EP3822475B1 - Vanne de dosage d'un fluide - Google Patents

Vanne de dosage d'un fluide Download PDF

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Publication number
EP3822475B1
EP3822475B1 EP20209959.4A EP20209959A EP3822475B1 EP 3822475 B1 EP3822475 B1 EP 3822475B1 EP 20209959 A EP20209959 A EP 20209959A EP 3822475 B1 EP3822475 B1 EP 3822475B1
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EP
European Patent Office
Prior art keywords
armature
spring
valve
stop element
valve needle
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
EP20209959.4A
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German (de)
English (en)
Other versions
EP3822475A1 (fr
Inventor
Andreas Glaser
Norbert Redlich
Martin Buehner
Matthias Boee
Peter Schramm
Christian Suenkel
Stefan Cerny
Joerg Abel
Marcel Behringer
Frank Mueller
Murat Ucal
Axel Heinstein
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP3822475A1 publication Critical patent/EP3822475A1/fr
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Publication of EP3822475B1 publication Critical patent/EP3822475B1/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
    • F02M51/0671—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
    • 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
    • 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
    • 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
    • F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for valve bodies
    • 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
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • F02M61/205—Means specially adapted for varying the spring tension or assisting the spring force to close the injection-valve, e.g. with damping of valve lift
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0075—Stop members in valves, e.g. plates or disks limiting the movement of armature, valve or spring

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 mount for a pre-stroke spring.
  • This configuration has the disadvantage that guidance between the armature and the valve needle is realized only over a short guidance length.
  • EP2789844 A1 discloses a valve for metering a fluid with an electromagnetic actuator and a valve needle that can be actuated by the actuator, with an armature of the actuator being guided on the valve needle, with a stop element being arranged on the valve needle, which limits a movement of the armature relative to the valve needle .
  • 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. In particular, improved guidance between the armature and the valve needle and the valve needle along a longitudinal axis of the housing can be implemented.
  • the design of the stop element according to the invention has the advantage that an advantageous flow of fuel in the area of the Stop element can be achieved without the inner bore of the inner pole must be increased.
  • 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 armature is adjusted by a spring to a stop that is stationary 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.
  • the guide length between the armature and the valve needle is increased.
  • the armature can be guided on its outside in the valve housing along the longitudinal axis.
  • the guidance of the valve needle along the longitudinal axis then improves accordingly due to the increased guidance length between the armature and the valve needle.
  • the result is correspondingly improved guidance of the armature relative to the housing.
  • the spring can immerse itself completely in the spring receptacle when it is actuated, so that an optimal compromise can be achieved in relation to several disadvantages of a conventional design.
  • the disadvantages of a conventional design relate firstly to manufacturability, costs and assembly if a design without a spring mount is implemented, in which an additional component is required to accommodate the spring and connect it to the armature.
  • Second Disadvantages arise when a pole face between the armature and the inner pole is reduced, since a lower magnetic force then occurs. This relates in particular to a possible configuration in which a stepped bore is designed on the inner pole in order to create space for a spring.
  • a third disadvantage relates to a magnetic short circuit across the spring and the associated loss of magnetic force, which results in slower force build-up and lower holding force in the open state. This usually affects the magnetic spring steel used, which represents a bypass for the magnetic flux between the armature and the inner pole.
  • a fourth disadvantage relates to the smaller contact surface between the armature and a stop ring in a variant in which the stop ring dips into the spring seat formed on the armature. This can cause increased wear and reduced hydraulic damping.
  • a fifth disadvantage may result in a lever arm between the upper needle guide and the armature, particularly in the above embodiment where the stop ring dips into the spring retainer. This can result in large needle deflection, leading to increased wear, skewing, and the like.
  • a sixth potential disadvantage relates to designs that require a large spring diameter. Due to the limited radial installation space, lower spring forces can then be realized, which is bad for rapid armature settling after the first injection, in particular with regard to multiple injections. With the same spring force, a larger spring diameter also means a larger tilting moment on the armature, which is also disadvantageous for the injector function and, in particular, can result in a tilted armature stop.
  • a seventh and last disadvantage relates to the risk of the spring bulging under load and the resulting contact with the inner pole and/or the stop ring due to a relatively long spring length and small radial space conditions. This leads to undefined friction, which, in addition to possible wear and the formation of particles, results in considerable scattering of the injection behavior.
  • the stop element can be made of a non-magnetic material, as a result of which it can separate the inner pole from the armature from a magnetic point of view.
  • the lever arm can be kept short. Both a pole face and a stop face between the armature and the stop element, in particular the stop ring, can be selected to be sufficiently large.
  • a relatively small inner diameter of the spring can be realized, so that relatively high spring forces can be achieved even with a comparatively thin wire thickness of the spring.
  • the spring can also be designed to be relatively short, so that the risk of buckling and wear that occurs accordingly is reduced and a tilting moment introduced in this regard on the armature remains within acceptable limits.
  • the armature can be guided in the housing. Furthermore, in a further possible configuration, an annular gap between the armature and the housing can be minimized. In relation to the specified housing dimensions, this results in a rapid build-up of force and a large holding force. Due to the intersection of the through-openings with the spring receptacle, the end face of the armature facing the inner pole can also be made larger than if separate through-openings are realized.
  • a further advantage is that the flow cross section can be increased disproportionately to the resulting reduction in the surface area of the end face of the armature.
  • 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 longitudinal axis 4 is defined by the housing 2 and serves as a reference for guiding a valve needle 5 arranged within the housing 2 . This means that the valve needle 5 should be aligned along the longitudinal axis 4 during operation.
  • 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 .
  • stops 7 ', 8' are formed.
  • the armature 6 can be moved between the stop elements 7, 8 when it is actuated, with an armature free path 9 being predetermined.
  • 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 L between an end face 22 facing the inner pole 3 and an end face 23 facing away from the inner pole 3 .
  • the armature 6 has a spring mount 25 .
  • the spring seat 25 is open on the end face 22 of the armature 6 .
  • the spring receptacle 25 has a length f along the longitudinal axis 4 between the end face 22 and a spring support surface 26 of the armature 6 .
  • the spring support surface 26 here represents the base 26 of the spring receptacle 25.
  • a spring 27 partially arranged in the spring receptacle 25 has a spring length F.
  • the spring length F is here the spring length F of the spring 27 in the non-actuated initial state.
  • the spring 27 supports this on the one hand on the spring support surface 26 of the armature 6 and on the other hand on the stop 7 'of the stop 7 from.
  • the spring length F is greater than the length f of the spring receptacle 25.
  • the spring 27 is shortened compared to its initial length F, and it can dip completely into the spring receptacle 25.
  • a guide web 28 is formed on the armature 6 .
  • the armature 6 has a (shortened) length l along the longitudinal axis 4 between the spring support surface 26 and the end face 23 . Without the guide web 28, only this shortened length l would be available as a guide length.
  • the guide bar 28 lengthens the length l by the length s of the guide bar 28 along the longitudinal axis 4 . This results in the guide length l+s in this exemplary embodiment.
  • the length s of the guide bar 28 is preferably chosen to be the same as or even greater than the length f of the spring receptacle 25 .
  • the guide length l + s of the armature 6 on the valve needle 5 is equal to or even greater than the length L 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 .
  • Possible configurations of the stop element 7, which allow an advantageous passage of the fluid, in particular fuel, are based on the Figures 5 to 8 described.
  • 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.
  • FIG. 2 shows a valve 1 in a partial, schematic sectional view corresponding to a second example not according to the invention.
  • a guide extension 40 is provided.
  • the guide extension 40 has a length s' along the longitudinal axis 4, by which the guide of the armature 6 on the valve needle 5 is extended. This means that in this example the guide length s′+l is realized along the longitudinal axis 4 between the armature 6 and the valve needle 5 .
  • the spring receptacle 25 it is thus possible in this example for the spring receptacle 25 to be directly adjacent to the valve needle 5 .
  • this facilitates the manufacture of the armature 6 since the spring receptacle 25 can be realized by a cylindrical recess aligned with the longitudinal axis 4 .
  • directly on the basic form 20 of the armature 6 only the length l which is shortened compared to the length L of the armature 6 between the end faces 22, 23 is available.
  • this shortened length l is lengthened by the length s′ via the guide extension 40 .
  • the length s′ can be predetermined in such a way that the guide length s′+l is equal to or even greater than the length L of the armature 6 between its end faces 22 , 23 .
  • the guide extension 40 is designed in the form of a sleeve. This means that an outer diameter 41 on the guide extension 40 is selected to be significantly smaller than an outer diameter 42 on the outside 32 of the armature 6.
  • the spring 27 is designed with ground spring ends 43, 44 in this example. This results in an even better edition. Furthermore, there is reduced wear and a more uniform 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.
  • FIGs 3 and 4 show possible configurations of the armature 6 of the valve 1 from FIG 1 III designated viewing direction, for better understanding, the valve needle 5 is shown as a sectional area.
  • the end face 22 is divided into sub-areas 22A and 22B, between which the spring receptacle 25 is provided.
  • through openings 51 to 54 are provided, which in this exemplary embodiment are configured as through bores 51 to 54 with a circular cross section. This results in intersections between the through bores 51 to 54 and the spring mount 25.
  • This means that the fuel can flow over the length f of the spring mount both through the part of the spring mount 25 not filled by the spring 27 and through the through openings 51 to 54 .
  • the fuel then flows over the shortened length l only through the through openings 51 to 54.
  • kidney-shaped configurations of the through-openings 51 to 54 are also implemented, so that the through-openings 51 to 54 extend in a circumferential direction 55 around the longitudinal axis 4 or circumferentially around the longitudinal axis 4 over a larger angular range.
  • the flow of fuel over the shortened length l of the armature 6 is improved in particular.
  • Figures 5 to 8 show possible configurations of the stop element 7 of the valve 1 contrary to the 1 View direction denoted by III, the valve needle 5 being shown in section for illustration purposes.
  • a support area 60 for the spring 27 is specified.
  • the support area 60 is delimited radially outwards by a broken line 60A.
  • the support area 60 is delimited radially inwards by a line 601 shown as a broken line.
  • the support area 60 serves as the structurally predetermined support area 60 in which the selected spring 27 is to be supported.
  • the Configurations preferably for an application in which a guide between the stop element 7 and the inner pole 3 is realized, as is the case, for example, in FIG 1 is illustrated.
  • Indentations 61 to 64 are provided in order to direct the fuel past the stop element 7 .
  • the stop element 7 can be modified by such indentations 61 to 64, starting from a basic hollow-cylindrical shape 65, which is characterized by an outer diameter D. This results in both the possibility of a guide on the outer diameter D and a fuel passage through the depressions 61 to 64.
  • the depressions 61 to 64 are designed here in such a way that, viewed from the longitudinal axis 4, they reach a maximum of a diameter d. This means that an annular surface 66 remains from the valve needle 5 to the diameter d.
  • the diameter d is set to be between the outer line 60A and the inner line 60l.
  • the spring 27 also rests at least partially on the support area 60 in the area of the depressions 61 to 64, namely at least on the annular surface 66. This results in a compromise between a good contact of the spring 27 on the support area 60 and the largest possible depressions 61 to 64 and at the same time the possibility of guiding on the outer diameter D.
  • FIGs 5 to 8 show different ways to perform the depressions 61 to 64.
  • figure 5 as an intersection with cylinder bores, 6 as intersections with rectangular cutouts, 7 as an intersection with flattening.
  • the flow cross section can be formed by ring segments.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Magnetically Actuated Valves (AREA)

Claims (4)

  1. Soupape (1) servant à doser un fluide, en particulier soupape d'injection de carburant pour moteurs à combustion interne, comportant un actionneur électromagnétique (10) et une aiguille de soupape (5) pouvant être actionnée par l'actionneur (10), dans laquelle une armature (6) de l'actionneur (10) est guidée sur l'aiguille de soupape (5), dans laquelle un élément de butée (7) est disposé sur l'aiguille de soupape (5), lequel limite un mouvement de l'armature (6) par rapport à l'aiguille de soupape (5), et dans laquelle l'armature (6) comprend un logement de ressort (25) ouvert en direction de l'élément de butée (7), logement de ressort dans lequel est inséré un ressort (27) supporté sur l'élément de butée (7),
    dans laquelle l'aiguille de soupape (5) est guidée par le biais de l'armature (6) et/ou de l'élément de butée (7) le long d'un axe longitudinal (4) d'un boîtier (2) et en ce que, considérée le long de l'axe longitudinal (4), une longueur (f) du logement de ressort (25) est inférieure à une longueur (F) du ressort (27) à l'état initial non actionné,
    caractérisée en ce que
    l'élément de butée (7) est basé sur une forme de base cylindrique creuse de diamètre extérieur déterminé (D) par rapport à l'axe longitudinal (4) et en ce que, sur un côté extérieur de la forme de base (65), au moins un évidement (61 - 64) est réalisé jusqu'à un diamètre déterminé (d) par rapport à l'axe longitudinal, et en ce qu'une région de support (60) pour le ressort (27) est située à l'intérieur du diamètre extérieur déterminé (D) de l'élément de butée (7) et à l'extérieur du diamètre déterminé (d) de l'élément de butée (7), une nervure de guidage (28) tournée vers l'élément de butée (7) étant réalisée sur l'armature (6), laquelle nervure de guidage guide l'armature (6) le long de l'axe longitudinal (4) sur l'aiguille de soupape (5).
  2. Soupape selon la revendication 1,
    caractérisée en ce que
    le ressort (27), lors de l'actionnement, peut être raccourci à la longueur (f) du logement de ressort (25) prédéfinie par le logement de ressort (25) de l'armature (6) .
  3. Soupape selon l'une des revendications 1 et 2,
    caractérisée en ce que
    l'armature (6) comprend au moins une ouverture traversante (51 - 54) s'étendant le long de l'axe longitudinal (4), laquelle intersecte le logement de ressort (25).
  4. Soupape selon la revendication 3,
    caractérisée en ce
    qu'au moins une ouverture traversante (51 - 54) est réalisée de manière allongée de façon réniforme dans une direction périphérique (55).
EP20209959.4A 2016-12-21 2017-10-19 Vanne de dosage d'un fluide Active EP3822475B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102016225776.5A DE102016225776A1 (de) 2016-12-21 2016-12-21 Ventil zum Zumessen eines Fluids
EP17786914.6A EP3559437B1 (fr) 2016-12-21 2017-10-19 Soupape servant à doser un fluide
PCT/EP2017/076701 WO2018114088A1 (fr) 2016-12-21 2017-10-19 Soupape servant à doser un fluide

Related Parent Applications (2)

Application Number Title Priority Date Filing Date
EP17786914.6A Division EP3559437B1 (fr) 2016-12-21 2017-10-19 Soupape servant à doser un fluide
EP17786914.6A Division-Into EP3559437B1 (fr) 2016-12-21 2017-10-19 Soupape servant à doser un fluide

Publications (2)

Publication Number Publication Date
EP3822475A1 EP3822475A1 (fr) 2021-05-19
EP3822475B1 true EP3822475B1 (fr) 2023-05-17

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ID=60138384

Family Applications (2)

Application Number Title Priority Date Filing Date
EP20209959.4A Active EP3822475B1 (fr) 2016-12-21 2017-10-19 Vanne de dosage d'un fluide
EP17786914.6A Active EP3559437B1 (fr) 2016-12-21 2017-10-19 Soupape servant à doser un fluide

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP17786914.6A Active EP3559437B1 (fr) 2016-12-21 2017-10-19 Soupape servant à doser un fluide

Country Status (7)

Country Link
US (1) US11359589B2 (fr)
EP (2) EP3822475B1 (fr)
JP (1) JP6845937B2 (fr)
KR (1) KR102394017B1 (fr)
CN (1) CN110100089B9 (fr)
DE (1) DE102016225776A1 (fr)
WO (1) WO2018114088A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018218682A1 (de) 2018-10-31 2020-04-30 Robert Bosch Gmbh Ventil zum Zumessen eines Fluids
DE102018219054A1 (de) 2018-11-08 2020-05-14 Robert Bosch Gmbh Ventil zum Zumessen eines Fluids
DE102018219543A1 (de) 2018-11-15 2020-05-20 Robert Bosch Gmbh Ventil zum Zumessen eines Fluids
DE102018222443A1 (de) 2018-12-20 2020-06-25 Robert Bosch Gmbh Ventil zum Zumessen eines Fluids

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DE102013222613A1 (de) 2013-11-07 2015-05-07 Robert Bosch Gmbh Ventil zum Zumessen von Fluid
EP3009655B1 (fr) * 2014-10-13 2017-08-23 Continental Automotive GmbH Soupape d'injection de carburant pour moteurs à combustion interne
DE102017207270A1 (de) * 2016-06-30 2018-01-04 Robert Bosch Gmbh Ventil zum Zumessen eines Fluids

Also Published As

Publication number Publication date
EP3822475A1 (fr) 2021-05-19
WO2018114088A1 (fr) 2018-06-28
KR20190097052A (ko) 2019-08-20
JP2020502423A (ja) 2020-01-23
US11359589B2 (en) 2022-06-14
CN110100089A (zh) 2019-08-06
EP3559437A1 (fr) 2019-10-30
JP6845937B2 (ja) 2021-03-24
US20190309712A1 (en) 2019-10-10
DE102016225776A1 (de) 2018-06-21
EP3559437B1 (fr) 2021-01-27
CN110100089B (zh) 2021-12-21
KR102394017B1 (ko) 2022-05-06
CN110100089B9 (zh) 2022-01-11

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