EP1259729A2 - Electrovanne destinee a la commande d'une soupape d'injection d'un moteur a combustion interne - Google Patents

Electrovanne destinee a la commande d'une soupape d'injection d'un moteur a combustion interne

Info

Publication number
EP1259729A2
EP1259729A2 EP01994586A EP01994586A EP1259729A2 EP 1259729 A2 EP1259729 A2 EP 1259729A2 EP 01994586 A EP01994586 A EP 01994586A EP 01994586 A EP01994586 A EP 01994586A EP 1259729 A2 EP1259729 A2 EP 1259729A2
Authority
EP
European Patent Office
Prior art keywords
armature
solenoid valve
anchor bolt
valve
plate
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
EP01994586A
Other languages
German (de)
English (en)
Other versions
EP1259729B1 (fr
Inventor
Rainer Haeberer
Hermann Koch-Grober
Holger Rapp
Christoffer Uhr
Andreas Rettich
Wolfgang Fleiner
Markus Rueckle
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
Priority claimed from DE10113008A external-priority patent/DE10113008A1/de
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1259729A2 publication Critical patent/EP1259729A2/fr
Application granted granted Critical
Publication of EP1259729B1 publication Critical patent/EP1259729B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • 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
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
    • F02M63/0036—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat with spherical or partly spherical shaped valve member ends
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
    • F02M2200/304—Fuel-injection apparatus having mechanical parts, the movement of which is damped using hydraulic means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M2200/306—Fuel-injection apparatus having mechanical parts, the movement of which is damped using mechanical 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
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/003—Valve inserts containing control chamber and valve piston

Definitions

  • Solenoid valve for controlling an injection valve of an internal combustion engine
  • the invention relates to a solenoid valve for controlling an injection valve of an internal combustion engine according to the preamble of claim 1.
  • Such a solenoid valve is used to control the fuel pressure in the control pressure chamber of an injection valve, for example an injector of a common rail injection system.
  • the movement of a valve piston, with which an injection opening of the injection valve is opened or closed, is controlled via the fuel pressure in the control pressure chamber.
  • the known solenoid valve has an electromagnet arranged in a housing part, a movable armature and a control valve member which is moved with the armature and acted upon by a closing spring in the closing direction and which cooperates with a valve seat of the solenoid valve and thus controls the fuel outflow from the control pressure chamber.
  • solenoid valves The disadvantage of solenoid valves is the so-called anchor bounce.
  • the armature, and with it the control valve member is accelerated from the closing spring of the solenoid valve to the valve seat in order to close a fuel outlet channel from the control pressure chamber.
  • the impact of the control valve member on the valve seat can result in disadvantageous swinging and / or bouncing of the control valve member on the valve seat, as a result of which the control of the injection process is impaired.
  • the armature is therefore made in two parts with an armature bolt and an armature plate slidably mounted on the armature bolt, so that the armature plate moves further against the tension force of a return spring when the control valve member impacts the valve seat.
  • the return spring then conveys the anchor plate back to its starting position at a stop of the anchor bolt.
  • the two-part design of the armature reduces the effectively braked mass and thus the kinetic energy causing the bouncing of the armature hitting the valve seat, but the armature plate can disadvantageously oscillate on the armature bolt after the solenoid valve has closed.
  • DE 197 08 104 AI proposes using an overstroke stop which limits the path length by which the anchor plate can move on the anchor bolt.
  • the overstroke stop is arranged in a fixed manner in the housing of the solenoid valve between the anchor plate and a slide piece guiding the anchor bolt.
  • the overstroke stop By means of the overstroke stop, the reverberation time of the anchor plate is shortened, but the required overstroke distance of the anchor plate must be during the installation of the Solenoid valve can be set in the housing of the solenoid valve. This requires a complex change in the manufacturing process, since the manufacturing facilities have to be retrofitted accordingly.
  • the solenoid valve according to the invention with the characterizing features of claim 1 avoids the disadvantages occurring in the prior art.
  • the armature with the armature plate, armature bolt, return spring and overstroke stop can advantageously be preassembled outside the assembly line of the injection valve and the required displacement path of the armature plate on the armature bolt can be set outside the housing of the injection valve.
  • the pre-assembled armature assembly can then be installed in the housing of the solenoid valve. A complex conversion of the assembly line is not necessary.
  • the return spring which presses the anchor plate with a first end in its rest position against a first stop on the anchor bolt, is not fixedly supported with the second end in the solenoid valve housing, but rather on one fixed to the anchor bolt and moved with the anchor bolt Supporting part is also advantageously achieved that the return spring does not counteract the closing spring of the solenoid valve acting on the anchor bolt.
  • the spring tension of the closing spring of the solenoid valve can therefore be designed to be lower. Since the return spring no longer counteracts the closing spring, the return spring no longer has any influence on the dynamic behavior of the anchor bolt.
  • the anchor bolt is slidably mounted in an opening of a slider which is fixed in the housing of the solenoid valve and for the side of the slider facing the anchor plate to be provided with a recess in which the support part fixed to the anchor bolt is arranged, wherein the outer contour of the support part is spaced from the inner contour of the recess by a gap.
  • FIG. 1 shows a cross section through the upper part of a fuel injection valve known from the prior art with a solenoid valve
  • FIG. 2 shows a partial area of the solenoid valve known from the prior art with an over-stroke adjusting disk
  • FIG. 3 shows a cross section through the armature assembly with slide piece according to a first embodiment of the invention
  • FIG. 4 shows a cross section through the armature assembly with slide piece according to a second embodiment of the invention.
  • Fig. 5 shows a cross section through the armature assembly with slider according to a third embodiment of the invention.
  • Fig. 1 shows the upper part of a fuel injection valve 1 known from the prior art, which is for use is determined in a fuel injection system which is equipped with a high-pressure fuel reservoir which is continuously supplied with high-pressure fuel by a high-pressure feed pump.
  • the fuel injector 1 shown has a valve housing 4 with a longitudinal bore 5, in which a valve piston 6 is arranged, which acts with its one end on a valve needle arranged in a nozzle body, not shown.
  • the valve needle is arranged in a pressure chamber which is supplied with fuel under high pressure via a pressure bore 8.
  • the valve needle is raised against the closing force of a spring by the high force of fuel which acts constantly on a pressure shoulder of the valve needle in the pressure chamber.
  • the fuel is then injected into the combustion chamber of the internal combustion engine through an injection opening which is then connected to the pressure chamber.
  • the valve needle is pressed into the valve seat of the injection valve in the closing direction and the injection process is ended.
  • valve piston 6 is guided at its end facing away from the valve needle in a cylinder bore 11 which is introduced into a valve piece 12 which is inserted into the valve housing 4.
  • a valve piece 12 which is inserted into the valve housing 4.
  • the end face 13 of the valve piston 6 is guided at its end facing away from the valve needle in a cylinder bore 11 which is introduced into a valve piece 12 which is inserted into the valve housing 4.
  • Valve piston 6 a control pressure chamber 14, which is connected via an inlet channel to a high-pressure fuel connection.
  • the inlet channel is essentially made up of three parts.
  • a bore leading radially through the wall of the valve piece 12, the inner walls of which form an inlet throttle 15 over part of its length, is constantly connected to an annular space 16 surrounding the valve piece on the circumference, which annular space in turn is in constant connection via a fuel filter inserted into the inlet channel with the high-pressure fuel connection of a connection piece 9 which can be screwed into the valve housing 4.
  • the annular space 16 is sealed to the longitudinal bore 5 via a sealing ring 39.
  • the control pressure chamber 14 is exposed to the high fuel pressure prevailing in the high-pressure fuel reservoir via the inlet throttle 15.
  • a bore running in the valve piece 12 which forms a fuel outlet channel 17 provided with an outlet throttle 18, which opens into a relief chamber 19, which is connected to a low-pressure fuel connection 10, which in turn is not further illustrated manner is connected to a fuel return of the injection valve 1.
  • the fuel drain channel 17 emerges from the valve piece 12 in the region of a conically countersunk part 21 of the outer end face of the valve piece 12.
  • the valve piece 12 is firmly clamped to the valve housing 4 in a flange area 22 via a screw member 23.
  • a valve seat 24 is formed in the conical part 21, with which a control valve member 25 of a solenoid valve 30 controlling the injection valve interacts.
  • the control valve member 25 is coupled to a two-part armature in the form of an armature bolt 27 and an armature plate 28, which armature interacts with an electromagnet 29 of the solenoid valve 30.
  • the solenoid valve 30 further comprises a housing part 60 which accommodates the electromagnet and which is firmly connected to the valve housing 4 via screwable connecting means 7.
  • the anchor plate 28 is dynamically slidably supported on the anchor bolt 27 under the action of its inertial mass against the biasing force of a return spring 35 and is pressed by this return spring in the idle state against a sickle disk 26 fixed on the anchor bolt.
  • the return spring 35 is supported in a housing-fixed manner on a flange 32 of a sliding piece 34 guiding the anchor bolt 27, which with this flange lies between a spacer disk 38 placed on the valve piece 12 and the screw member 23 in the valve housing is firmly clamped.
  • the armature bolt 27 and with it the armature disk 28 and the control valve member 25 coupled to the armature bolt are constantly acted upon in the closing direction by a closing spring 31 which is fixed to the housing, so that the control valve member 25 normally bears against the valve seat 24 in the closed position.
  • a closing spring 31 which is fixed to the housing, so that the control valve member 25 normally bears against the valve seat 24 in the closed position.
  • the armature plate 28 is attracted by the electromagnet and the drain channel 17 is opened toward the relief chamber 19.
  • annular shoulder 33 on the armature bolt 27 which strikes the flange 32 when the electromagnet is excited and thus limits the opening stroke of the control valve member 25.
  • the spacer 38 arranged between the flange 32 and the valve piece 12 serves to adjust the opening stroke.
  • the opening stroke of the control valve member 25 is adjusted by a stop element arranged between the armature plate 28 and the electromagnet 29.
  • the opening and closing of the injection valve is controlled by the solenoid valve 30 as described below.
  • the anchor bolt 27 is constantly acted upon by the closing spring 31 in the closing direction, so that the control valve member 25 rests on the valve seat 24 in the closed position when the electromagnet is not energized, and the control pressure chamber 14 is closed to the relief side 19, so that the high one there via the inlet channel very quickly Builds up pressure that is also present in the high-pressure fuel reservoir.
  • the pressure in the control pressure chamber 14 generates a closing force on the valve piston 6 and thus in FIG.
  • Control pressure chamber 14 very quickly, since this via the throttle 15 is decoupled from the high pressure side. As a result, the force acting on the valve needle in the opening direction outweighs the high fuel pressure applied to the valve needle, so that the valve needle moves upwards and at the same time the at least one injection opening toward it
  • the control valve member reverts as a result of the impact of the anchor bolt on the valve seat causing an elastic deformation thereof, which acts as an energy store, part of the energy being transferred to the control valve member, which then bounces off the valve seat 24 together with the anchor bolt.
  • the known solenoid valve shown in FIG. 1 therefore uses a two-part armature with an armature plate 28 decoupled from the armature pin 27. In this way, the mass impinging on the valve seat as a whole can be reduced, but the armature plate 28 can oscillate in a disadvantageous manner. For this reason, an overstroke adjusting disk 70 arranged between the armature plate 28 and the sliding sleeve 34 is provided in the known solenoid valve, as shown in FIG. 2.
  • the overtravel 70 limits the displacement of the anchor plate 28 on the anchor bolt 27 to the dimension d.
  • the swinging of the anchor plate 28 is reduced by the overtravel 70 and the anchor plate 28 returns to its initial position at the stop 26 faster.
  • the spacer 38, the slider 34 and the overtravel 70 are fixed in place in the solenoid valve housing. stressed.
  • the overtravel distance d in the solenoid valves known in the prior art must therefore be set during the assembly in the solenoid valve housing via the thickness of the related overtravel adjusting disc. In some embodiments, however, the thickness of the overtravel adjusting disc also influences the distance of the armature plate 28 from the electromagnet 29. This is the case when, for example, the end face of the solenoid valve housing 60 is clamped against the flange 32.
  • Fig. 3 shows a first embodiment of the solenoid valve according to the invention. Only the slider 34 and the anchor with anchor bolt 27, anchor plate 28 and return spring 35 are shown. The same parts are provided with the same reference numerals.
  • the armature assembly shown can be used, for example, in the solenoid valve housing 60 shown in FIG. 1.
  • An important difference from the known arrangement shown in FIG. 2 is that a support part 50 is provided in place of the overtravel adjusting disk which is arranged in a fixed manner in the solenoid valve housing and is firmly connected to the anchor bolt 27.
  • a disk fixed to the anchor bolt 27 can be provided as the supporting part.
  • the washer is pushed onto the anchor bolt 27 and then firmly connected to the anchor bolt by, for example, welding or gluing. Other types of fastening such as shrinking on are also possible.
  • the support part 50 is welded to the anchor bolt 27 on the side 59 facing away from the anchor plate.
  • the weld seam 51 on the underside 59 of the support part 50 can be seen in FIG. 1.
  • the return spring 35 is supported with one end 61 on the anchor plate 28 and with its other end 62 on the side 57 of the support part 50 which faces the anchor plate 28.
  • the anchor plate 28 When manufacturing the anchor assembly, the anchor plate 28 is first pushed onto the anchor bolt 27 until the anchor plate strikes a head 55 of the anchor bolt.
  • the head 55 replaces the sickle disk 26 in FIGS. 1 and 2 and, like this, serves as a stop for the anchor plate.
  • the return spring 35 is then pushed over the guide stub 65 of the anchor plate 28 until its end 61 abuts the anchor plate.
  • the disk-shaped support part 50 is pushed so far onto the anchor bolt 27 that the required overtravel distance d remains between the mutually facing sides 57 and 58 of the support part 50 and the guide stub 65. Finally, the support part 50 is fixed in this position on the anchor bolt 27.
  • the anchor assembly consisting of anchor bolt 27, anchor plate 28, return spring 35 and support member 50 is then inserted into the slider 34.
  • the anchor bolt 27 is inserted into a central bore 68 of the slider 34.
  • the slider 34 can already be clamped with the flange 36 in the housing 60 of the solenoid valve.
  • no annular shoulder 33 is provided, which limits the opening stroke of the anchor bolt by a stop on the slide piece 34. Instead, the opening stroke is limited by a stop of the armature bolt head 55 on the electromagnet or a projection of the electromagnet. This is necessary so that the anchor bolt 27 in FIG. 3 can be inserted into the slider 34 from above.
  • FIG. 3 deviating from the known arrangement shown in FIG. 2
  • the side of the slider 34 facing the support part 50 has a recess 52 into which the support part engages.
  • the lower end 67 of the anchor bolt 27 acts on the control valve member 25, which is pressed against the valve seat 24 by the closing force of the spring 31 when the electromagnet is not energized.
  • the side 59 of the support part 50 facing away from the anchor plate 28 and the weld seam 51 are spaced apart from the inner wall of the recess 52 by a gap.
  • the support part 50 which is moved with the anchor bolt, is prevented from striking the inner wall of the recess 52, since such a striking could result in the control valve member 25 not coming into contact with the valve seat 24.
  • the recess 52 is therefore designed in such a way that it can also accommodate the weld seam 51 and is always at a distance from it.
  • the lower side 59 of the support part 50 approaches the inner wall of the cylindrical recess 52 of the slider 34 when the solenoid valve closes, creating a hydraulic damping space.
  • the fuel compressed between the support part 50 and the recess 52 which can only escape laterally through the gap, advantageously dampens the impact of the anchor bolt 27 and the control valve member 25 coupled to the valve seat 24.
  • Gap between the anchor plate 28 and the support member 50 held fuel exerts a counterforce that counteracts the movement of the anchor plate.
  • the compensating movement of the anchor plate 28 is therefore limited by the position of the support part on the anchor bolt 27, which leads to a reversal of movement after previous damping and thus to a reduction in the ringing process.
  • FIG. 4 shows a further exemplary embodiment of the invention, which differs from the exemplary embodiment shown in FIG. 3 in that the supporting part 50 is positively fixed on the anchor bolt 27.
  • the support part 50 is designed as a sickle disk with an open recess 56 which is pushed laterally onto the anchor bolt with the open end.
  • the anchor bolt 27 has a circumferential groove 54, in which the inner contour of the recess 56 of the sickle disk 50 engages in a form-fitting manner.
  • the crescent disk 50 pushed onto the anchor bolt is secured in its position perpendicular to the anchor bolt by the recess 52 of the slider 34.
  • the path length by which the anchor bolt is displaced in the axial direction when the solenoid valve is opened and closed is significantly smaller than the depth of the recess 52, so that the sickle disk 50 cannot accidentally slip out of its position on the anchor bolt 27.
  • FIG. 5 shows a third exemplary embodiment, which shows a modification of the exemplary embodiment illustrated in FIG. 4.
  • the support part 50 is again designed as a sickle disk, which is pushed with the open end, not shown, onto a section 72 of the anchor bolt 27.
  • the diameter of the section 72 is made smaller than the diameter of the section of the anchor bolt 27 guided in the slider 34 and is delimited from it by a circumferential shoulder 71.
  • the return spring 35 is supported at one end on the anchor plate 28. The return spring 35 presses the other end Sickle disc 50 against the circumferential shoulder 71 formed on the anchor bolt 27.
  • the anchor assembly can be inserted as a preassembled unit in the slide 34, the anchor bolt 27 being inserted into the opening 68 and the sickle disc 50 at least partially penetrating into the recess 52. Due to the inner contour of the recess 52, the sickle plate 50 is secured against lateral slipping off the anchor bolt.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

L'invention concerne une électrovanne destinée à la commande d'une soupape d'injection d'un moteur à combustion interne. Cette électrovanne comprend un électroaimant (29), un induit mobile doté d'une plaque d'ancrage (28) et d'un boulon d'ancrage (27), et un organe de commande (25) qui se déplace avec l'induit et coopère avec un siège de soupape (24) et qui est destiné à ouvrir et fermer un canal de sortie de carburant (17) d'une chambre de pression de commande (14) de la soupape d'injection (1). La plaque d'ancrage (28) est montée sur le boulon d'ancrage (27) de manière à glisser sous l'effet de sa masse inerte dans la direction de fermeture de l'organe de commande de soupape (25) à l'encontre de la force de serrage d'un ressort de rappel (35) agissant sur la plaque d'ancrage (28). Cette électrovalve comprend également un dispositif amortisseur hydraulique qui permet d'amortir une postvibration de la plaque d'ancrage (28) lors de son déplacement dynamique sur le boulon d'ancrage (27). Pour simplifier le montage et réduire une postvibration désavantageuse de la plaque d'ancrage, le ressort de rappel (35) s'appuie, par son extrémité (62) opposée à la plaque d'ancrage (28), sur un élément support (50) placé sur le boulon d'ancrage (27) et se déplaçant avec le boulon d'ancrage. Cet élément support (50) constitue simultanément une partie (57) du dispositif d'amortissement.
EP01994586A 2000-11-23 2001-11-16 Electrovanne destinee a la commande d'une soupape d'injection d'un moteur a combustion interne Expired - Lifetime EP1259729B1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE10058007 2000-11-23
DE10058007 2000-11-23
DE10113008A DE10113008A1 (de) 2000-11-23 2001-03-17 Magnetventil zur Steuerung eines Einspritzventils einer Brennkraftmaschine
DE10113008 2001-03-17
PCT/DE2001/004318 WO2002042632A2 (fr) 2000-11-23 2001-11-16 Electrovanne destinee a la commande d'une soupape d'injection d'un moteur a combustion interne

Publications (2)

Publication Number Publication Date
EP1259729A2 true EP1259729A2 (fr) 2002-11-27
EP1259729B1 EP1259729B1 (fr) 2006-01-18

Family

ID=26007749

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01994586A Expired - Lifetime EP1259729B1 (fr) 2000-11-23 2001-11-16 Electrovanne destinee a la commande d'une soupape d'injection d'un moteur a combustion interne

Country Status (6)

Country Link
US (1) US6796543B2 (fr)
EP (1) EP1259729B1 (fr)
JP (1) JP4138481B2 (fr)
DE (1) DE50108770D1 (fr)
ES (1) ES2256333T3 (fr)
WO (1) WO2002042632A2 (fr)

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EP1801409A1 (fr) * 2005-12-23 2007-06-27 Delphi Technologies, Inc. Injecteur de carburant
CN104066964A (zh) * 2011-11-01 2014-09-24 康明斯公司 具有喷射控制阀筒的燃料喷射器

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DE102004035291A1 (de) * 2004-07-21 2006-03-16 Robert Bosch Gmbh Magnetventil für einen Injektor für Common-Rail-Kraftstoffeinspritzsysteme mit Dämpfungselement
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EP1834078B1 (fr) * 2005-01-07 2011-03-23 Delphi Technologies Holding S.à.r.l. Appareil d'injection de carburant
DE102005053115A1 (de) * 2005-11-08 2007-05-10 Robert Bosch Gmbh Optimierte Ankergruppenführung für Magnetventile
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ATE500411T1 (de) * 2008-12-29 2011-03-15 Fiat Ricerche Brennstoffeinspritzsystem mit hoher betriebswiederholbarkeit und -stabilität für einen verbrennungsmotor
US8316826B2 (en) * 2009-01-15 2012-11-27 Caterpillar Inc. Reducing variations in close coupled post injections in a fuel injector and fuel system using same
EP2444651B1 (fr) 2010-10-19 2013-07-10 Continental Automotive GmbH Ensemble de soupape pour soupape d'injection et soupape d'injection
US8689772B2 (en) 2011-05-19 2014-04-08 Caterpillar Inc. Fuel injector with telescoping armature overtravel feature
US8943906B2 (en) 2011-12-22 2015-02-03 Caterpillar Inc. Solenoid force measurement system and method
DE102012202253A1 (de) * 2012-02-15 2013-08-22 Robert Bosch Gmbh Brennstoffeinspritzventil
DE102012215448B3 (de) 2012-08-31 2013-12-12 Continental Automotive Gmbh Injektor zur Krafteinspritzung in eine Brennkraftmaschine
US9212639B2 (en) * 2012-11-02 2015-12-15 Caterpillar Inc. Debris robust fuel injector with co-axial control valve members and fuel system using same
US9644589B2 (en) * 2013-11-20 2017-05-09 Stanadyne Llc Debris diverter shield for fuel injector
EP2896813B1 (fr) 2014-01-17 2018-01-10 Continental Automotive GmbH Soupape d'injection de carburant pour moteurs à combustion interne
US9797342B2 (en) * 2014-10-28 2017-10-24 Caterpillar Inc. Port injection system for gaseous fuels
CN106894926B (zh) * 2017-01-25 2018-12-18 中国第一汽车股份有限公司 电控燃料喷射阀的控制阀
US11603815B1 (en) * 2021-11-04 2023-03-14 Standard Motor Products, Inc. Modular armature-needle assembly for fuel injectors

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CN104066964A (zh) * 2011-11-01 2014-09-24 康明斯公司 具有喷射控制阀筒的燃料喷射器
CN104066964B (zh) * 2011-11-01 2017-06-20 康明斯公司 具有喷射控制阀筒的燃料喷射器

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US6796543B2 (en) 2004-09-28
ES2256333T3 (es) 2006-07-16
WO2002042632A3 (fr) 2002-08-08
JP4138481B2 (ja) 2008-08-27
DE50108770D1 (de) 2006-04-06
WO2002042632A2 (fr) 2002-05-30
US20040026540A1 (en) 2004-02-12
EP1259729B1 (fr) 2006-01-18
JP2004514823A (ja) 2004-05-20

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