EP3636911A1 - Ensemble de soupape pour soupape d'injection et soupape d'injection de carburant - Google Patents

Ensemble de soupape pour soupape d'injection et soupape d'injection de carburant Download PDF

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Publication number
EP3636911A1
EP3636911A1 EP18199089.6A EP18199089A EP3636911A1 EP 3636911 A1 EP3636911 A1 EP 3636911A1 EP 18199089 A EP18199089 A EP 18199089A EP 3636911 A1 EP3636911 A1 EP 3636911A1
Authority
EP
European Patent Office
Prior art keywords
armature
valve
valve assembly
flow holes
fluid
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.)
Withdrawn
Application number
EP18199089.6A
Other languages
German (de)
English (en)
Inventor
Mauro Grandi
Stefano Filippi
Valerio Polidori
Luca Matteucci
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.)
Vitesco Technologies GmbH
Original Assignee
Continental Automotive 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 Continental Automotive GmbH filed Critical Continental Automotive GmbH
Priority to EP18199089.6A priority Critical patent/EP3636911A1/fr
Priority to CN201910949123.2A priority patent/CN111042968A/zh
Publication of EP3636911A1 publication Critical patent/EP3636911A1/fr
Withdrawn legal-status Critical Current

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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
    • 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
    • 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
    • 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
    • F02M51/0635—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a plate-shaped or undulated armature not entering the winding
    • F02M51/0642—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a plate-shaped or undulated armature not entering the winding the armature having a valve attached thereto
    • F02M51/0653—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a plate-shaped or undulated armature not entering the winding the armature having a valve attached thereto the valve being an elongated body, e.g. a needle valve
    • 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
    • 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

Definitions

  • the present invention relates to a valve assembly for a fluid injection valve and to a fluid injection valve, e.g. a fuel injection valve of a vehicle. It particularly relates to solenoid injection valves.
  • Injection valves of the "free lift"-design as well as those where the armature is fixed to the needle usually have a chrome plating on surfaces of the armature contacting the pole piece to improve wear resistance.
  • the chrome plating is costly and should be avoided for environmental reasons.
  • a valve assembly for an injection valve comprising a valve body with a central longitudinal axis comprising a cavity with a fluid inlet portion and a fluid outlet portion. Furthermore, the valve assembly comprises a valve needle axially movable in the cavity, the valve needle preventing a fluid flow through the fluid outlet portion in the closing position and releasing the fluid flow through the fluid outlet portion in further positions.
  • the valve assembly comprises an armature of an electromagnetic actuator unit being designed to actuate the valve needle.
  • the armature is arranged in the cavity and axially displaceable relative to the valve body in reciprocating fashion.
  • the armature is also axially displaceable relative to the armature in reciprocating fashion.
  • the armature may expediently be engageable in a form-fit connection with an armature retainer of the valve needle so that the armature is operable to take the valve needle with it, in particular when travelling axially towards a pole piece of the electromagnetic actuator unit, i.e. in direction towards the fluid inlet portion in case of an inward opening valve.
  • An inward opening valve is a valve which is designed such that the valve needle is movable away from the closing position in axial direction from the fluid outlet portion towards the fluid inlet portion for opening the valve.
  • the armature has a plurality of flow holes extending in an axial direction from an upper side of the armature facing towards the fluid inlet portion to a lower side facing towards the fluid outlet portion, the flow holes permitting fuel to pass through the armature.
  • Inlets of the flow holes on the upper side of the armature are at a distance R 1 from the central longitudinal axis L, wherein R 1 is larger than the radius r P of a central opening in an element of the valve assembly adjacent to the upper side of the armature. Furthermore, outlets of the flow holes on the lower side of the armature are arranged at a distance R 2 from the central longitudinal axis L, wherein R 2 is smaller than the radius r H of a disk-shaped element arranged in an axial region of the valve needle adjacent to the lower side of armature.
  • the inlets of the flow holes on the upper side of the armature have a radial overlap with the element of the valve assembly adjacent to the upper side of the armature.
  • This element is usually the pole piece of the valve assembly and would in a traditional design of the injector be in contact with the upper side of the armature in a fully open position of the valve.
  • the inlets of the flow holes are arranged in the region of the upper side of the armature that would in the traditional design be in contact with the elements of the valve assembly adjacent to the other side of the armature, for example the pole piece.
  • This has the effect, that due to the hydraulic force, which the fuel exerts on the upper side of the armature, there is a residual gap between the upper side of the armature and the elements of the valve assembly adjacent to the armature, for example the pole piece. This residual gap stays open because of the hydraulic force acting on the upper side of the armature.
  • the armature is suspended in the maximum opening position by an equilibrium of forces in a stable position.
  • a magnetic force acting in a direction away from the fluid outlet portion is balanced by the sum of the hydraulic force and a spring force exerted by the calibration spring, both acting in a direction towards the fluid outlet portion.
  • outlets of the flow holes on the lower side of the armature have a radial overlap with a disk-shaped element arranged adjacent to the lower side of the armature.
  • the disk-shaped element may be positionally fix relative to the valve body or relative to the valve needle.
  • This disk-shaped element may also be called a "hydro-disc” and may, in some embodiments, be fixed to the valve needle or may be formed in one piece with the valve needle.
  • the disk-shaped element and the armature retainer of the valve needle are positioned on opposite axial sides of the armature.
  • the armature retainer and the disk-shaped element may expediently limit the axial play of the armature relative to the valve needle in both axial directions, in particular the armature retainer in direction towards the fluid inlet portion and the disk-shaped element in direction towards the fluid outlet portion.
  • the radial overlap between the outlets and the disk-shaped element means that in a fully closed position of the valve the outlets are covered at least partially by the disk-shaped element. This has the effect, that fluid may be squeezed through the closing gap between the outlets and the disk-shaped element, thereby dissipating energy of the armature and dampening the armature movement.
  • the valve assembly has the advantage, that movement of the armature is dampened at the end of the opening phase as well as at the end of the closing phase of the valve. Because most of the energy of the armature is dissipated before the armature makes contact with the disk-shaped elements at the end of the closing phase, uncontrolled reopening of the needle should be prevented.
  • r H may be r H > R 2 + 0.7 d, in particular r H > R 2 + 0.9 d or even r H > R 2 + d. If r H is equal to the sum of R 2 and d, the outlets are fully covered by the disc-shaped element in a fully closed position.
  • a radial gap is arranged between an outer circumferential surface of the armature and an inner circumferential surface of the valve body, the radial gap establishing a fluid leakage path from the upper side of the armature to the lower side.
  • a "fluid leakage path” is understood in the present context to be a fluid path which is in particular dimensioned so that its contribution to the fluid flow is insignificant.
  • the valve assembly comprises at least one main fluid path in parallel to the above described fluid leakage path.
  • the hydraulic diameter of the main fluid path is preferably at least 10 times as large, for example at least 20 times as large as the hydraulic diameter of the fluid leakage path.
  • the radial gap establishing the fluid leakage path may be just as large as is required due to manufacturing tolerances of the armature and the valve body. Alternatively, the hydraulic diameter of the fuel leakage path might be slightly larger than is required by manufacturing tolerances.
  • a fuel injection valve comprising the above-described valve assembly.
  • the fuel injection valve has the advantages described above in connection with the valve assembly and is in particular suitable for being employed as a gasoline direct injection injector.
  • FIGS 1 and 2 show an injection valve 1 that is in particular suitable for dosing fuel to an internal combustion engine.
  • the injection valve 1 comprises in particular a valve assembly 3.
  • the valve assembly 3 comprises a valve body 4 with a central longitudinal axis L.
  • a housing 6 is partially arranged around the valve body 4.
  • the valve body 4 comprises a cavity 9.
  • the cavity 9 has a fluid outlet portion 7.
  • the fluid outlet portion 7 communicates with a fluid inlet portion 5 which is provided in the valve body 4.
  • the fluid inlet portion 5 and the fluid outlet portion 7 are in particular positioned at opposite axial ends of the valve body 4.
  • the cavity 9 takes in a valve needle 11.
  • the valve needle 11 comprises a needle shaft 15 and a sealing ball 13 welded to the tip of the needle shaft 15.
  • the sealing ball 13 sealingly rests on a seat plate 17 having at least one injection nozzle.
  • a preloaded calibration spring 18 exerts a force on the needle 11 towards a closing position.
  • the fluid outlet portion 7 is arranged near the seat plate 17. In the closing position of the valve, a fluid flow through the at least one injection nozzle is prevented.
  • the injection nozzle may be, for example, an injection hole. However, it may also be of some other type suitable for dosing fluid.
  • the valve assembly 3 is provided with an electro-magnetic actuator unit 19.
  • the electro-magnetic actuator unit 19 comprises a solenoid 21, which is preferably arranged inside the housing 6. Furthermore, the electro-magnetic actuator unit 19 comprises an armature 23.
  • the housing 6, parts of the valve body 4 and the armature 23 form an electromagnetic circuit.
  • the actuator unit 19 further comprises a pole piece 25.
  • the armature 23 is axially movable in the cavity 9 and fixed to the valve needle 11 by form fit.
  • the needle 11 is guided by a central axial opening 26 in the armature 23.
  • the armature 23 is axially movable relative to the needle 11, i.e. it may slide on the needle 11.
  • An armature retainer 25 is fixed to one end of the valve needle 11.
  • An armature spring 27 is arranged between the retainer 25 and an upper side 33 of the armature 23.
  • Adjacent to a lower side 35 of the armature 23, a hydro-disc 40 is fixed to the valve needle 11, an upper side 41 of the hydro-disc 40 being in contact with the lower side 35 of the armature 23 in a fully closed and in a fully open position of the valve 1.
  • the armature 23 comprises a number of flow holes 36, which provide a fluid path from the upper side 33 to the lower side 35.
  • the flow holes 36 may be vertical or inclined.
  • the flow holes 36 have a diameter d which is constant in the embodiment shown in figures 1 and 2 , but which might vary in other embodiments.
  • the flow holes 36 have an inlet 37 at the upper side 33 of the armature 23 and an outlet 39 at the lower side 35.
  • a distance R 1 between the inlet 37 and the central longitudinal axis L is larger than a radius r P of a central opening 28 of the pole piece 29.
  • a distance R 2 between the outlet 39 of the flow holes 36 and the central longitudinal axis L is smaller than a radius r H of the hydro-disc 40.
  • the radial gap 45 establishes a fluid leakage path from the upper side 33 of the armature 23 to the lower side 35. Only a very small amount of fuel is able to pass through the radial gap 45.
  • the main fluid path is through the flow holes 36 in the armature 23.
  • Figures 1 and 2 show the injection valve 1 in a fully closed position.
  • the solenoid 21 is energized and the armature 23 experiences a magnetic force and slides upwards towards the pole piece 29, moving in axial direction away from the fluid outlet portion 7, thereby compressing the calibration spring 18.
  • Fuel starts to flow along the upper side 33 of the armature 23 and through the flow holes 36 and on into the cavity 9 below the armature 23, which is possible because a gap has opened between the hydro-disc 40 and the armature 23.
  • the sealing ball 13 is lifted from the seat plate 17 and the at least one injection nozzle is unblocked.
  • the armature 23 stops moving upwards before contact with the pole piece 29 is made.
  • a residual gap 43 is formed between the upper side 33 of the armature 23 and the lower side 31 of the pole piece 29.
  • the residual gap 43 stays open because of the hydraulic force the fuel exerts on the upper side 33 of the armature 23. Consequently, there is no hard stop for the armature 23 in the maximum opening position.
  • the radius r H of the hydro-disc 40 is larger than the sum of R 2 and d. Therefore, the outlets 39 of the flow holes 36 are covered completely by the hydro-disc 40 when the hydro-disc 40 makes contact with the armature 23.
  • the radius r H of the hydro-disc 40 is smaller than the sum of R 2 and d, but still larger than R 2 .
  • the outlets 39 of the flow holes 36 are covered partially by the hydro-disc 40 when the hydro-disc 40 makes contact with the armature 23. According to these embodiments, the dampening effect is slightly reduced.
  • valve assembly 1 may be chosen by taking into account several factors, in particular fuel pressure, the force exerted by the calibration spring 18, the width of the radial gap 45 and the relation between r H and R 2 .
  • the calibration spring 18 When the solenoid 21 is de-energized, the calibration spring 18 is able to force the valve needle 11 to move in axial direction into its closing position. By dissipating energy of the armature 23 during the downward movement by way of the closing gap between the hydro-disc 40 and the armature 23, undesired re-opening of the needle 11 is prevented.
EP18199089.6A 2018-10-08 2018-10-08 Ensemble de soupape pour soupape d'injection et soupape d'injection de carburant Withdrawn EP3636911A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP18199089.6A EP3636911A1 (fr) 2018-10-08 2018-10-08 Ensemble de soupape pour soupape d'injection et soupape d'injection de carburant
CN201910949123.2A CN111042968A (zh) 2018-10-08 2019-10-08 用于喷射阀的阀组件和燃料喷射阀

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP18199089.6A EP3636911A1 (fr) 2018-10-08 2018-10-08 Ensemble de soupape pour soupape d'injection et soupape d'injection de carburant

Publications (1)

Publication Number Publication Date
EP3636911A1 true EP3636911A1 (fr) 2020-04-15

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ID=63794371

Family Applications (1)

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EP18199089.6A Withdrawn EP3636911A1 (fr) 2018-10-08 2018-10-08 Ensemble de soupape pour soupape d'injection et soupape d'injection de carburant

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EP (1) EP3636911A1 (fr)
CN (1) CN111042968A (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2851551A1 (fr) * 2013-09-20 2015-03-25 Continental Automotive GmbH Soupape d'injection de fluide
EP2985445A1 (fr) 2014-08-14 2016-02-17 Continental Automotive GmbH Soupape d'injection de fluide actionnée par solénoïde
EP3009663A1 (fr) * 2014-10-15 2016-04-20 Continental Automotive GmbH Ensemble de soupape et injecteur de fluide
DE102017207273A1 (de) * 2016-06-30 2018-01-04 Robert Bosch Gmbh Ventil zum Zumessen eines Fluids

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8215573B2 (en) * 2010-05-14 2012-07-10 Continental Automotive Systems Us, Inc. Automotive gasoline solenoid double pole direct injector
WO2013167597A1 (fr) * 2012-05-08 2013-11-14 Continental Automotive Gmbh Boîtier de soupapes destiné à une soupape d'injection et soupape d'injection

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2851551A1 (fr) * 2013-09-20 2015-03-25 Continental Automotive GmbH Soupape d'injection de fluide
EP2985445A1 (fr) 2014-08-14 2016-02-17 Continental Automotive GmbH Soupape d'injection de fluide actionnée par solénoïde
EP3009663A1 (fr) * 2014-10-15 2016-04-20 Continental Automotive GmbH Ensemble de soupape et injecteur de fluide
DE102017207273A1 (de) * 2016-06-30 2018-01-04 Robert Bosch Gmbh Ventil zum Zumessen eines Fluids

Also Published As

Publication number Publication date
CN111042968A (zh) 2020-04-21

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