EP2462335B1 - Dispositif pour injection sous haute pression - Google Patents

Dispositif pour injection sous haute pression Download PDF

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Publication number
EP2462335B1
EP2462335B1 EP10728156A EP10728156A EP2462335B1 EP 2462335 B1 EP2462335 B1 EP 2462335B1 EP 10728156 A EP10728156 A EP 10728156A EP 10728156 A EP10728156 A EP 10728156A EP 2462335 B1 EP2462335 B1 EP 2462335B1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
valve needle
fuel injection
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.)
Not-in-force
Application number
EP10728156A
Other languages
German (de)
English (en)
Other versions
EP2462335A1 (fr
Inventor
Sebastian Jansen
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 EP2462335A1 publication Critical patent/EP2462335A1/fr
Application granted granted Critical
Publication of EP2462335B1 publication Critical patent/EP2462335B1/fr
Not-in-force 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
    • 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
    • F02M61/08—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 the valves opening in direction of fuel flow
    • 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
    • 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
    • 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
    • F02M51/066—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 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

Definitions

  • the present invention relates to a device for high-pressure fuel injection, which can be used in particular in internal combustion engines with direct injection in the stratified charge mode.
  • an injection valve with outwardly opening valve needle is disclosed, which is actuated by a solenoid actuator and having a guide element on the valve needle, which is guided in a valve housing, wherein the diameters of the guide element and a valve seat of the valve needle are selected so that the valve needle is essentially pressure balanced.
  • the high-pressure injection valves of the prior art are only insufficiently suitable to a simple and inexpensive to produce device for To provide high pressure injection for internal combustion engines with direct injection in stratified charge mode, which provides a high sealing force between the valve seat and valve needle in the closed state, and can be operated by a solenoid actuator with low actuation force or low power consumption and has a comparable switching dynamics as an injection valve with piezo actuator.
  • valve assembly according to the invention with the features of claim 1 has the advantage that it has a simple and thus more cost-effective design with a solenoid actuator that opens an outwardly opening valve needle due to effective on the valve needle pressure equalization with a significantly reduced operating force. Therefore, in the valve assembly according to the invention solenoid actuators with low power consumption, especially at injection pressures of 20 MPa or higher, can be used, which allow sufficient switching dynamics and reliable sealing of the valve needle valve seat of the valve in the closed state. This is inventively achieved in that when activating an electromagnetic actuator arranged between the high pressure region and low pressure region of the valve assembly control valve is opened in front of an outwardly opening valve needle.
  • a pressure equalization d. H. a pressure increase in the low pressure region, which causes a hydraulic force on an active surface of a valve element of the control valve in the opening direction of the valve needle and thereby significantly reduces an opening force of the electromagnetic actuator for the valve needle.
  • the control valve is opened by means of a freely movable magnet armature or a component connected to the magnet armature.
  • the device according to the invention for high-pressure fuel injection further comprises a driver attached to the valve needle with an armature contact region, wherein the driver is arranged in the starting position at a predetermined distance from the armature and the armature is movably disposed on the valve needle.
  • a closing spring for closing the valve needle also restores the armature. This ensures that upon activation of the electromagnetic actuator whose armature first moves from the starting position to the armature contact region of the driver and thereby opens the control valve for pressure equalization, without operating the valve needle. Only when the magnet armature is applied to the driver, the valve needle is actuated directly via the armature and opened.
  • a ring-cylindrical component is attached to the armature, wherein the valve seat of the control valve is arranged on a free end face of the annular-cylindrical component.
  • a gap seal is formed between the annular cylindrical component and the valve housing.
  • a diameter of the gap seal is formed larger than a diameter of the valve seat of the valve needle.
  • the distance from the starting position of the magnet armature to the driver attached to the valve needle is smaller than a total stroke of the magnet armature, ie, there is a residual stroke for opening the valve needle.
  • a first partial stroke the magnet armature from the starting position to the driver is a rapid opening of the control valve for pressure equalization and thus a rapid pressure equalization for the easier opening of the valve needle achieved, which is then opened with a second partial stroke.
  • a first partial stroke of the armature is first carried out by the driver to the closed position of the control valve and the control valve thus closed.
  • the valve element of the control valve acts as another actuated by the armature driver for the return of the valve needle.
  • the closing of the valve needle can be done faster by a hydraulic force in the closing direction of the valve needle supporting hydraulic force. This makes it possible to use magnetic actuators with low power consumption and to realize the switching dynamics required for gasoline injection during stratified operation of internal combustion engines.
  • the device for high-pressure fuel injection between the pressure chamber and the low-pressure region further comprises a throttle.
  • a leakage check valve can be inserted between the pressure chamber and the low-pressure region.
  • a leakage or return amount of fuel to a fuel return when opening the valve needle is significantly reduced.
  • the device according to the invention can be used very economically.
  • the leakage check valve has as closure member a collar-like extension formed on the valve needle and a seat which is formed on the valve housing.
  • FIGS. 1 to 6 a device 1 for high-pressure fuel injection according to a first preferred embodiment of the invention described in detail.
  • FIG. 1 shows a schematically simplified sectional view of the device according to the invention in the closed state.
  • the device 1 comprises a valve housing 2, an outwardly opening valve needle 3, which is arranged in the valve housing 2 in a pressure chamber 4 filled with fuel.
  • This pressure chamber 4 a fuel K is supplied via a fuel inlet 24 under pressure, wherein the valve needle 3 seals on a valve seat 16 on the valve housing 2.
  • the device 1 has a closing spring 5, which returns the valve needle 3 to a starting position, and an electromagnetic actuator 6 with a magnetic coil 63, an inner pole 62, a magnet housing 61 and a movably arranged magnet armature 7, the valve needle 3 via a thereto trained or attached driver 9 is actuated.
  • a control valve 8 having a valve element 10 and a valve seat 11 is arranged on an end region 29 of the valve needle 3 opposite the injection side.
  • the valve element 10 has a first active surface 13, which faces the pressure chamber 4, and a second active surface 14, which faces a pressure chamber 12, which communicates with a low-pressure region 19.
  • the valve element 10 of the control valve 8 is designed to release and close a connection between the pressure chamber 4 and the pressure chamber 12, the valve seat 11 of the control valve 8 being arranged on an end face of a ring-cylindrical component 17 fastened to the magnet armature 7. Between the outer circumference of the annular cylindrical member 17 and the valve housing 2, a gap seal 18 is formed with a small guide clearance.
  • FIG. 1 17 flow through openings 30, 31, for the supply of the fuel K are formed in the armature 7 and the annular cylindrical member. Accordingly, when the valve needle 3 is closed and the control valve 8 is closed, the high pressure of the fuel inlet 24 is present supplied fuel in all connected to the pressure chamber 4 interior spaces of the device. In the pressure chamber 12, there is low pressure, since it is connected via a throttle 21 to the fuel return 25 and the control valve 8 is closed.
  • a diameter ds of the valve seat 16 is selected to be smaller than a diameter d1 of the valve element 10, the valve needle 3 is additionally pressed, in addition to the force of the closing spring 5, into the valve seat 16 by a hydraulic force component resulting from this difference in diameter , As a result, a reliable sealing of the device 1 is ensured when the valve needle 3 is closed.
  • FIG. 2 shows an enlarged schematic sectional view showing a part of the device 1 of FIG. 1 illustrated in more detail.
  • a closed control valve 8 and inactivated electromagnetic actuator 6 whose armature 7 in its initial position.
  • the closing spring 5 acts on the armature 7 and is supported on the housing 2 from.
  • the axially freely movable armature 7 due to the spring force of the closing spring 5 a distance A to the driver 9 on the valve needle 3, and a distance H to the inner pole 62.
  • FIG. 3 shows a schematically simplified sectional view of the device 1 of FIG. 1 When opening the valve needle 3.
  • the magnetic coil 63 of the electromagnetic actuator 6 is energized (which is illustrated by a lightning-shaped symbol)
  • the armature 7 performs a first partial stroke in the direction of the inner pole 62, which corresponds to the degree of the distance A, until he the driver 9 touched.
  • the control valve 8 opens so that fuel K flows from the fuel inlet 24 into the pressure chamber 4 and via the flow opening 31 into the pressure chamber 12 (as indicated by an arrow B in FIG FIG. 3 is clarified).
  • the pressure in the pressure chamber 12 rises directly and causes a force on the valve needle 3, which results from the ratio of the hydraulically effective first and second active surfaces 13 and 14 on the valve element 10, which are each subjected to high pressure.
  • This resulting hydraulic force acts in the open control valve 8 in addition to Magnetic force of the armature 7 in the opening direction of the valve needle 3 and reduces the contact pressure of the valve needle 3 on the valve seat 16.
  • the valve needle 3 can now be taken or moved with little force from the armature 3 via the driver 9 in the opening direction, so that the valve needle 3 opens and the injection process can begin.
  • FIG. 4 shows a schematically simplified sectional view of the device of FIG. 1 with open valve needle. Due to the continued energization of the solenoid 63, the magnet armature 7 was pulled together with the valve needle 3 in the opening direction of the device 1 and has a second partial stroke to stop at the inner pole 62 executed, and thereby raised the valve needle 3 from the valve seat 16 to the outside and opened.
  • the second partial stroke for opening the valve needle 3 is here designed to be larger than the first partial stroke A for opening the control valve 8.
  • the effluent between the valve needle 3 and the valve housing 2 fuel spray is indicated by small arrows C in the FIG. 4 illustrated.
  • FIG. 5 shows an enlarged schematic sectional view showing a part of the device 1 of FIG. 4 illustrated in more detail.
  • open control valve 8 a portion of the fuel in the pressure chamber 12 via the throttle 21 (as illustrated by an arrow D) in the fuel return 25 as a leakage amount back.
  • This leakage amount through the throttle 21 is defined or limited to a predetermined value, so that the pressure drop in the pressure chamber 12 after switching off the electromagnetic actuator 6 (closing the valve needle 3) does not take too long and extends the dead times of the switching cycles and thus the switching dynamics deteriorated.
  • FIG. 6 is a schematically simplified sectional view of the device of FIG. 1 illustrated when closing the valve needle 3.
  • the state of the device 1 is shown, which adjusts after switching off the solenoid 63 of the electromagnetic actuator 6, wherein first the control valve 8 is closed. Thereafter, the pressure in the pressure chamber 12 drops due to the connection to the fuel return 25 via the throttle 21 again, so that the second effective surface 14 is acted upon only with the low pressure from the fuel return 25.
  • the first active surface 13 is still with the high pressure in the interior of the annular cylindrical member 17 acted upon.
  • a hydraulic closing force is generated which presses the valve needle 3 in addition to the spring force of the closing spring 5 in the valve seat 16 until the closed state of the valve needle 3 (see. FIG. 1 ) is restored and the injection process is completed.
  • the closing spring 5 acts on the magnet armature 7, the annular cylindrical component 17 and the valve element 10 on the valve needle 3.
  • FIGS. 7 to 10 a device 1 for high-pressure fuel injection according to a second preferred embodiment of the invention described in detail. Identical or functionally identical parts are denoted by the same reference numerals as in the first embodiment.
  • FIG. 7 shows a schematically simplified sectional view of a second embodiment of the inventive device 1 for high-pressure fuel injection with the valve needle closed 3.
  • the second embodiment of the device 1 according to the invention differs from the first embodiment described above in that in this case between the pressure chamber 12 and the low pressure region 19 of the fuel return 25, a leakage check valve 26 is arranged.
  • the leakage check valve 26 is a leakage amount to the fuel return 25, as occurs in the first embodiment in the throttle 21, drastically reduced.
  • the leakage check valve 26 has a collar-like extension 22 of the diameter at the end region 29 of the valve needle 3.
  • the leakage check valve 26 closes the pressure chamber 12 from the fuel return 25 in the closed state.
  • FIG. 7 shows how out, when the valve needle 3 is closed, the control valve 8 is closed and the leakage check valve 26 is opened so that a low pressure prevails in the pressure chamber 12.
  • FIG. 9 shows an enlarged schematic sectional view of a part of the device of FIG. 7 , which illustrates the pressure conditions when the valve needle 3 is closed. How out FIG. 9 can be seen, an annular groove 27 is formed in the valve housing 2 in a region between the annular cylindrical member 17 and the valve element 10 of the control valve 8 to an unimpeded fuel flow into the pressure chamber 12 with open control valve 8 (see FIG. 10 ).
  • the valve needle 3 is closed, the control valve 8 is closed and the leakage check valve 26 is opened.
  • FIG. 8 is a schematically simplified sectional view of the second embodiment of FIG. 7 when the valve needle 3 is open, in this state, the leakage check valve 26 is closed and the control valve 8 is opened.
  • high pressure prevails in the pressure chamber 12, so that the valve needle 3 can be opened with small forces. Since the leakage check valve 26 is closed, no amount of leakage into the fuel return 25 occurs.
  • the collar-like extension 22 of the leakage check valve 26 that adjoins the stop 23 at the same time defines a stroke stop of the opened valve needle 3.
  • FIG. 10 shows an enlarged schematic sectional view of a part of the device of FIG. 8 , which illustrates the pressure conditions when the valve needle 3 is open. How out FIG. 10 can be seen, in this case the control valve 8 is opened and the leakage check valve 26 is closed.
  • the high-pressure region 28 is in this case both in the control valve 8 and in the leakage check valve 26 formed while only in the fuel return 25 of the low pressure region 19 is formed.
  • the actuation of the valve needle 3 can be done directly by a low-cost electromagnetic actuator, even at high injection pressures of 20 MPa, with a sufficiently high switching dynamics , Because of the correspondingly low power requirement of the electromagnetic actuator, the control of the device 1 can therefore be compared with conventional, d. H. available power amplifiers for solenoid high-pressure injection valves. This contributes to a further cost reduction and thus to increased cost-effectiveness of the inventive device 1 for high-pressure fuel injection.

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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)

Claims (9)

  1. Dispositif pour injection sous haute pression de carburant, comprenant
    - un boîtier de soupape (2),
    - une aiguille de soupape (3) s'ouvrant vers l'extérieur, laquelle est disposée dans le boîtier de soupape (2) dans un espace de pression (4) rempli de carburant, auquel espace de pression est acheminé du carburant (K) sous pression, l'aiguille de soupape (3) réalisant l'étanchéité contre un siège de soupape (16),
    - un ressort de fermeture (5) qui ramène l'aiguille de soupape (3) à une position initiale,
    - un actionneur électromagnétique (6) comprenant une armature magnétique (7) disposée de manière mobile pour l'actionnement de l'aiguille de soupape (3),
    caractérisé en ce
    qu'une soupape de commande (8) est pourvue d'un élément de soupape (10) et d'un siège de soupape (11), l'élément de soupape (10) comprenant une première surface active (13) et une deuxième surface active (14), la première surface active (13) étant tournée vers l'espace de pression (4), la deuxième surface active (14) étant tournée vers une chambre de pression (12) qui est en liaison avec une zone de basse pression (19) et l'élément de soupape (10) libère et ferme une liaison entre l'espace de pression (4) et la chambre de pression (12) et le siège de soupape (11) est disposé sur l'armature magnétique (7) ou sur un composant relié à l'armature magnétique (7),
    la soupape de commande (8) s'ouvrant avant l'aiguille de soupape (3) s'ouvrant vers l'extérieur lors d'une activation de l'actionneur électromagnétique (6), afin de réduire une force d'ouverture pour l'aiguille de soupape (3) par libération de la liaison entre l'espace de pression (4) et la chambre de pression (12).
  2. Dispositif pour injection sous haute pression de carburant selon la revendication 1, comportant en outre un élément d'entraînement (9) fixé à l'aiguille de soupape (3) et comprenant une zone de contact d'armature (20), l'élément d'entraînement (9) étant disposé à une distance (A) de l'armature magnétique (7) dans la position initiale et l'armature magnétique (7) étant disposée de manière mobile sur l'aiguille de soupape (3).
  3. Dispositif pour injection sous haute pression de carburant selon la revendication 1 ou 2, caractérisé en ce qu'un composant cylindrique annulaire (17) est fixé à l'armature magnétique (7), le siège de soupape (11) de la soupape de commande (8) étant disposé sur un côté frontal libre du composant cylindrique annulaire (17).
  4. Dispositif pour injection sous haute pression de carburant selon la revendication 3, caractérisé en ce qu'un joint d'étanchéité à fente (18) est réalisé entre la périphérie extérieure du composant cylindrique annulaire (17) et le boîtier de soupape (2).
  5. Dispositif pour injection sous haute pression de carburant selon la revendication 4, caractérisé en ce qu'un diamètre (d1) du joint d'étanchéité à fente (18) est supérieur à un diamètre (ds) du siège de soupape (16).
  6. Dispositif pour injection sous haute pression de carburant selon l'une quelconque des revendications 2 à 5, caractérisé en ce que la distance (A) entre l'élément d'entraînement (9) et l'armature magnétique (7) dans la position initiale est inférieure à une différence entre une course totale (H) de l'armature magnétique (7) et la distance (A).
  7. Dispositif pour injection sous haute pression de carburant selon l'une quelconque des revendications précédentes, caractérisé en ce qu'un étranglement (21) est disposé entre la chambre de pression (12) et la zone de basse pression (19).
  8. Dispositif pour injection sous haute pression de carburant selon l'une quelconque des revendications 1 à 6, caractérisé en ce qu'une soupape d'arrêt de fuite (26) est disposée entre la chambre de pression (12) et la zone de basse pression (19).
  9. Dispositif pour injection sous haute pression de carburant selon la revendication 8, caractérisé en ce que la soupape d'arrêt de fuite (26) comporte, en tant qu'organe de fermeture, un élargissement de type rebord (22) formé sur l'aiguille de soupape (3) et un siège (23) de la soupape d'arrêt de fuite (26) est formé sur le boîtier de soupape (2).
EP10728156A 2009-08-05 2010-06-17 Dispositif pour injection sous haute pression Not-in-force EP2462335B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200910028234 DE102009028234A1 (de) 2009-08-05 2009-08-05 Vorrichtung zur Kraftstoffhochdruckeinspritzung
PCT/EP2010/058580 WO2011015405A1 (fr) 2009-08-05 2010-06-17 Dispositif pour l'injection à haute pression de carburant

Publications (2)

Publication Number Publication Date
EP2462335A1 EP2462335A1 (fr) 2012-06-13
EP2462335B1 true EP2462335B1 (fr) 2013-03-06

Family

ID=42371483

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10728156A Not-in-force EP2462335B1 (fr) 2009-08-05 2010-06-17 Dispositif pour injection sous haute pression

Country Status (4)

Country Link
EP (1) EP2462335B1 (fr)
KR (1) KR101762106B1 (fr)
DE (1) DE102009028234A1 (fr)
WO (1) WO2011015405A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101776313B1 (ko) 2011-06-30 2017-09-07 현대자동차주식회사 저압분사 인젝터
KR101765938B1 (ko) 2011-06-30 2017-08-07 현대자동차주식회사 저압분사 인젝터
US8616474B2 (en) * 2011-09-09 2013-12-31 Continental Automotive Systems, Inc. High flow outward opening gaseous injector for automotive applications
DE102013206385A1 (de) * 2013-04-11 2014-10-16 Robert Bosch Gmbh Ventil zum Zumessen von Fluid
US9625264B1 (en) 2016-01-20 2017-04-18 Denso Corporation Systems and methods for displaying route information

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AUPN391295A0 (en) 1995-06-30 1995-07-27 Orbital Engine Company (Australia) Proprietary Limited Fuel injection apparatus
ATE381670T1 (de) 2005-11-02 2008-01-15 Delphi Tech Inc Verfahren zur auslegung eines kraftstoffeinspritzventils
DE102007038430A1 (de) 2007-08-14 2009-02-19 Robert Bosch Gmbh Kraftstoffeinspritzventileinrichtung

Also Published As

Publication number Publication date
DE102009028234A1 (de) 2011-02-17
EP2462335A1 (fr) 2012-06-13
WO2011015405A1 (fr) 2011-02-10
KR101762106B1 (ko) 2017-07-27
KR20120040731A (ko) 2012-04-27

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