 of the armature 6.
  • a first opening 55 of the fluid channel 15, which adjoins the first region 17, is in the end face 22, while a second opening 56, which adjoins the second region 18, is located in the second end face 23.
  • An advantageous hydraulic connection between the first area 17 and the second area 18 is made possible by the inclined bore 50 running from the first end face 22 to the second end face 23 of the armature 6 .
  • the fluid in particular the fuel, can advantageously flow from the inner bore 31 of the inner pole 3 into the fluid channel 15 .
  • an inner part 57 of the second end face 23, on which the armature 6 with the second stop surface 8', can be specified to be sufficiently large in accordance with a predetermined and possibly large second stop surface 8', without the second opening 56 lying in this inner part 57 or without the fluid channel 15 intersecting this inner part 57 of the second end face 23.
  • a large damping surface can be realized between the second stop surface 8 ′ and the second end face 23 .
  • points 62, 63 at the second opening 56 there are points 62, 63 at the second opening 56, the point 62 being at a maximum distance from the longitudinal axis 4 at the edge of the second opening 56 and the point 63 being at a minimum distance from the longitudinal axis 4 at the edge of the second Opening 56 is located. Viewed radially, the point 62 is further away from the longitudinal axis 4 than the point 60. Furthermore, the point 63 of the second opening 56 is further away from the longitudinal axis 4, viewed radially, than the point 61 on the edge of the first opening 55. There is also a centroid 64 of the first opening 55 radially closer to the longitudinal axis 4 than a centroid 65 of the second opening 56.
  • the oblique bore 50 is also designed in such a way that the bottom 26 of the spring receptacle 25 is cut into by the oblique bore 50 .
  • the spring receptacle 25 can thus be used in an advantageous manner for conducting the fuel through and can be integrated into the fluid channel 15 over its entire length 58 .
  • the second opening 56 or a partial surface 56 ′ on the second end face 23 of the armature 6 is oriented perpendicular to the axis 53 of the oblique bore 50 .
  • the partial surface 56' of the armature 6 can be designed with a circumferential groove 85 or individual countersunk holes.
  • the partial surface 56 ′ on the second end face 23 of the armature 6 can first be designed, and then the oblique bore 50 can be drilled starting from the second end face 23 . This allows a drill bit to hit the partial surface 56' of the anchor 6 at right angles 1 described first embodiment, which is used in particular to improve drilling. In this way, breakage of a drill can also be avoided, since drilling does not take place at an angle to a surface.
  • the partial surface 56' is configured by a groove running around the longitudinal axis 4, from which the individual oblique bores 50 then spread out circumferentially .
  • FIG. 3 shows a valve 1 in a partial, schematic sectional view corresponding to a third example not according to the invention.
  • the armature 6 has a chamfer 66 which intersects the second end face 23 at its outside diameter 42 .
  • the chamfer 66 then lies between the second end face 23 and the outside 32 of the armature 6.
  • the chamfer 66 is preferably designed at right angles to the axis 53 of the oblique bore 50.
  • FIG. This configuration has the advantage that a production optimization is achieved, as is based on the 2 is described.
  • the inner part 57 of the second end face 23, on which the armature 6 interacts with the stop surface 8' can be designed to be as large as possible. This results in particularly great design freedom. A very large hydraulic damping can therefore be achieved in the respective application.
  • the fluid channel 15 has a first coaxial blind hole 71 and a second coaxial blind hole 72 .
  • the first coaxial blind hole 71 runs from the first end face 22 in the coaxial direction 19.
  • the second coaxial blind hole 72 runs from the second end face 23 in the opposite direction to the coaxial direction 19.
  • the two blind holes 71, 72 intersect with one another. Viewed along the longitudinal axis 4 , an intersection area 73 can be arranged close to the base 26 of the spring receptacle 25 . This results in favorable flow conditions.
  • the blind holes 71, 72 and at least part 51 of the spring receptacle 25 can then be used.
  • the spring receptacle 25 can also be advantageously at least partially integrated into the fluid channel 15 in this exemplary embodiment.
  • the fluid is guided radially outwards along the longitudinal axis 4 viewed in the coaxial direction 19 . This also results in an advantageous introduction of the fluid, starting from the inner bore 31 of the
  • a point 60 of a first opening 55 of the fluid channel 15 that is radially at most far outside of the longitudinal axis 4 is closer to the longitudinal axis 4 than a point 62 of a second opening 56 of the fluid channel 15 that is radially at most far outside of the longitudinal axis 4. It is also advantageous if a centroid 64 of a first opening 55 of the fluid channel 15 is closer to the longitudinal axis 4 than a centroid 65 of a second opening 56 of the fluid channel 15.
  • the fluid channel 15 exits at an exit surface 80 of the armature 6 towards the second region 18 of the armature space (16), with an axis 81 of the fluid channel 15, along which the fluid channel 15 at the exit surface 80 of the armature 6 exits, is oriented perpendicularly to the exit surface 80 .
  • This makes it possible, among other things, to form the fluid channel 15 from this side with a bore that can be introduced into the armature perpendicularly to the exit surface 80, which improves manufacturability.
  • the exit surface 80 can lie in an annular surface 82 that is circumferential with respect to the longitudinal axis 4, with the annular surface 82 being configured as a partial surface 82 of a cone shell 83 that is rotationally symmetrical with respect to the longitudinal axis 4, or as a partial surface 82 of a circular disk 84 oriented perpendicularly to the longitudinal axis 4. This is possible, for example, by designing a circumferential groove 85 or a chamfer 66 .

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Magnetically Actuated Valves (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Sampling And Sample Adjustment (AREA)
  • Catching Or Destruction (AREA)
  • Measuring Volume Flow (AREA)

Description

Stand der TechnikState of the art

Die Erfindung betrifft ein Ventil zum Zumessen eines Fluids, insbesondere ein Brennstoffeinspritzventil für Brennkraftmaschinen. Speziell betrifft die Erfindung das Gebiet der Injektoren für Brennstoffeinspritzanlagen von Kraftfahrzeugen, bei denen vorzugsweise eine direkte Einspritzung von Brennstoff in Brennräume einer Brennkraftmaschine erfolgt. Aus der DE 10 2013 222 613 A1 ist ein Ventil zum Zumessen von Fluid bekannt. Das bekannte Ventil weist einen Elektromagneten zum Betätigen einer eine Zumessöffnung steuernden Ventilnadel auf. Der Elektromagnet dient zum Betätigen eines auf einer Ventilnadel verschiebbaren Ankers. Hierbei weist der Anker eine an die Ventilnadel angrenzende Bohrung auf, die eine Federaufnahme für eine Vorhubfeder bildet.The invention relates to a valve for metering a fluid, in particular a fuel injection valve for internal combustion engines. In particular, the invention relates to the field of injectors for fuel injection systems in motor vehicles, in which fuel is preferably injected directly into the combustion chambers of an internal combustion engine. From the DE 10 2013 222 613 A1 a valve for metering fluid is known. The known valve has an electromagnet for actuating a valve needle that controls an orifice. The electromagnet is used to actuate an armature that can be moved on a valve needle. Here, the armature has a bore adjacent to the valve needle, which forms a spring receptacle for a pre-stroke spring.

Das Dokument JP 2015 218 664 A zeigt ein Kraftstoffeinspritzventil, das einem Anker mit einer Schrägbohrung aufweist. Die Schrägbohrung erstreckt sich in Längsrichtung zwischen einer Federaufnahme und einem Nadelraum. Die Schrägbohrung erstreckt sich in Kraftstoffströmungsrichtung radial nach außen.The document JP 2015 218 664 A shows a fuel injection valve having an armature with an inclined bore. The oblique bore extends in the longitudinal direction between a spring seat and a needle space. The oblique bore extends radially outwards in the fuel flow direction.

Offenbarung der ErfindungDisclosure of Invention

Das erfindungsgemäße Ventil mit den Merkmalen des Anspruchs 1 hat den Vorteil, dass eine verbesserte Ausgestaltung und Funktionsweise ermöglicht sind. Hierbei kann speziell eine verbesserte Führung zwischen dem Anker und der Ventilnadel, insbesondere eine Dämpfung und Beruhigung des Ankers, und zugleich eine vorteilhafte Durchleitung des Fluids durch einen Ankerraum erfolgen.The valve according to the invention with the features of claim 1 has the advantage that an improved design and mode of operation are made possible. Here, in particular, improved guidance between the armature and the valve needle, in particular a damping and calming of the armature, and at the same time an advantageous conduction of the fluid through an armature chamber can take place.

Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen des im Anspruch 1 angegebenen Ventils möglich.Advantageous further developments of the valve specified in claim 1 are possible as a result of the measures listed in the dependent claims.

Bei dem Ventil zum Zumessen des Fluids ist der als Magnetanker dienende Anker nicht fest mit der Ventilnadel verbunden, sondern zwischen Anschlägen fliegend gelagert. Solch ein Anschlag kann an einem Anschlagelement ausgebildet sein, das als Anschlaghülse und/oder Anschlagring realisiert werden kann. Das Anschlagelement kann allerdings auch einstückig mit der Ventilnadel ausgebildet sein. Über eine Feder wird der Anker im Ruhezustand an einen bezüglich der Ventilnadel ortsfesten Anschlag verstellt, so dass der Anker dort anliegt. Bei der Ansteuerung des Ventils steht dann der komplette Ankerfreiweg als Beschleunigungsstrecke zur Verfügung, wobei die Feder während der Beschleunigung verkürzt wird. Der Ankerfreiweg kann über das axiale Spiel zwischen dem Anker und den beiden Anschlägen vorgegeben werden.In the valve for metering the fluid, the armature that serves as the magnet armature is not firmly connected to the valve needle, but is mounted in a cantilevered manner between stops. Such a stop can be formed on a stop element, which can be realized as a stop sleeve and/or a stop ring. However, the stop element can also be formed in one piece with the valve needle. The anchor is held in place by a spring Position of rest adjusted to a stationary stop with respect to the valve needle, so that the armature rests there. When the valve is actuated, the entire free travel of the armature is then available as an acceleration path, with the spring being shortened during acceleration. The armature free travel can be specified via the axial play between the armature and the two stops.

Eine Führungslänge zwischen dem Anker und der Ventilnadel kann vergrößert werden, indem die Federaufnahme durch eine nicht an die Ventilnadel angrenzende Ringnut ausgestaltet wird. Hierbei kann die Federaufnahme in vorteilhafter Weise dennoch nahe an der Längsachse, also mit einem geringen radialen Abstand zu der Längsachse ausgestaltet werden, um bei einer entsprechenden Ausgestaltung des Ventils eine vorteilhafte Einleitung des Fluids von dem ersten Bereich des Ankerraums in die Federaufnahme zu ermöglichen.A guide length between the armature and the valve needle can be increased by configuring the spring receptacle with an annular groove that is not adjacent to the valve needle. In this case, the spring seat can advantageously be designed close to the longitudinal axis, i.e. at a small radial distance from the longitudinal axis, in order to enable the fluid to be advantageously introduced from the first region of the armature chamber into the spring seat with a corresponding design of the valve.

Bei einer Kombination aus einem Anker mit geraden Durchflussbohrungen und einem an der Ventilnadel angeordneten Anschlag mit großem Außendurchmesser ist es denkbar, dass es zu einer Überdeckung zwischen der Durchflussbohrung und einer an einem entsprechenden Anschlagelement ausgestalteten Anschlagfläche (Anschlag) kommt. Hierdurch geht ein Teil der Dämpfungsfläche zwischen dem Anker und dem diesbezüglichen Anschlagelement verloren. Ferner verringert sich im Bereich der Endstellungen des Ankers an den Anschlagelementen auch ein freier Durchflussquerschnitt.In the case of a combination of an armature with straight through-flow bores and a stop with a large outside diameter arranged on the valve needle, it is conceivable that there will be an overlap between the through-flow bore and a stop surface (stop) configured on a corresponding stop element. As a result, part of the damping surface between the armature and the relevant stop element is lost. Furthermore, a free flow cross section is also reduced in the area of the end positions of the armature on the stop elements.

Die sich ergebende Situation hat zwar den Vorteil eines geringen Adhäsionseffektes beim Lösen des Ankers von dem jeweiligen Anschlagelement bei einem Betätigungsvorgang, führt aber auch dazu, dass eine zur Dämpfung eines Anprallens beziehungsweise zur Ankerberuhigung gewünschte Dämpfung verringert wird. Speziell beim Schließen des Ventils kann dies dazu führen, dass in Bezug auf die gewünschten Ansteuerungszeiten eine zu lange Dauer zur ausreichenden Beruhigung des Ankers erforderlich ist. Im Hinblick auf gegebenenfalls sehr kurze Pausenzeiten, beispielsweise von weniger als 1,2 ms, wie sie bei einer Mehrfacheinspritzung gewünscht sein können, ergeben sich somit erhebliche Nachteile einer nahe an der Ventilnadel ausgestalteten geraden Durchflussbohrung durch den Anker.Although the resulting situation has the advantage of a low adhesion effect when the armature is released from the respective stop element during an actuation process, it also means that the damping desired for damping an impact or for calming the armature is reduced. Especially when the valve is closing, this can mean that, in relation to the desired control times, it takes too long to settle the armature sufficiently. In view of possibly very short pause times, for example less than 1.2 ms, as may be desired in the case of multiple injection, there are considerable disadvantages in a straight flow bore through the armature designed close to the valve needle.

In vorteilhafter Weise kann durch einen vorgeschlagenen Fluidkanal eine vorteilhafte Durchleitung von Fluid durch den Ankerraum erfolgen und zugleich eine Beeinträchtigung eines Dämpfungsverhaltens reduziert werden, was insbesondere für eine Beruhigung des Ankers beim Schließen des Ventils vorteilhaft ist. Hierdurch kann auch durch die konstruktive Ausgestaltung der Anschlagfläche an dem Anschlagelement zumindest weitgehend unbeeinflusst von der Durchleitung des Fluids durch den Anker eine Vorgabe beziehungsweise Einstellung der gewünschten Dämpfung erzielt werden.A proposed fluid channel can advantageously allow fluid to be conducted through the armature space and at the same time an impairment of a damping behavior can be reduced, which is particularly advantageous for calming the armature when the valve closes. As a result, at least through the structural design of the stop surface on the stop element a specification or setting of the desired damping can be achieved largely unaffected by the passage of the fluid through the armature.

Eine Weiterbildung, bei der ein von der Längsachse radial maximal weit außenliegender Punkt einer ersten Öffnung des Fluidkanals näher an der Längsachse liegt als ein von der Längsachse radial maximal weit außenliegender Punkt einer zweiten Öffnung des Fluidkanals, hat den Vorteil, dass an der ersten Stirnseite des Ankers in vorteilhafter Weise eine längsachsennahe Einleitung des Fluids in den Fluidkanal erfolgen kann, während an der zweiten Stirnseite des Ankers eine Verlegung der Öffnung des Fluidkanals in einen weiter von der Ventilnadel entfernten Bereich möglich ist. Bei der Weiterbildung nach Anspruch 2 ergibt sich insbesondere der Vorteil, dass eine Überlappung der Öffnung des Fluidkanals an der zweiten Stirnseite des Ankers mit einer Anschlagfläche an dem zweiten Anschlagelement verringert oder ganz vermieden werden kann. Speziell kann der maximal weit innenliegende Punkt der zweiten Öffnung des Fluidkanals radial außerhalb einer Anschlagfläche des zweiten Anschlagelements liegen. Entsprechende Vorteile können bei der Weiterbildung realisiert werden, bei der ein Flächenschwerpunkt einer ersten Öffnung des Fluidkanals näher an der Längsachse liegt als ein Flächenschwerpunkt einer zweiten Öffnung des Fluidkanals.A further development, in which a point of a first opening of the fluid channel that is radially at most far outside of the longitudinal axis is closer to the longitudinal axis than a point of a second opening of the fluid channel that is radially at most far outside of the longitudinal axis, has the advantage that on the first end face of the Anchor advantageously a longitudinal axis near introduction of the fluid into the fluid channel, while on the second end face of the armature relocation of the opening of the fluid channel is possible in an area further away from the valve needle. In the development according to claim 2, there is the particular advantage that overlapping of the opening of the fluid channel on the second end face of the armature with a stop surface on the second stop element can be reduced or completely avoided. In particular, the maximum internal point of the second opening of the fluid channel can be located radially outside of a stop surface of the second stop element. Corresponding advantages can be realized in the development in which a centroid of a first opening of the fluid channel is closer to the longitudinal axis than a centroid of a second opening of the fluid channel.

Die Weiterbildung nach Anspruch 3 hat unter anderem den Vorteil, dass eine Herstellbarkeit des Fluidkanals mittels einer Bohrung ermöglicht beziehungsweise verbessert wird. Eine hierfür vorteilhafte Maßnahme ist im Anspruch 4 angegebenen.The further development according to claim 3 has the advantage, among other things, that the ability to manufacture the fluid channel by means of a bore is made possible or improved. A measure that is advantageous for this is specified in claim 4 .

Die Weiterbildung nach Anspruch 5 hat den Vorteil, dass zum einen eine strömungstechnisch günstige Ausgestaltung des Fluidkanals realisiert werden kann. Hierbei kann gemäß der Weiterbildung nach Anspruch 6 in vorteilhafter Weise eine Optimierung im Hinblick auf einen Kippwinkel, mit dem eine Achse der Schrägbohrung gegenüber der Längsachse verkippt ist, realisiert werden, wobei der Kippwinkel beispielsweise bei gegebenen Vorgaben für die Öffnung an der zweiten Stirnseite des Ankers optimal klein gehalten werden kann. Ferner kann hierdurch der für die Durchleitung des Fluids zur Verfügung stehende Querschnitt entlang der koaxialen Richtung über den gesamten Verlauf durch den Anker in Folge der Ausgestaltung der Schrägbohrung vergrößert werden, wenn dies im jeweiligen Anwendungsfall sinnvoll ist.The development according to claim 5 has the advantage that, on the one hand, the fluid channel can be configured in a way that is favorable in terms of flow technology. Here, according to the development according to claim 6, an optimization with regard to a tilting angle with which an axis of the oblique bore is tilted relative to the longitudinal axis can be implemented in an advantageous manner, the tilting angle being, for example, given specifications for the opening on the second end face of the armature can be kept optimally small. Furthermore, the cross section available for the passage of the fluid along the coaxial direction over the entire course through the armature can be enlarged as a result of the design of the oblique bore, if this makes sense in the respective application.

Die Weiterbildung nach Anspruch 7 ermöglicht hierbei insbesondere eine Nutzung der Federaufnahme entlang ihrer gesamten Erstreckung entlang der Längsachse.The development according to claim 7 in particular enables the spring mount to be used along its entire extent along the longitudinal axis.

Somit kann in vorteilhafter Weise eine Kombination einer sich im Anker befindlichen Ankerfreiwegsfeder mit einem Anker realisiert werden, der einen radial nach außen verlaufenden Fluidkanal, insbesondere eine Schrägbohrung, aufweist. Diese Kombination ermöglicht, dass zwischen einem Anschlagelement und dem Anker eine maximal große Dämpfungsfläche realisiert werden kann. Speziell kann hierbei eine Reduzierung der Dämpfungsfläche durch eine Überlappung mit der entsprechenden Öffnung vermieden werden. Da bei der Ausgestaltung eines Ventils vorzugsweise mehrere Fluidkanäle vorgesehen sind, die vorzugsweise anstelle von herkömmlichen Durchflussbohrungen realisiert sind, kann sich ein wesentlicher Einfluss auf die Funktionsweise des Ventils, insbesondere eine deutlich verbesserte Dämpfung, ergeben. Beispielsweise können zwei bis zehn Fluidkanäle, insbesondere zwei bis sechs Fluidkanäle, realisiert werden. Solche Fluidkanäle können hierbei gemeinsam die Federaufnahme zumindest teilweise mit einbeziehen. Dadurch kann sich auch das Durchflussverhalten verbessern. Prinzipiell ist allerdings auch eine Ausgestaltung mit nur einem einzigen Fluidkanal oder eine Kombination mit zumindest einem vorgeschlagenen Fluidkanal mit zumindest einer herkömmlichen Durchgangsbohrung denkbar.Thus, in an advantageous manner, a combination of an armature free travel spring located in the armature can be implemented with an armature which has a fluid channel running radially outwards, in particular an inclined bore. This combination makes it possible for a maximally large damping surface to be realized between a stop element and the armature. In particular, a reduction in the damping area can be avoided by overlapping with the corresponding opening. Since the configuration of a valve preferably provides for a plurality of fluid channels, which are preferably implemented instead of conventional through-flow bores, the functioning of the valve can be significantly influenced, in particular significantly improved damping. For example, two to ten fluid channels, in particular two to six fluid channels, can be implemented. Such fluid channels can at least partially include the spring receptacle together. This can also improve the flow behavior. In principle, however, an embodiment with only a single fluid channel or a combination with at least one proposed fluid channel with at least one conventional through hole is also conceivable.

Speziell ist somit eine Ausgestaltung realisierbar, bei der es in Bezug auf eine Anschlagfläche an dem diesbezüglichen Anschlagelement zu keiner Überdeckung zwischen der diesbezüglichen Öffnung oder den diesbezüglichen Öffnungen des zumindest einen Fluidkanals und der Anschlagfläche am Anschlagelement mehr kommt. Dadurch steht die maximale Dämpfungsfläche zur Verfügung.In particular, an embodiment can thus be implemented in which, with respect to a stop surface on the relevant stop element, there is no longer any overlapping between the relevant opening or the relevant openings of the at least one fluid channel and the stop surface on the stop element. This means that the maximum damping surface is available.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Bevorzugte Ausführungsbeispiele der Erfindung sind in der nachfolgenden Beschreibung unter Bezugnahme auf die beigefügten Zeichnungen, in denen sich entsprechende Elemente mit übereinstimmenden Bezugszeichen versehen sind, näher erläutert. Es zeigen:

  • Fig. 1 ein Ventil in einer auszugsweisen, schematischen Schnittdarstellung entsprechend einem ersten Ausführungsbeispiel;
  • Fig. 2 ein Ventil in einer auszugsweisen, schematischen Schnittdarstellung entsprechend einem zweiten Ausführungsbeispiel;
  • Fig. 3 ein Ventil in einer auszugsweisen, schematischen Schnittdarstellung entsprechend einem dritten Ausführungsbeispiel und
  • Fig. 4 ein Ventil in einer auszugsweisen, schematischen Schnittdarstellung entsprechend einem vierten Ausführungsbeispiel.
Preferred exemplary embodiments of the invention are explained in more detail in the following description with reference to the attached drawings, in which corresponding elements are provided with the same reference symbols. Show it:
  • 1 a valve in a partial, schematic sectional view according to a first embodiment;
  • 2 a valve in a partial, schematic sectional view according to a second embodiment;
  • 3 a valve in a partial, schematic sectional view according to a third embodiment and
  • 4 a valve in a partial, schematic sectional view according to a fourth embodiment.

Ausführungsformen der ErfindungEmbodiments of the invention

Fig. 1 zeigt ein Ventil 1 zum Zumessen eines Fluids in einer auszugsweisen, schematischen Schnittdarstellung entsprechend einem ersten Ausführungsbeispiel. Das Ventil 1 kann insbesondere als Brennstoffeinspritzventil 1 ausgebildet sein. Ein bevorzugter Anwendungsfall ist eine Brennstoffeinspritzanlage, bei der solche Brennstoffeinspritzventile 1 als Hochdruckeinspritzventile 1 ausgebildet sind und zur direkten Einspritzungen von Brennstoff in zugeordnete Brennräume der Brennkraftmaschine dienen. Als Brennstoff können hierbei flüssige oder gasförmige Brennstoffe zum Einsatz kommen. Entsprechend eignet sich das Ventil 1 zum Zumessen von flüssigen oder gasförmigen Fluiden. 1 shows a valve 1 for metering a fluid in a partial, schematic sectional view according to a first embodiment. The valve 1 can be embodied in particular as a fuel injection valve 1 . A preferred application is a fuel injection system in which such fuel injectors 1 are designed as high-pressure injectors 1 and are used for direct injection of fuel into associated combustion chambers of the internal combustion engine. Liquid or gaseous fuels can be used as the fuel. Accordingly, the valve 1 is suitable for metering liquid or gaseous fluids.

Das Ventil 1 weist ein Gehäuse (Ventilgehäuse) 2 auf, in dem ortsfest ein Innenpol 3 angeordnet ist. Eine in diesem Ausführungsbeispiel innerhalb des Gehäuses 2 angeordneten Ventilnadel 5 ist bezüglich dem Gehäuse 2 entlang einer Längsachse 4 geführt.The valve 1 has a housing (valve housing) 2 in which an inner pole 3 is arranged in a stationary manner. A valve needle 5 arranged within the housing 2 in this exemplary embodiment is guided along a longitudinal axis 4 with respect to the housing 2 .

An der Ventilnadel 5 ist ein Anker (Magnetanker) 6 angeordnet. An der Ventilnadel 5 sind außerdem ein Anschlagelement 7 und ein weiteres Anschlagelement 8 angeordnet. An den Anschlagelementen 7, 8 sind Anschlagflächen 7', 8' ausgebildet. Der Anker 6 kann hierbei bei einer Betätigung entlang der Längsachse 4 relativ zu der Ventilnadel 5 zwischen den Anschlagelementen 7, 8 bewegt werden, wobei ein Ankerfreiweg 9 vorgegeben ist. Die Längsachse 4 kann hier als Längsachse 4 der Ventilnadel 5 beziehungsweise als Längsachse 4 des Ankers 5 bezeichnet werden. Der Anker 6, der Innenpol 3 sowie eine nicht dargestellte Magnetspule sind Bestandteile eines elektromagnetischen Aktuators 10.An armature (magnetic armature) 6 is arranged on the valve needle 5 . A stop element 7 and a further stop element 8 are also arranged on the valve needle 5 . Stop surfaces 7', 8' are formed on stop elements 7, 8. The armature 6 can be moved between the stop elements 7, 8 relative to the valve needle 5 when it is actuated along the longitudinal axis 4, with an armature free path 9 being predetermined. The longitudinal axis 4 can be referred to here as the longitudinal axis 4 of the valve needle 5 or as the longitudinal axis 4 of the armature 5 . The armature 6, the inner pole 3 and a magnet coil (not shown) are components of an electromagnetic actuator 10.

An der Ventilnadel 5 ist ein Ventilschließkörper 11 ausgebildet, der mit einer Ventilsitzfläche 12 zu einem Dichtsitz zusammenwirkt. Bei einer Betätigung des Ankers 6 wird dieser in Richtung auf den Innenpol 3 beschleunigt. Wenn der Anker 6 an dem Anschlag 7' des Anschlagelement 7 anschlägt und dadurch die Ventilnadel 5 betätigt, dann kann Brennstoff über den geöffneten Dichtsitz und zumindest eine Düsenöffnung 13 in einen Raum, insbesondere einen Brennraum, eingespritzt werden.A valve closing body 11 is formed on the valve needle 5 and interacts with a valve seat surface 12 to form a sealing seat. When the armature 6 is actuated, it is accelerated in the direction of the inner pole 3 . If the armature 6 hits the stop 7' of the stop element 7 and thereby actuates the valve needle 5, then fuel can be injected via the opened sealing seat and at least one nozzle opening 13 into a space, in particular a combustion chamber.

Das Ventil 1 weist eine Rückstellfeder 14 auf, die die Ventilnadel 5 über das Anschlagelement 7 in ihre Ausgangsstellung verstellt, in der der Dichtsitz geschlossen ist.The valve 1 has a restoring spring 14, which moves the valve needle 5 via the stop element 7 into its initial position, in which the sealing seat is closed.

Der Anker 6 basiert auf einer zylinderförmigen Grundform 20 mit einer Durchgangsbohrung 21, wobei der Anker 6 an der Durchgangsbohrung 21 an der Ventilnadel 5 geführt ist. Hierbei weist die Grundform 20 des Ankers 6 eine Länge 24 zwischen einer dem Innenpol 3 zugewandten ersten Stirnseite 22 des Ankers 6 und einer von dem Innenpol 3 abgewandten zweiten Stirnseite 23 des Ankers 6 auf. Der Anker 6 ist in einem Ankerraum 16 angeordnet. Hierbei grenzt die erste Stirnseite 22 an einen ersten Bereich 17 des Ankerraums 16 an. Ferner grenzt die zweite Stirnseite 23 an einen zweiten Bereich 18 des Ankerraums 16 an. Im Betrieb ist eine Durchleitung von Brennstoff durch den Anker über zumindest einen Teil seiner Länge 24 durch zumindest einen Fluidkanal 15 ermöglicht.The armature 6 is based on a cylindrical basic shape 20 with a through hole 21 , the armature 6 being guided on the through hole 21 on the valve needle 5 . Here, the basic shape 20 of the armature 6 has a length 24 between a first face 22 of the armature 6 facing the inner pole 3 and a second face 23 of the armature 6 facing away from the inner pole 3 . The armature 6 is arranged in an armature space 16 . In this case, the first end face 22 adjoins a first region 17 of the armature space 16 . Furthermore, the second end face 23 adjoins a second area 18 of the armature space 16 . During operation, fuel can be conducted through the armature over at least part of its length 24 through at least one fluid channel 15 .

Der Anker 6 weist eine Federaufnahme 25 auf. Der Fluidkanal 15 bezieht hierbei die Federaufnahme 25 mit ein. Somit führt der Fluidkanal 15 zumindest über einen Teil der Federaufnahme 25. Die Federaufnahme 25 an der Stirnseite 22 des Ankers 6 geöffnet. Eine Federstützfläche 26, an der eine teilweise in der Federaufnahme 25 angeordnete Feder 27 abgestützt ist, ist durch den Boden 26 der Federaufnahme 25 gebildet. Die Feder 27 stützt sich ferner an der Anschlagfläche 7' des Anschlags 7 ab. Bei einer Betätigung des Ankers 6 wird die Feder 27 gegenüber ihrer Ausgangslänge verkürzt, wobei sie vollständig in die Federaufnahme 25 eintauchen kann.The armature 6 has a spring mount 25 . The fluid channel 15 includes the spring mount 25 here. Thus, the fluid channel 15 leads at least over part of the spring seat 25. The spring seat 25 on the end face 22 of the armature 6 is open. A spring support surface 26 on which a spring 27 partially arranged in the spring seat 25 is supported is formed by the bottom 26 of the spring seat 25 . The spring 27 is also supported on the stop surface 7 ′ of the stop 7 . When the armature 6 is actuated, the spring 27 is shortened compared to its initial length, and it can dip completely into the spring receptacle 25 .

Ferner ist die Feder 27 in diesem Ausführungsbeispiel mit angeschliffenen Federenden 43, 44 ausgestaltet. Dadurch ergibt sich eine noch bessere Auflage. Ferner ergeben sich ein reduzierter Verschleiß sowie eine gleichmäßigere Krafteinleitung einerseits in den Anker 6 an der Federstützfläche 26 und andererseits an dem Anschlag 7' des Anschlagelements 7.Furthermore, the spring 27 is designed with ground spring ends 43, 44 in this exemplary embodiment. This results in an even better edition. Furthermore, there is reduced wear and a more even introduction of force into the armature 6 on the spring support surface 26 on the one hand and on the stop 7′ of the stop element 7 on the other hand.

An dem Anker 6 ist in diesem Ausführungsbeispiel ein Führungssteg 28 ausgebildet. Dadurch ist die Führungslänge des Ankers 6 an der Ventilnadel 5 gleich der Länge 24 des Ankers 6 zwischen seinen Stirnseiten 22, 23.In this exemplary embodiment, a guide bar 28 is formed on the armature 6 . As a result, the guide length of the armature 6 on the valve needle 5 is equal to the length 24 of the armature 6 between its end faces 22, 23.

Die Führung der Ventilnadel 5 bezüglich der Längsachse 4 beziehungsweise bezüglich des Gehäuses 2 ergibt sich in diesem Ausführungsbeispiel über das Anschlagelement 7. Hierbei ist das Anschlagelement 7 in einem Führungsbereich 30 an einer Innenbohrung 31 des Innenpols 3 geführt. Bei einer abgewandelten Ausgestaltung kann die Führung der Ventilnadel 5 zusätzlich oder alternativ auch über den Anker 6 realisiert werden. Hierbei reicht die Außenseite 32 des Ankers 6 zumindest teilweise bis an die Innenseite 33 des Gehäuses 2. Bei dieser Ausgestaltung kann anstelle des Führungsbereichs 30 dann ein Ringspalt zwischen dem Anschlagelement 7 und dem Innenpol 3 realisiert werden.In this exemplary embodiment, the valve needle 5 is guided with respect to the longitudinal axis 4 or with respect to the housing 2 via the stop element 7 . In a modified embodiment, the valve needle 5 can additionally or alternatively also be guided via the armature 6 . The outside 32 of the armature 6 extends at least partially to the inside 33 of the housing 2. In this embodiment, instead of the guide area 30, an annular gap can then be realized between the stop element 7 and the inner pole 3.

In diesem Ausführungsbeispiel weist der Fluidkanal 15 eine Schrägbohrung 50 auf. Hierbei weist der Fluidkanal 15 vorzugsweise genau eine Schrägbohrung 50 auf. Der Fluidkanal 15 führt dann über die Schrägbohrung 50 und zumindest einen Teil 51 der Federaufnahme 25.In this exemplary embodiment, the fluid channel 15 has an inclined bore 50 . In this case, the fluid channel 15 preferably has precisely one oblique bore 50 . The fluid channel 15 then leads via the inclined bore 50 and at least part 51 of the spring mount 25.

In diesem Ausführungsbeispiel ergibt sich eine bezüglich der Längsachse 4 koaxiale Richtung 19, die von der ersten Stirnseite 22 zu der zweiten Stirnseite 23 orientiert ist, in einer Orientierung entgegen einer Öffnungsrichtung 52, in der die Ventilnadel 5 beim Öffnen des Ventils 1 betätigt wird.In this exemplary embodiment, there is a direction 19 which is coaxial with respect to the longitudinal axis 4 and which is oriented from the first end face 22 to the second end face 23, in an orientation opposite to an opening direction 52 in which the valve needle 5 is actuated when the valve 1 is opened.

Die Schrägbohrung 50 ist so in dem Anker 6 ausgestaltet, dass sie entlang der koaxialen Richtung 19 radial nach außen, also von der Längsachse 4 weg, verläuft, wobei sich in der Zeichenebene zwischen der koaxialen Richtung 19 und einer Achse 53 der Schrägbohrung 50 ein Neigungswinkel 54 ergibt. Allerdings ist die Ausgestaltung der Schrägbohrung 50 nicht darauf beschränkt, dass die Achse 53 in der gleichen Ebene wie die Längsachse 4 der Ventilnadel 5 liegt, wie es in dem dargestellten Ausführungsbeispiel mit der durch die Zeichenebene gegebenen Ebene der Fall ist.The oblique bore 50 is designed in the armature 6 in such a way that it runs radially outwards along the coaxial direction 19, i.e. away from the longitudinal axis 4, with an angle of inclination in the plane of the drawing between the coaxial direction 19 and an axis 53 of the oblique bore 50 54 results. However, the design of the oblique bore 50 is not limited to the axis 53 lying in the same plane as the longitudinal axis 4 of the valve needle 5, as is the case in the exemplary embodiment shown with the plane defined by the plane of the drawing.

Ferner verläuft die Schrägbohrung 50 in diesem Ausführungsbeispiel von der ersten Stirnseite 22 des Ankers 6 zu der zweiten Stirnseite 23 des Ankers 6. Hierbei liegt eine erste Öffnung 55 des Fluidkanals 15, die an den ersten Bereich 17 angrenzt, in der Stirnseite 22, während eine zweite Öffnung 56, die an den zweiten Bereich 18 angrenzt, in der zweiten Stirnseite 23 liegt. Durch die von der ersten Stirnseite 22 bis zu der zweiten Stirnseite 23 des Ankers 6 verlaufende Schrägbohrung 50 wird eine vorteilhafte hydraulische Verbindung zwischen dem ersten Bereich 17 und dem zweiten Bereich 18 ermöglicht. Durch die achsnahe Positionierung der ersten Öffnung 55 an der Längsachse 4 kann ein Einströmen des Fluids, insbesondere des Brennstoffs, aus der Innenbohrung 31 des Innenpols 3 in vorteilhafter Weise in den Fluidkanal 15 erfolgen. Durch die achsferne Anordnung der zweiten Öffnung 56 des Fluidkanals 15 bezüglich der Längsachse 4 kann ein innerer Teil 57 der zweiten Stirnseite 23, an dem der Anker 6 mit der zweiten Anschlagfläche 8' zusammenwirkt, entsprechend einer vorgegebenen und gegebenenfalls großen zweiten Anschlagfläche 8' ausreichend groß vorgegeben werden, ohne dass die zweite Öffnung 56 in diesem inneren Teil 57 liegt beziehungsweise ohne dass der Fluidkanals 15 diesen inneren Teil 57 der zweiten Stirnseite 23 anschneidet. Hierdurch kann eine große Dämpfungsfläche zwischen der zweiten Anschlagfläche 8' und der zweiten Stirnseite 23 realisiert werden.Furthermore, the oblique bore 50 in this embodiment runs from the first end face 22 of the armature 6 to the second end face 23 of the armature 6. A first opening 55 of the fluid channel 15, which adjoins the first region 17, is in the end face 22, while a second opening 56, which adjoins the second region 18, is located in the second end face 23. An advantageous hydraulic connection between the first area 17 and the second area 18 is made possible by the inclined bore 50 running from the first end face 22 to the second end face 23 of the armature 6 . By positioning the first opening 55 on the longitudinal axis 4 close to the axis, the fluid, in particular the fuel, can advantageously flow from the inner bore 31 of the inner pole 3 into the fluid channel 15 . Due to the off-axis arrangement of the second opening 56 of the fluid channel 15 with respect to the longitudinal axis 4, an inner part 57 of the second end face 23, on which the armature 6 with the second stop surface 8', can be specified to be sufficiently large in accordance with a predetermined and possibly large second stop surface 8', without the second opening 56 lying in this inner part 57 or without the fluid channel 15 intersecting this inner part 57 of the second end face 23. As a result, a large damping surface can be realized between the second stop surface 8 ′ and the second end face 23 .

Da die Schrägbohrung 50 in vorteilhafter Weise über eine gesamte Länge 58 der Federaufnahme 25 entlang der Längsachse 4 mit der Federaufnahme 25 verschnitten ist, ergibt sich ein günstiges Strömungsverhalten und eine bezüglich der Federaufnahme 25 noch vergrößerte erste Öffnung 55 des Fluidkanals 15. Speziell liegt hierbei ein Punkt 60, an dem die erste Öffnung 55 radial maximal von der Längsachse 4 beabstandet ist, noch außerhalb der Federaufnahme 25. Ein Punkt 61, an dem die erste Öffnung 55 einen minimalen Abstand zu der Längsachse 4 hat, liegt hingegen noch am Rand der Federaufnahme 25. Ferner ergeben sich an der zweiten Öffnung 56 Punkte 62, 63, wobei der Punkt 62 maximal weit von der Längsachse 4 beabstandet an dem Rand der zweiten Öffnung 56 liegt und wobei der Punkt 63 minimal beabstandet zu der Längsachse 4 an dem Rand der zweiten Öffnung 56 liegt. Der Punkt 62 ist radial betrachtet weiter von der Längsachse 4 entfernt als der Punkt 60. Ferner ist der Punkt 63 der zweiten Öffnung 56 radial betrachtet weiter von der Längsachse 4 entfernt als der Punkt 61 auf dem Rand der ersten Öffnung 55. Ferner liegt ein Flächenschwerpunkt 64 der ersten Öffnung 55 radial näher an der Längsachse 4 als ein Flächenschwerpunkt 65 der zweiten Öffnung 56.Since the inclined bore 50 advantageously intersects with the spring mount 25 over an entire length 58 of the spring mount 25 along the longitudinal axis 4, this results in favorable flow behavior and a first opening 55 of the fluid channel 15 that is even larger than the spring mount 25 Point 60, at which the first opening 55 is at a maximum radial distance from the longitudinal axis 4, is still outside the spring mount 25. A point 61, at which the first opening 55 has a minimum distance from the longitudinal axis 4, however, is still at the edge of the spring mount 25. Furthermore, there are points 62, 63 at the second opening 56, the point 62 being at a maximum distance from the longitudinal axis 4 at the edge of the second opening 56 and the point 63 being at a minimum distance from the longitudinal axis 4 at the edge of the second Opening 56 is located. Viewed radially, the point 62 is further away from the longitudinal axis 4 than the point 60. Furthermore, the point 63 of the second opening 56 is further away from the longitudinal axis 4, viewed radially, than the point 61 on the edge of the first opening 55. There is also a centroid 64 of the first opening 55 radially closer to the longitudinal axis 4 than a centroid 65 of the second opening 56.

In diesem Ausführungsbeispiel ist die Schrägbohrung 50 außerdem so ausgestaltet, dass der Boden 26 der Federaufnahme 25 von der Schrägbohrung 50 angeschnitten ist. Somit kann die Federaufnahme 25 in vorteilhafter Weise zum Durchleiten des Brennstoffs genutzt werden und über ihre gesamte Länge 58 in den Fluidkanal 15 integriert werden.In this exemplary embodiment, the oblique bore 50 is also designed in such a way that the bottom 26 of the spring receptacle 25 is cut into by the oblique bore 50 . The spring receptacle 25 can thus be used in an advantageous manner for conducting the fuel through and can be integrated into the fluid channel 15 over its entire length 58 .

Fig. 2 zeigt ein Ventil 1 in einer auszugsweisen, schematischen Schnittdarstellung entsprechend einem zweiten Ausführungsbeispiel. In diesem Ausführungsbeispiel ist die zweite Öffnung 56 beziehungsweise eine Teilfläche 56' an der zweiten Stirnseite 23 des Ankers 6, in der die zweite Öffnung 56 liegt, senkrecht zu der Achse 53 der Schrägbohrung 50 orientiert. Die Teilfläche 56' des Ankers 6 kann hierbei über eine umlaufende Nut 85 oder einzelne Senkbohrungen ausgestaltet werden. Speziell kann zunächst die Teilfläche 56' an der zweiten Stirnseite 23 des Ankers 6 ausgestaltet werden, und dann kann die Schrägbohrung 50 ausgehend von der zweiten Stirnseite 23 gebohrt werden. Dies ermöglicht ein rechtwinkliges Auftreffen einer Bohrerspitze auf die Teilfläche 56' des Ankers 6. Somit ergibt sich insbesondere eine fertigungsoptimierte Abwandlung zu dem anhand der Fig. 1 beschriebenen ersten Ausführungsbeispiel, die insbesondere zur Verbesserung des Bohrens dient. Hierdurch kann auch ein Bruch eines Bohrers vermieden werden, da das Anbohren nicht schräg zu einer Oberfläche erfolgt. 2 shows a valve 1 in a partial, schematic sectional view according to a second embodiment. In this exemplary embodiment, the second opening 56 or a partial surface 56 ′ on the second end face 23 of the armature 6 , in which the second opening 56 lies, is oriented perpendicular to the axis 53 of the oblique bore 50 . The partial surface 56' of the armature 6 can be designed with a circumferential groove 85 or individual countersunk holes. In particular, the partial surface 56 ′ on the second end face 23 of the armature 6 can first be designed, and then the oblique bore 50 can be drilled starting from the second end face 23 . This allows a drill bit to hit the partial surface 56' of the anchor 6 at right angles 1 described first embodiment, which is used in particular to improve drilling. In this way, breakage of a drill can also be avoided, since drilling does not take place at an angle to a surface.

In Bezug auf mehrere an dem Anker 6 zu realisierende Schrägbohrungen, die entsprechend der Schrägbohrung 50 ausgestaltet sind, ist hierbei insbesondere eine Ausgestaltung der Teilfläche 56' durch eine um die Längsachse 4 umlaufende Nut, von der dann die einzelnen Schrägbohrungen 50 umfänglich verteilt ausgehen, vorteilhaft.With regard to several oblique bores to be realized on the armature 6, which are designed in accordance with the oblique bore 50, it is particularly advantageous if the partial surface 56' is configured by a groove running around the longitudinal axis 4, from which the individual oblique bores 50 then spread out circumferentially .

Fig. 3 zeigt ein Ventil 1 in einer auszugsweisen, schematischen Schnittdarstellung entsprechend einem dritten nicht erfindungsgemäßen Beispiel. In diesem Beispiel ist an dem Anker 6 eine Fase 66 ausgestaltet, die die zweite Stirnseite 23 an ihrem Außendurchmesser 42 anschneidet. Die Fase 66 liegt dann zwischen der zweiten Stirnseite 23 und der Außenseite 32 des Ankers 6. Vorzugsweise ist die Fase 66 im rechten Winkel zu der Achse 53 der Schrägbohrung 50 ausgestaltet. Diese Ausgestaltung hat zum einen den Vorteil, dass eine Fertigungsoptimierung erzielt ist, wie es entsprechend anhand der Fig. 2 beschrieben ist. Ferner kann der innere Teil 57 der zweiten Stirnseite 23, an dem der Anker 6 mit der Anschlagfläche 8' zusammenwirkt, maximal groß ausgestaltet werden. Dadurch ergeben sich besonders große konstruktive Freiheiten. Im jeweiligen Anwendungsfall kann daher eine sehr große hydraulische Dämpfung erzielt werden. 3 shows a valve 1 in a partial, schematic sectional view corresponding to a third example not according to the invention. In this example, the armature 6 has a chamfer 66 which intersects the second end face 23 at its outside diameter 42 . The chamfer 66 then lies between the second end face 23 and the outside 32 of the armature 6. The chamfer 66 is preferably designed at right angles to the axis 53 of the oblique bore 50. FIG. This configuration has the advantage that a production optimization is achieved, as is based on the 2 is described. Furthermore, the inner part 57 of the second end face 23, on which the armature 6 interacts with the stop surface 8', can be designed to be as large as possible. This results in particularly great design freedom. A very large hydraulic damping can therefore be achieved in the respective application.

Fig. 4 zeigt ein Ventil 1 in einer auszugsweisen, schematischen Schnittdarstellung entsprechend einem vierten nicht erfindungsgemäßen Beispiel. In diesem Beispiel weist der Fluidkanal 15 eine erste koaxiale Sacklochbohrung 71 und eine zweite koaxiale Sacklochbohrung 72 auf. Die erste koaxiale Sacklochbohrung 71 verläuft ausgehend von der ersten Stirnseite 22 in der koaxialen Richtung 19. Die zweite koaxiale Sacklochbohrung 72 verläuft ausgehend von der zweiten Stirnseite 23 entgegen der koaxialen Richtung 19. Innerhalb des Ankers 6 sind die beiden Sacklochbohrungen 71, 72 miteinander verschnitten. Ein Verschneidungsbereich 73 kann hierbei entlang der Längsachse 4 betrachtet nahe an dem Boden 26 der Federaufnahme 25 angeordnet werden. Dadurch ergeben sich günstige Strömungsverhältnisse. Beim Durchleiten des Fluids durch den Anker 6 können dann die Sacklochbohrungen 71, 72 und zumindest ein Teil 51 der Federaufnahme 25 genutzt werden. Hierdurch kann auch in diesem Ausführungsbeispiel die Federaufnahme 25 in vorteilhafter Weise zumindest teilweise in den Fluidkanal 15 integriert werden. Im Verschneidungsbereich 73 wird das Fluid in der koaxialen Richtung 19 betrachtet entlang der Längsachse 4 radial nach außen geführt. Hierdurch ergibt sich ebenfalls eine vorteilhafte Einleitung des Fluids ausgehend von der Innenbohrung 31 des 4 shows a valve 1 in a partial, schematic sectional view corresponding to a fourth example not according to the invention. In this example, the fluid channel 15 has a first coaxial blind hole 71 and a second coaxial blind hole 72 . The first coaxial blind hole 71 runs from the first end face 22 in the coaxial direction 19. The second coaxial blind hole 72 runs from the second end face 23 in the opposite direction to the coaxial direction 19. Within the armature 6, the two blind holes 71, 72 intersect with one another. Viewed along the longitudinal axis 4 , an intersection area 73 can be arranged close to the base 26 of the spring receptacle 25 . This results in favorable flow conditions. When the fluid is passed through the armature 6, the blind holes 71, 72 and at least part 51 of the spring receptacle 25 can then be used. In this way, the spring receptacle 25 can also be advantageously at least partially integrated into the fluid channel 15 in this exemplary embodiment. In the area of intersection 73 the fluid is guided radially outwards along the longitudinal axis 4 viewed in the coaxial direction 19 . This also results in an advantageous introduction of the fluid, starting from the inner bore 31 of the

Innenpols 3 in den Fluidkanal 15 und zugleich eine vorteilhafte Dämpfung an dem zweiten Anschlagelement 8.Inner pole 3 in the fluid channel 15 and at the same time an advantageous damping on the second stop element 8.

Vorteilhaft ist also insbesondere, dass ein von der Längsachse 4 radial maximal weit außenliegender Punkt 60 einer ersten Öffnung 55 des Fluidkanals 15 näher an der Längsachse 4 liegt als ein von der Längsachse 4 radial maximal weit außenliegender Punkt 62 einer zweiten Öffnung 56 des Fluidkanals 15. Ferner ist es vorteilhaft, wenn ein Flächenschwerpunkt 64 einer ersten Öffnung 55 des Fluidkanals 15 näher an der Längsachse 4 liegt als ein Flächenschwerpunkt 65 einer zweiten Öffnung 56 des Fluidkanals 15.It is therefore particularly advantageous that a point 60 of a first opening 55 of the fluid channel 15 that is radially at most far outside of the longitudinal axis 4 is closer to the longitudinal axis 4 than a point 62 of a second opening 56 of the fluid channel 15 that is radially at most far outside of the longitudinal axis 4. It is also advantageous if a centroid 64 of a first opening 55 of the fluid channel 15 is closer to the longitudinal axis 4 than a centroid 65 of a second opening 56 of the fluid channel 15.

Bei den vorgestellten Ausführungsbeispielen, die insbesondere anhand der Fig. 2 bis 4 beschrieben sind, ist in vorteilhafter Weise realisierbar, dass der Fluidkanal 15 an einer Austrittsfläche 80 des Ankers 6 zu dem zweiten Bereich 18 des Ankerraums (16) hin austritt, wobei eine Achse 81 des Fluidkanals 15, entlang der der Fluidkanal 15 an der Austrittsfläche 80 des Ankers 6 austritt, senkrecht zu der Austrittsfläche 80 orientiert ist. Dadurch ist es unter anderem möglich, den Fluidkanal 15 von dieser Seite her mit einer Bohrung auszubilden, die senkrecht zu der Austrittsfläche 80 in den Anker eingebracht werden kann, was die Herstellbarkeit verbessert. Die Austrittsfläche 80 kann hierbei in einer bezüglich der Längsachse 4 umlaufenden Ringfläche 82 liegen, wobei die Ringfläche 82 als Teilfläche 82 eines bezüglich der Längsachse 4 rotationssymmetrischen Kegelmantels 83 oder als Teilfläche 82 einer senkrecht zu der Längsachse 4 orientierten Kreisscheibe 84 ausgestaltet ist. Dies ist beispielsweise durch die Ausgestaltung einer umlaufenden Nut 85 oder einer Fase 66 möglich.In the exemplary embodiments presented, which are based in particular on the Figures 2 to 4 are described, it can be implemented in an advantageous manner that the fluid channel 15 exits at an exit surface 80 of the armature 6 towards the second region 18 of the armature space (16), with an axis 81 of the fluid channel 15, along which the fluid channel 15 at the exit surface 80 of the armature 6 exits, is oriented perpendicularly to the exit surface 80 . This makes it possible, among other things, to form the fluid channel 15 from this side with a bore that can be introduced into the armature perpendicularly to the exit surface 80, which improves manufacturability. The exit surface 80 can lie in an annular surface 82 that is circumferential with respect to the longitudinal axis 4, with the annular surface 82 being configured as a partial surface 82 of a cone shell 83 that is rotationally symmetrical with respect to the longitudinal axis 4, or as a partial surface 82 of a circular disk 84 oriented perpendicularly to the longitudinal axis 4. This is possible, for example, by designing a circumferential groove 85 or a chamfer 66 .

Die Erfindung ist nicht auf die beschriebenen Ausführungsbeispiele, sondern auf die folgenden Ansprüche beschränkt.The invention is not limited to the exemplary embodiments described, but rather to the following claims.

Claims (8)

  1. Valve (1) for metering a fluid, in particular a fuel injection valve for internal combustion engines, having an electromagnetic actuator (10) which has an armature (6) which is arranged in an armature chamber (16), and having a valve needle (5) which is able to be actuated by the actuator (10) by means of the armature (6), wherein the armature (6) is guided on the valve needle (5), wherein, on the valve needle (5), there are arranged a first stop element (7), which interacts with a first end face (22) of the armature (6) during operation, and a second stop element (8), which interacts with a second end face (23) of the armature (6) during operation, said stop elements limiting a movement of the armature (6) relative to the valve needle (5), and wherein the armature (6) has a spring receptacle (25) which is open towards the first end face (22) of the armature (6) and into which there is inserted a spring (27) which is supported against the stop element (7),
    wherein the armature (6) has at least one fluid channel (15) which, during operation, allows fluid to pass between a first region (17), adjoining the first end face (22) of the armature (6), of the armature chamber (16) and a second region (18), adjoining the second end face (23) of the armature (6), of the armature chamber (16), wherein the fluid channel (15) at least partially incorporates the spring receptacle (25), and wherein the fluid channel (15) at least sectionally extends radially outwards along a direction (19) which is oriented from the first end face (22) to the second face side (23) and which is coaxial with respect to a longitudinal axis (4), wherein the fluid channel (15) has at least one oblique bore (50) which extends at least radially outwards along the coaxial direction (19),
    characterized
    in that the oblique bore (50) intersects the spring receptacle (25), wherein the oblique bore (50) intersects the spring receptacle (25) over an entire length (58) of the spring receptacle (25) along the longitudinal axis (4), wherein a point (60) at which the oblique bore (50) is spaced radially apart furthest from the longitudinal axis (4) at the first end face (22) is still situated outside the spring receptacle (25).
  2. Valve according to Claim 1,
    characterized
    in that a point (61) of a first opening (55) of the fluid channel (15) that is situated radially furthest to the inside with respect to the longitudinal axis (4) is situated closer to the longitudinal axis (4) than a point (63) of a second opening (56) of the fluid channel (15) that is situated radially furthest to the inside with respect to the longitudinal axis (4).
  3. Valve according to Claim 1 or 2,
    characterized
    in that the fluid channel (15) emerges at an exit surface (80) of the armature (6) towards the second region (18) of the armature chamber (16), and in that an axis (81) of the fluid channel (15), along which the fluid channel (15) emerges at the exit surface (80) of the armature (6), is oriented perpendicularly to the exit surface (80) .
  4. Valve according to one of Claims 1 to 3,
    characterized
    in that the exit surface (80) is situated in an annular surface (82) which is peripheral with respect to the longitudinal axis (4), and in that the annular surface (82) is in the form of a part-surface (82) of a cone lateral surface (83) which is circularly symmetrical with respect to the longitudinal axis (4) or is in the form of a part-surface (82) of a circular disc (84) which is oriented perpendicularly to the longitudinal axis (4).
  5. Valve according to one of Claims 1 to 4,
    characterized
    in that the fluid channel (15) extends continuously radially outwards along the coaxial direction (19).
  6. Valve according to one of the preceding claims,
    characterized
    in that the oblique bore (50) extends from the first end face (22) of the armature (6) as far as the second end face (23) of the armature (6).
  7. Valve according to one of Claims 1 to 6,
    characterized
    in that the oblique bore (50) intersects the spring receptacle (25) in such a way that a base (26) of the spring receptacle (25) is incipiently cut by the oblique bore (50).
  8. Valve according to one of the preceding claims,
    characterized
    in that the spring receptacle (25) is formed by an annular groove which does not adjoin the valve needle (5), whereby a guide web (28) is formed on the armature (6).
EP22157406.4A 2017-05-10 2018-05-03 Valve for metering a fluid Active EP4033087B1 (en)

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DE102017207845.6A DE102017207845A1 (en) 2017-05-10 2017-05-10 Valve for metering a fluid
PCT/EP2018/061296 WO2018206382A1 (en) 2017-05-10 2018-05-03 Valve for metering a fluid
EP18722483.7A EP3622170A1 (en) 2017-05-10 2018-05-03 Valve for metering a fluid

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JP (2) JP2020519805A (en)
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DE19948238A1 (en) 1999-10-07 2001-04-19 Bosch Gmbh Robert Fuel injector
DE19950761A1 (en) * 1999-10-21 2001-04-26 Bosch Gmbh Robert Fuel injection valve has supporting ring between elastomeric ring and armature that supports elastomeric ring axially near opening of fuel channel in armature and radially on shoulder
DE10043085A1 (en) * 2000-09-01 2002-03-14 Bosch Gmbh Robert Fuel injector
US20030075621A1 (en) * 2001-10-05 2003-04-24 Siemens Automotive Corporation Fuel injection sleeve armature
JP2003232268A (en) * 2002-02-08 2003-08-22 Hitachi Ltd Solenoid operated fuel injection valve
US20030178509A1 (en) * 2002-03-19 2003-09-25 Visteon Global Technologies, Inc. Fuel injector with flux washer
JP2006017101A (en) * 2004-06-02 2006-01-19 Denso Corp Fuel injection valve
CN102094736B (en) * 2006-09-25 2012-09-05 株式会社日立制作所 Fuel injection valve
DE102007049945A1 (en) * 2007-10-18 2009-04-23 Robert Bosch Gmbh Fuel injector
KR101345431B1 (en) 2011-12-09 2013-12-27 주식회사 현대케피코 GDI fuel injector
DE102012202549A1 (en) * 2012-02-20 2013-08-22 Robert Bosch Gmbh Fuel injector
DE102013220791B4 (en) * 2013-10-15 2015-07-23 Continental Automotive Gmbh Injection valve for an internal combustion engine
DE102013222613A1 (en) 2013-11-07 2015-05-07 Robert Bosch Gmbh Valve for metering fluid
EP2918816B1 (en) * 2014-03-14 2017-09-06 Continental Automotive GmbH Fuel injector
JP6063894B2 (en) * 2014-04-23 2017-01-18 日立オートモティブシステムズ株式会社 Fuel injection device
JP6256188B2 (en) * 2014-05-19 2018-01-10 株式会社デンソー Fuel injection valve
EP2947306A1 (en) 2014-05-22 2015-11-25 Continental Automotive GmbH Injector for injecting fluid
EP3009663B1 (en) * 2014-10-15 2020-06-24 Vitesco Technologies GmbH Valve assembly and fluid injector
DE102015214171A1 (en) 2015-07-27 2017-02-02 Robert Bosch Gmbh Valve for metering a fluid
EP3156638B1 (en) * 2015-10-14 2020-03-18 Vitesco Technologies GmbH Fuel injector
DE102017222501A1 (en) 2017-12-12 2019-06-13 Robert Bosch Gmbh Valve for metering a fluid

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CN110612390B (en) 2022-05-31
JP2020519805A (en) 2020-07-02
WO2018206382A1 (en) 2018-11-15
JP7270684B2 (en) 2023-05-10
CN114876689B (en) 2023-09-01
KR102678806B1 (en) 2024-06-28
EP3622170A1 (en) 2020-03-18
KR20200003824A (en) 2020-01-10
CN114876689A (en) 2022-08-09
DE102017207845A1 (en) 2018-11-15
KR102673915B1 (en) 2024-06-12
US20200386199A1 (en) 2020-12-10
EP3779172A1 (en) 2021-02-17
EP4033087A1 (en) 2022-07-27
CN110612390A (en) 2019-12-24
US11852106B2 (en) 2023-12-26
JP2021179214A (en) 2021-11-18
EP3779172B1 (en) 2022-07-06

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