EP3822475A1 - Vanne de dosage d'un fluide - Google Patents

Vanne de dosage d'un fluide Download PDF

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Publication number
EP3822475A1
EP3822475A1 EP20209959.4A EP20209959A EP3822475A1 EP 3822475 A1 EP3822475 A1 EP 3822475A1 EP 20209959 A EP20209959 A EP 20209959A EP 3822475 A1 EP3822475 A1 EP 3822475A1
Authority
EP
European Patent Office
Prior art keywords
armature
spring
length
valve
stop element
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP20209959.4A
Other languages
German (de)
English (en)
Other versions
EP3822475B1 (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
Application granted granted Critical
Publication of EP3822475B1 publication Critical patent/EP3822475B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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 of 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 controlling a metering opening.
  • the electromagnet is used to actuate an armature that can be displaced on a valve needle.
  • the armature has a bore adjoining the valve needle which forms a spring receptacle for a forward stroke spring.
  • This embodiment has the disadvantage that a guide between the armature and the valve needle is only implemented over a short guide length.
  • the valve according to the invention with the features of claim 1 has the advantage that an improved design and functionality are made possible.
  • improved guidance between the armature and the valve needle and the valve needle can be implemented along a longitudinal axis of the housing.
  • the embodiment of the stop element according to the invention has the advantage that an advantageous fuel flow can be achieved in the area of the stop element without the inner bore of the inner pole having to be enlarged.
  • the armature serving as a magnet armature is not permanently connected to the valve needle, but rather is overhung between stops.
  • a stop can be formed on a stop element which can be implemented as a stop sleeve and / or stop ring.
  • the stop element can, however, also be designed in one piece with the valve needle.
  • the development according to claim 2 has the advantage that 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 is then correspondingly improved over the increased guide length between the armature and the valve needle.
  • the valve needle is guided via the stop element, for example on an inner pole arranged in a stationary manner in the housing, there is correspondingly improved guidance of the armature relative to the housing.
  • the further development according to claim 5 has the advantage that the guide extension can in particular be designed with an outer diameter that lies within the mouth openings of through openings of the armature, which are used to guide a fluid through the armature. This has a positive effect on the operating behavior.
  • the disadvantages of a conventional design relate firstly to the manufacturability, the costs and the assembly, if a design is implemented without a spring receptacle, in which an additional component is required to accommodate the spring and its connection to the armature. Secondly, there are disadvantages if a pole area between the armature and the inner pole is reduced, since a lower magnetic force then occurs. This relates in particular to a possible embodiment in which a stepped bore is made 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 a slower build-up of force and a lower holding force in the open state. This usually affects the magnetic spring steels used, which represent a bypass for the magnetic flux between the armature and the inner pole.
  • a fourth disadvantage relates to the smaller contact area between the armature and a stop ring in a variant in which the stop ring dips into the spring receptacle formed on the armature. This can result in increased wear and tear and reduced hydraulic damping.
  • a fifth disadvantage can result in a lever arm between the upper needle guide and the armature, which relates in particular to the above-mentioned embodiment in which the stop ring dips into the spring receptacle. This can result in a large deflection of the needle, which leads to increased wear, skewed striking and the like.
  • a sixth potential disadvantage relates to designs that require a large spring diameter. Because of the limited radial installation space, lower spring forces can then be achieved, which is bad for quick armature calming after the first injection, in particular with regard to multiple injections. With the same spring force, a larger spring diameter also means a greater 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 final 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 limited radial space. This leads to undefined friction, which, in addition to possible wear and the formation of particles, results in considerable variations in the injection behavior.
  • the stop element can be made of a non-magnetic material which allows it to 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 a stop ring, can be chosen 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 bulging and corresponding wear is reduced and a tilting moment applied to the armature in this regard remains within acceptable limits.
  • the development according to claim 8 enables an advantageous flow through the armature.
  • the armature can be guided in the housing.
  • an annular gap between the armature and the housing can be minimized. In relation to the given housing dimensions, this results in a quick build-up of force and a large holding force.
  • the end face of the armature facing the inner pole can also be made larger than if separate through openings are implemented.
  • the development according to claim 9 has the further advantage that the flow cross-section can be increased disproportionately to the reduction in the area of the end face of the armature caused thereby.
  • Fig. 1 shows a valve 1 for metering a fluid in a partial, schematic sectional illustration according to a first embodiment.
  • the valve 1 can in particular be designed as a fuel injector 1.
  • a preferred application is a fuel injection system in which such fuel injection valves 1 are designed as high-pressure injection valves 1 and are used for direct injection of fuel into assigned combustion chambers of the internal combustion engine. Liquid or gaseous fuels can be used as 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, which here 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 (magnet 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 on the stop elements 7, 8.
  • the armature 6 can be moved between the stop elements 7, 8 when actuated, an armature free path 9 being predetermined.
  • the armature 6, the inner pole 3 and a magnetic coil (not shown) are components of an electromagnetic actuator 10.
  • a valve closing body 11 On the valve needle 5, a valve closing body 11 is formed, which 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.
  • fuel can be injected into a space, in particular a combustion chamber, via the open sealing seat and at least one nozzle opening 13.
  • the valve 1 has a return spring 14 which moves the valve needle 5 via the stop element 7 into its starting 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 receptacle 25.
  • the spring receptacle 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 represents the bottom 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 unactuated initial state.
  • the spring 27 is supported 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.
  • the spring length F is greater than the length f of the spring receptacle 25.
  • the spring 27 is, however, shortened compared to its initial length F, whereby it can plunge completely into the spring receptacle 25.
  • a guide web 28 is formed on the armature 6. Between the spring support surface 26 and the end face 23, the armature 6 has a (shortened) length I along the longitudinal axis 4. Without the guide web 28, only this shortened length I would be available as a guide length.
  • the length I is lengthened by the length s of the guide web 28 along the longitudinal axis 4. This results in the guide length I + s in this exemplary embodiment.
  • the length s of the guide web 28 is preferably selected to be equal to or even greater than the length f of the spring receptacle 25.
  • the guide length I + 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.
  • the stop element 7 is guided in a guide region 30 on an inner bore 31 of the inner pole 3.
  • Possible configurations of the stop element 7, which enable the fluid, in particular fuel, to be advantageously passed through, are illustrated in FIG 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 up to the inside 33 of the housing 2.
  • an annular gap can then be implemented between the stop element 7 and the inner pole 3.
  • valve needle 5 can be advantageously guided along the longitudinal axis 4. This also results in an advantageous guidance between the armature 6 and the valve needle 5 over a guide length I + s, which is preferably not less than the length L.
  • Fig. 2 shows a valve 1 in a partial, schematic sectional view corresponding to a second embodiment.
  • 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 exemplary embodiment the guide length s ′ + I is implemented along the longitudinal axis 4 between the armature 6 and the valve needle 5.
  • the spring receptacle 25 can directly adjoin the valve needle 5. This particularly facilitates the manufacture of the armature 6, since the spring receptacle 25 can be realized by a cylindrical recess aligned on the longitudinal axis 4. As a result, however, only the length I, which is shortened compared to the length L of the armature 6, which it has between the end faces 22, 23, is available directly on the basic shape 20 of the armature 6. This shortened length I is hereby extended to a certain extent via the guide extension 40 by the length s'. Specifically, the length s 'can be specified in such a way that the guide length s' + I 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 shape of a sleeve. This means that an outside diameter 41 on the guide extension 40 is selected to be significantly smaller than an outside diameter 42 on the outside 32 of the armature 6.
  • the spring 27 is designed with ground spring ends 43, 44. This results in an even better print run. There are also a Reduced wear and a more uniform introduction of force, on the one hand, into armature 6 on spring support surface 26 and, on the other hand, on stop 7 ′ of stop element 7.
  • Figures 3 and 4 show possible configurations of the armature 6 of the valve 1 from FIG Fig. 1 Direction of view marked III, the valve needle 5 being shown as a cut surface for better understanding.
  • the end face 22 is divided into partial 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 designed 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 receptacle 25. This means that the fuel can flow over the length f of the spring receptacle both through the part of the spring receptacle 25 not filled by the spring 27 and through the through openings 51 to 54 .
  • the fuel then flows over the shortened length I only through the through openings 51 to 54.
  • This enables fuel to flow from the end face 22 to the end face 23 with little restriction, without affecting the total area of the end face 22, which is made up of the partial areas 22A, 22B composed, is further reduced.
  • This has a favorable effect on the control behavior when the armature 6 is actuated, since both a large magnetic force and a reduced hydraulic throttling result.
  • 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. In particular, this improves the fuel flow over the shortened length I of the armature 6.
  • Figures 5 to 8 show possible configurations of the stop element 7 of the valve 1 contrary to that in FIG Fig. 1
  • Direction of view denoted by III the valve needle 5 being shown in section for the purpose of illustration.
  • a support area 60 for the spring 27 is specified here.
  • the support region 60 is delimited radially outward by a line 60A shown in broken lines.
  • the support region 60 is delimited radially inward by a line 60I shown in broken lines.
  • the support area 60 serves as the structurally predetermined support area 60 in which the selected spring 27 is intended to be supported.
  • the refinements preferably relate to an application in which a guide is implemented between the stop element 7 and the inner pole 3, as is the case, for example, in FIG Fig. 1 is illustrated.
  • depressions 61 to 64 are provided.
  • the recesses 61 to 64 are designed here in such a way that, viewed from the longitudinal axis 4, they extend at most up to a diameter d. This means that an annular surface 66 remains from the valve needle 5 up to the diameter d.
  • the diameter d is preferably specified in such a way that it lies between the outer line 60A and the inner line 60I.
  • the spring 27 also rests at least partially, namely at least on the annular surface 66, on the support region 60 in the region of the depressions 61 to 64. This results in a compromise between good contact between the spring 27 and the support area 60 and the largest possible depressions 61 to 64 and, at the same time, the possibility of guidance on the outer diameter D.
  • FIGS. 5 to 8 show different ways of implementing the depressions 61 to 64.
  • Fig. 5 as an intersection with cylinder bores
  • Fig. 6 as intersections with rectangular cutouts
  • Fig. 7 as an intersection with flattened areas.
  • 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)
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
PCT/EP2017/076701 WO2018114088A1 (fr) 2016-12-21 2017-10-19 Soupape servant à doser un fluide
EP17786914.6A EP3559437B1 (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 true EP3822475A1 (fr) 2021-05-19
EP3822475B1 EP3822475B1 (fr) 2023-05-17

Family

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

Citations (5)

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Publication number Priority date Publication date Assignee Title
WO2001025614A1 (fr) * 1999-10-07 2001-04-12 Robert Bosch Gmbh Soupape d'injection de carburant
JP2010180758A (ja) * 2009-02-04 2010-08-19 Denso Corp 燃料噴射弁
EP2789844A1 (fr) * 2011-12-09 2014-10-15 Kefico Corporation Injecteur de carburant à injection directe
WO2015049195A1 (fr) * 2013-10-02 2015-04-09 Continental Automotive Gmbh Ensemble soupape d'une soupape d'injection
DE102013222613A1 (de) 2013-11-07 2015-05-07 Robert Bosch Gmbh Ventil zum Zumessen von Fluid

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US3707992A (en) * 1970-11-09 1973-01-02 Skinner Precision Ind Inc Electromagnetic valve assembly
US5984210A (en) * 1997-11-04 1999-11-16 Caterpillar Inc. Fuel injector utilizing a solenoid having complementarily-shaped dual armatures
DE19946602A1 (de) * 1999-09-29 2001-04-12 Bosch Gmbh Robert Brennstoffeinspritzventil
JP2002357173A (ja) 2001-03-28 2002-12-13 Denso Corp 燃料噴射弁の製造方法および燃料噴射弁
DE10133166A1 (de) 2001-07-07 2003-01-16 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
DE10205970A1 (de) 2002-02-14 2003-09-04 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
JP5488120B2 (ja) 2010-03-30 2014-05-14 株式会社デンソー 燃料噴射弁
US8453951B2 (en) * 2010-09-22 2013-06-04 Delphi Technologies, Inc. Fuel injector
DE102011090006B4 (de) * 2011-12-28 2015-03-26 Continental Automotive Gmbh Ventil
EP3009655B1 (fr) 2014-10-13 2017-08-23 Continental Automotive GmbH Soupape d'injection de carburant pour moteurs à combustion interne
DE102017207273A1 (de) * 2016-06-30 2018-01-04 Robert Bosch Gmbh Ventil zum Zumessen eines Fluids

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001025614A1 (fr) * 1999-10-07 2001-04-12 Robert Bosch Gmbh Soupape d'injection de carburant
JP2010180758A (ja) * 2009-02-04 2010-08-19 Denso Corp 燃料噴射弁
EP2789844A1 (fr) * 2011-12-09 2014-10-15 Kefico Corporation Injecteur de carburant à injection directe
WO2015049195A1 (fr) * 2013-10-02 2015-04-09 Continental Automotive Gmbh Ensemble soupape d'une soupape d'injection
DE102013222613A1 (de) 2013-11-07 2015-05-07 Robert Bosch Gmbh Ventil zum Zumessen von Fluid

Also Published As

Publication number Publication date
US11359589B2 (en) 2022-06-14
CN110100089B (zh) 2021-12-21
KR102394017B1 (ko) 2022-05-06
EP3559437A1 (fr) 2019-10-30
US20190309712A1 (en) 2019-10-10
JP6845937B2 (ja) 2021-03-24
EP3822475B1 (fr) 2023-05-17
CN110100089A (zh) 2019-08-06
CN110100089B9 (zh) 2022-01-11
KR20190097052A (ko) 2019-08-20
DE102016225776A1 (de) 2018-06-21
EP3559437B1 (fr) 2021-01-27
WO2018114088A1 (fr) 2018-06-28
JP2020502423A (ja) 2020-01-23

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