EP4033087B1 - Soupape de distribution d'un fluide - Google Patents

Soupape de distribution d'un fluide 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
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German (de)
English (en)
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EP4033087A1 (fr
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/fr
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Publication of EP4033087B1 publication Critical patent/EP4033087B1/fr
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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 .

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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)
  • Magnetically Actuated Valves (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Sampling And Sample Adjustment (AREA)
  • Catching Or Destruction (AREA)
  • Measuring Volume Flow (AREA)

Claims (8)

  1. Soupape (1) pour doser un fluide, notamment soupape d'injection de carburant pour moteurs à combustion interne, comprenant un actionneur électromagnétique (10), qui présente un induit (6) agencé dans une chambre d'induit (16), et une aiguille de soupape (5) pouvant être actionnée par l'actionneur (10) au moyen de l'induit (6), l'induit (6) étant guidé sur l'aiguille de soupape (5), un premier élément de butée (7) qui coopère en fonctionnement avec un premier côté frontal (22) de l'induit (6) et un deuxième élément de butée (8) qui coopère en fonctionnement avec un deuxième côté frontal (23) de l'induit (6) étant agencés sur l'aiguille de soupape (5), qui limitent un mouvement de l'induit (6) par rapport à l'aiguille de soupape (5), et l'induit (6) présentant un logement de ressort (25) ouvert vers le premier côté frontal (22) de l'induit (6), dans lequel est inséré un ressort (27) appuyé contre l'élément de butée (7),
    l'induit (6) présentant au moins un canal de fluide (15), qui, en fonctionnement, permet un passage de fluide entre une première zone (17) de la chambre d'induit (16) adjacente au premier côté frontal (22) de l'induit (6) et une deuxième zone (18) de la chambre d'induit (16) adjacente au deuxième côté frontal (23) de l'induit (6), le canal de fluide (15) intégrant au moins partiellement le logement de ressort (25), et le canal de fluide (15) s'étendant radialement vers l'extérieur, au moins par sections, le long d'une direction (19) orientée du premier côté frontal (22) vers le deuxième côté frontal (23) et coaxiale par rapport à un axe longitudinal (4), le canal de fluide (15) présentant au moins un alésage oblique (50) qui s'étend au moins radialement vers l'extérieur le long de la direction coaxiale (19),
    caractérisée en ce que
    l'alésage oblique (50) est intersecté avec le logement de ressort (25),
    l'alésage oblique (50) étant intersecté avec le logement de ressort (25) sur toute une longueur (58) du logement de ressort (25) le long de l'axe longitudinal (4), un point (60) auquel l'alésage oblique (50) est espacé radialement au maximum de l'axe longitudinal (4) sur le premier côté frontal (22) étant encore situé à l'extérieur du logement de ressort (25).
  2. Soupape selon la revendication 1, caractérisée en ce qu'un point (61) d'une première ouverture (55) du canal de fluide (15), situé radialement au maximum à l'intérieur de l'axe longitudinal (4), est plus proche de l'axe longitudinal (4) qu'un point (63) d'une deuxième ouverture (56) du canal de fluide (15), situé radialement au maximum à l'intérieur de l'axe longitudinal (4).
  3. Soupape selon la revendication 1 ou 2, caractérisée en ce que le canal de fluide (15) sort au niveau d'une surface de sortie (80) de l'induit (6) vers la deuxième zone (18) de la chambre d'induit (16) et en ce qu'un axe (81) du canal de fluide (15), le long duquel le canal de fluide (15) sort au niveau de la surface de sortie (80) de l'induit (6), est orienté perpendiculairement à la surface de sortie (80).
  4. Soupape selon l'une quelconque des revendications 1 à 3, caractérisée en ce que la surface de sortie (80) est située dans une surface annulaire (82) circonférentielle par rapport à l'axe longitudinal (4) et en ce que la surface annulaire (82) est conçue en tant que surface partielle (82) d'une enveloppe conique (83) à symétrie de rotation par rapport à l'axe longitudinal (4) ou en tant que surface partielle (82) d'un disque circulaire (84) orienté perpendiculairement à l'axe longitudinal (4) .
  5. Soupape selon l'une quelconque des revendications 1 à 4, caractérisée en ce que le canal de fluide (15) s'étend radialement vers l'extérieur de manière continue le long de la direction coaxiale (19).
  6. Soupape selon l'une quelconque des revendications précédentes, caractérisée en ce que l'alésage oblique (50) s'étend du premier côté frontal (22) de l'induit (6) jusqu'au deuxième côté frontal (23) de l'induit (6).
  7. Soupape selon l'une quelconque des revendications 1 à 6, caractérisée en ce que l'alésage oblique (50) est intersecté avec le logement de ressort (25) de telle sorte qu'un fond (26) du logement de ressort (25) est coupé par l'alésage oblique (50).
  8. Soupape selon l'une quelconque des revendications précédentes, caractérisée en ce que le logement de ressort (25) est réalisé par une rainure annulaire non adjacente à l'aiguille de soupape (5), ce qui permet de former une nervure de guidage (28) sur l'induit (6).
EP22157406.4A 2017-05-10 2018-05-03 Soupape de distribution d'un fluide Active EP4033087B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102017207845.6A DE102017207845A1 (de) 2017-05-10 2017-05-10 Ventil zum Zumessen eines Fluids
EP18722483.7A EP3622170A1 (fr) 2017-05-10 2018-05-03 Soupape servant à doser un fluide
PCT/EP2018/061296 WO2018206382A1 (fr) 2017-05-10 2018-05-03 Soupape servant à doser un fluide

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
EP18722483.7A Division EP3622170A1 (fr) 2017-05-10 2018-05-03 Soupape servant à doser un fluide

Publications (2)

Publication Number Publication Date
EP4033087A1 EP4033087A1 (fr) 2022-07-27
EP4033087B1 true EP4033087B1 (fr) 2023-08-30

Family

ID=62116435

Family Applications (3)

Application Number Title Priority Date Filing Date
EP20191515.4A Active EP3779172B1 (fr) 2017-05-10 2018-05-03 Soupape de dosage d'un fluide
EP18722483.7A Withdrawn EP3622170A1 (fr) 2017-05-10 2018-05-03 Soupape servant à doser un fluide
EP22157406.4A Active EP4033087B1 (fr) 2017-05-10 2018-05-03 Soupape de distribution d'un fluide

Family Applications Before (2)

Application Number Title Priority Date Filing Date
EP20191515.4A Active EP3779172B1 (fr) 2017-05-10 2018-05-03 Soupape de dosage d'un fluide
EP18722483.7A Withdrawn EP3622170A1 (fr) 2017-05-10 2018-05-03 Soupape servant à doser un fluide

Country Status (7)

Country Link
US (1) US11852106B2 (fr)
EP (3) EP3779172B1 (fr)
JP (2) JP2020519805A (fr)
KR (1) KR102673915B1 (fr)
CN (2) CN110612390B (fr)
DE (1) DE102017207845A1 (fr)
WO (1) WO2018206382A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN117795187A (zh) * 2021-05-28 2024-03-29 斯坦蒂内有限责任公司 燃料喷射器

Family Cites Families (21)

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DE19948238A1 (de) * 1999-10-07 2001-04-19 Bosch Gmbh Robert Brennstoffeinspritzventil
DE19950761A1 (de) * 1999-10-21 2001-04-26 Bosch Gmbh Robert Brennstoffeinspritzventil
DE10043085A1 (de) * 2000-09-01 2002-03-14 Bosch Gmbh Robert Brennstoffeinspritzventil
US20030075621A1 (en) * 2001-10-05 2003-04-24 Siemens Automotive Corporation Fuel injection sleeve armature
JP2003232268A (ja) * 2002-02-08 2003-08-22 Hitachi Ltd 電磁式燃料噴射弁
US20030178509A1 (en) * 2002-03-19 2003-09-25 Visteon Global Technologies, Inc. Fuel injector with flux washer
JP2006017101A (ja) 2004-06-02 2006-01-19 Denso Corp 燃料噴射弁
CN102094736B (zh) * 2006-09-25 2012-09-05 株式会社日立制作所 燃料喷射阀
DE102007049945A1 (de) * 2007-10-18 2009-04-23 Robert Bosch Gmbh Brennstoffeinspritzventil
KR101345431B1 (ko) * 2011-12-09 2013-12-27 주식회사 현대케피코 직분사 연료 인젝터
DE102012202549A1 (de) * 2012-02-20 2013-08-22 Robert Bosch Gmbh Brennstoffeinspritzventil
DE102013220791B4 (de) * 2013-10-15 2015-07-23 Continental Automotive Gmbh Einspritzventil für eine Verbrennungskraftmaschine
DE102013222613A1 (de) 2013-11-07 2015-05-07 Robert Bosch Gmbh Ventil zum Zumessen von Fluid
EP2918816B1 (fr) * 2014-03-14 2017-09-06 Continental Automotive GmbH Injecteur de carburant
JP6063894B2 (ja) * 2014-04-23 2017-01-18 日立オートモティブシステムズ株式会社 燃料噴射装置
JP6256188B2 (ja) * 2014-05-19 2018-01-10 株式会社デンソー 燃料噴射弁
EP2947306A1 (fr) * 2014-05-22 2015-11-25 Continental Automotive GmbH Injecteur pour injection de fluides
EP3009663B1 (fr) * 2014-10-15 2020-06-24 Vitesco Technologies GmbH Ensemble de soupape et injecteur de fluide
DE102015214171A1 (de) * 2015-07-27 2017-02-02 Robert Bosch Gmbh Ventil zum Zumessen eines Fluids
EP3156638B1 (fr) * 2015-10-14 2020-03-18 Vitesco Technologies GmbH Injecteur de carburant
DE102017222501A1 (de) * 2017-12-12 2019-06-13 Robert Bosch Gmbh Ventil zum Zumessen eines Fluids

Also Published As

Publication number Publication date
JP7270684B2 (ja) 2023-05-10
EP3779172A1 (fr) 2021-02-17
CN114876689A (zh) 2022-08-09
US20200386199A1 (en) 2020-12-10
DE102017207845A1 (de) 2018-11-15
WO2018206382A1 (fr) 2018-11-15
KR102673915B1 (ko) 2024-06-12
EP3622170A1 (fr) 2020-03-18
CN110612390B (zh) 2022-05-31
KR20200003824A (ko) 2020-01-10
EP4033087A1 (fr) 2022-07-27
US11852106B2 (en) 2023-12-26
CN114876689B (zh) 2023-09-01
JP2021179214A (ja) 2021-11-18
CN110612390A (zh) 2019-12-24
EP3779172B1 (fr) 2022-07-06
JP2020519805A (ja) 2020-07-02
KR20230043253A (ko) 2023-03-30

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