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EP2100026B1 - Injecteur de carburant avec électrovanne à siège sphérique - Google Patents

Injecteur de carburant avec électrovanne à siège sphérique Download PDF

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Publication number
EP2100026B1
EP2100026B1 EP07821236A EP07821236A EP2100026B1 EP 2100026 B1 EP2100026 B1 EP 2100026B1 EP 07821236 A EP07821236 A EP 07821236A EP 07821236 A EP07821236 A EP 07821236A EP 2100026 B1 EP2100026 B1 EP 2100026B1
Authority
EP
European Patent Office
Prior art keywords
pressure
valve
valve member
fuel injector
chamber
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
EP07821236A
Other languages
German (de)
English (en)
Other versions
EP2100026A1 (fr
Inventor
Nadja Eisenmenger
Hans-Christoph Magel
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 EP2100026A1 publication Critical patent/EP2100026A1/fr
Application granted granted Critical
Publication of EP2100026B1 publication Critical patent/EP2100026B1/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
    • 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
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • 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
    • 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
    • F02M63/0071—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059 characterised by guiding or centering means in valves including the absence of any guiding means, e.g. "flying arrangements"
    • 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
    • F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member
    • F02M63/008—Hollow valve members, e.g. members internally guided
    • 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
    • F02M2200/28—Details of throttles in fuel-injection apparatus
    • 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • 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
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails

Definitions

  • An injector for injecting fuel into a combustion chamber of an internal combustion engine in which an injection valve member is actuated via a solenoid-operated control valve, is off EP-A 1 612 403 known.
  • a flow restrictor from a control room in the fuel return can be closed or released.
  • the control chamber is bounded on one side by a control piston with which an injection valve member is actuated, which releases at least one injection opening into the combustion chamber of the internal combustion engine or closes it.
  • the outlet throttle is received in a body, which is on the side facing away from the control chamber with a tapered valve seat 29en.
  • a closing element is adjustable, which is connected to the armature of the solenoid valve.
  • an edge is formed on the closing element, which is provided against the conically shaped seat.
  • the closing element moves on an axial rod, which is integrally connected to the body in which the drainage throttle is formed.
  • a fuel injector which has a control valve with a movable piston, wherein the piston is mounted pressure balanced.
  • a control valve for a fuel injector with a force balanced control valve member is known, which cooperates with a flat or hemispherical valve seat.
  • z. B. on high-pressure accumulator injection systems used fuel injectors z. B. stroke-controlled injectors are used, which are operated by means of a solenoid valve to control the pressure in a control room.
  • the preferred needle-shaped injection valve member is z. B. controlled by a servo control room.
  • the solenoid valve is usually not pressure balanced and therefore requires high spring forces, high magnetic switching forces and due to the size of spring and magnet large space.
  • a disadvantage of such solenoid valves is the fact that there are severe restrictions on the sequence of multiple injections exist, so that very short successive injection intervals can not be realized.
  • Pressure compensated solenoid valves typically require much smaller spring forces, hence smaller magnetic forces to effect opening, as well as smaller valve strokes, thus allowing faster shift times.
  • a multiple injection capability can be improved.
  • these pressure-balanced designed valves require a high-pressure-tight guide and a linearly extending sealing edge, which correspond to the guide diameter of the valve member, which allows the pressure balance of the solenoid valve only.
  • a pressure-balanced solenoid valve wherein the preferably needle-shaped valve member has a self-adjusting mechanical wear due to material removal or deformation robust ball seat formed seat.
  • a valve seat of the present invention proposed solenoid valve with ball seat is formed on the valve sealing point, ie the seat of the valve member, a ball seat.
  • the ball seat can be z. B. represent by a hemispherical configuration of the seat of the valve member facing the end of the valve member.
  • the Z. B. hemispherical end of the valve member may be funnel-shaped, such. B. as a conical seat, trained seat in a valve piece.
  • the needle-shaped valve member is guided with an inner in an actuator housing loosely mounted pressure pin, whereby a pressure equalization can be achieved.
  • the solenoid valve is provided with a ball seat, so z. B. a balance of Parallelticiansohnem between the preferably needle-shaped valve member and a seat body, d. H. z. B. the valve piece, follow, so that thereby favorable multi-part valve design variants can be realized.
  • a further improvement is achieved by the connection of the ball seat proposed according to the invention with a small compression stage which is effective in the closing direction.
  • a hydraulic force acting on the valve member closing force is generated, whereby a bouncing is reduced in the valve closing, which in turn has beneficial effects on the self-adjusting wear, as occur during bouncing mechanical peak loads.
  • the damping behavior when closing the solenoid valve is improved by the effective pressure in the closing direction, since in the closed state of the seat of the preferably needle-shaped valve member, a hydraulic closing force builds up, which prevents reopening of the preferably needle-shaped valve member.
  • this allows optimized valve tuning and, on the other hand, improves the multiple injection capability of the fuel injector which is actuated by the solenoid valve having a ball seat proposed according to the invention.
  • a damping chamber can be provided in the high-pressure region of the fuel injector, whereby on the one hand the speed at which the preferably needle-shaped valve member moves and, on the other hand, the bouncing properties and bouncing stresses caused by the latter can advantageously be optimized with regard to the mechanical components. If the preferably needle-shaped injection valve member and an armature attracted by the solenoid valve armature formed integrally, a small moving mass can be achieved, and with optimized damping behavior can thus short intervals of individual injections realize, which favorably influences the Mehrfacheinspritzungswin.
  • the inventively proposed pressure balanced solenoid valve with ball seat can be used to control injection systems, in particular advantageously as a control valve for a servo-controlled Kraftstoffinjektor which is actuated by means of a solenoid valve.
  • the ball seat can be formed directly in the valve piece, in which a control chamber, in particular a servo control chamber, is located, and which closes a pressure chamber within the injector body of the fuel injector.
  • the sole FIGURE shows a section through the inventively proposed fuel injector, which is actuated by means of a solenoid valve which comprises a ball seat.
  • a fuel injector 10 is acted upon via a pressure accumulator 12, in which a system pressure p sys , with high-pressure fuel.
  • the system pressure p sys in pressure accumulator 12 is replaced by a not shown in the drawing high-pressure pumping unit, such.
  • the high-pressure line 14 opens within an injector 16 and acts on a reference numeral 34 designated pressure chamber with system pressure p sys stationary system pressure.
  • the fuel injector 10 further comprises a nozzle body 18, which is only indicated here, and an actuator housing 20, in which an actuator designed as a solenoid valve 22 is accommodated.
  • the actuator housing 20 is closed by a housing cover 24.
  • the housing cover 24 is provided with an external thread and can be screwed into a correspondingly formed internal thread of the actuator housing 20.
  • a magnetic core 26, an enclosed by this magnetic coil 28, a magnetic core 26 supporting supporting sleeve 30 are received and a part of a valve piece 32.
  • the partially housed in the actuator housing 20 valve piece 32 limits the aforementioned pressure chamber 34, in which the Pressure accumulator 12 outgoing high pressure line 14 opens.
  • a control chamber 36 is formed, which is filled via an inlet throttle 38 from under system pressure p sys pressure chamber 34 with fuel.
  • the control chamber 36 - formed in the drawing as a servo control room - is depressurized via an outlet throttle 40.
  • the outlet throttle 40 is also formed in the valve piece 32 and opens into a valve space identified by reference numeral 84.
  • the system pressure p sys applied via the inlet throttle 38 in the control chamber 36 acts on an end face 44 of a preferably needle-shaped injection valve member 42.
  • the injection valve member 42 comprises a support disk 46 against which a closing spring 48 is supported.
  • the support disk 46 opposite end of the closing spring 48 is supported on the valve piece 32 from.
  • annular space 52 extends through the injector housing 16. Via the annular space 52, fuel under system pressure p sys flows to a nozzle space designated by reference numeral 50, which is formed inside the nozzle body 18. From the annulus 52 passes under system pressure p sys standing fuel via at least one throttle point 56, the z. B. may be formed as at least one bevel on the circumference of the preferably needle-shaped injection valve member 42, in the nozzle chamber 50th
  • the injection valve member 42 comprises a pressure stage 54 in the region in which it is enclosed in the nozzle body 18 by the nozzle chamber 50.
  • injection ports 60 are closed at the combustion chamber end of the fuel injector 10 by the asked in his seat 58, preferably needle-shaped injection valve member 42.
  • At least one, preferably formed as a bevel throttle body 56 is at the periphery of the preferably needle-shaped injection valve member 42. About this at least one throttle point 56 of the system pressure p sys standing annular space 52 and the nozzle chamber 50 are hydraulically connected to each other.
  • the solenoid valve 22 accommodated in the actuator housing 20 comprises a valve spring 70, which encloses a pressure pin 66.
  • the valve spring 70 is supported on the underside of the housing cover 24.
  • the pressure pin 66 is loosely received in the actuator housing 20.
  • the valve spring 70 acts on an upper end side of a valve member designed as a valve member 62.
  • an anchor plate 64 is formed, which is disposed opposite to the solenoid coil 28 of the solenoid valve 22.
  • the pressure pin 66 is formed in a diameter that represents a guide diameter 68 for the valve member 62.
  • a lower end face of the pressure pin 66 bounded by the preferably needle-shaped valve member 62 a pressure compensation chamber 78.
  • the pressure relief chamber 66 and the valve member 62 limited pressure compensation chamber 78 communicates via a flow connection 74 with a valve chamber 84 in connection.
  • the valve space 84 is bounded by a conical surface 82 in the valve piece 32 on the one hand and on the other hand by a spherical surface 86 at the lower end of the valve member 62.
  • the spherical surface 86 which represents the ball seat, on the valve member 62 is executed.
  • spherical surface 86 at the valve piece 32 facing the end of the preferably needle-shaped valve member 62 can be achieved in an advantageous manner, a compensation of parallelism errors between the valve member 62 and the seat body performing valve member 32.
  • inventively proposed arrangement favorable, multi-part valve bodies can be realized by the inventively proposed arrangement favorable, multi-part valve bodies.
  • the conical surface 82 can also be formed on the valve member 62 and the spherical surface 86 on the valve piece 32 to be executed. Further, it is possible to realize both the valve member 62 and the valve piece 32 each spherical geometries.
  • the pressure balance of the solenoid valve 22 acts. It can be inventively proposed valve design realized by forming a spherical surface 86 ball seat in cooperation with a Conical surface 82 realize because the pressure pin 66 can be mounted independently of the valve seat 80 from the opposite side of the seating area.
  • a flow connection is identified, which connects the pressure equalization or damping chamber 78 with the valve space 84.
  • An embodiment of the fuel injector shown in the drawing is given by the fact that at the pressure pin 66, on which the preferably needle-shaped valve member 62 is guided, an effective compression in the closing direction is generated.
  • the effective in the closing direction of the preferably needle-shaped valve member 62 pressure stage can be achieved by increasing the guide diameter 68 of the loosely received in the actuator housing 20 pressure pin 66 with respect to the diameter of the given by the spherical surface 86 ball seat.
  • a hydraulic valve closing force is generated, whereby a bouncing of the Solenoid valve when closing the valve member 62 is reduced.
  • the damping behavior when closing the valve member 62 can be improved by the pressure acting in the closing direction, given by the enlargement of the guide diameter 68 with respect to the diameter of the given by the spherical surface 86 ball seat, since in the closed state of the ball seat builds up a hydraulic closing force which prevents reopening of the preferably needle-shaped valve member 62.
  • This in turn allows for optimized valve tuning and an improvement in the multiple injection capability of the fuel injector 10 proposed according to the invention.
  • the speed at which the valve member 62 opens can be optimized and the bouncing characteristics improved. If the preferably needle-shaped injection valve member 62 and the armature plate 64 designed as a component, so sets a small mass to be moved, which leads through a damper throttle 76, which is arranged in the flow connection 74 to an optimized damping behavior, resulting in very short distances be made possible with individual fuel injections in quick succession via the injection openings 30.
  • the ball seat realized by the spherical surface 86 is formed directly on the valve piece 32, which limits the control space 36 serving as a servo control room and separates from the pressure space 34 in the injector housing 16 under system pressure p sys .
  • the valve piece 32 is made in a sealing manner against the injector body 16 via the support sleeve 30, the magnetic core 26 resting thereon and the housing cover 24, with which the actuator housing 20 is closed.
  • the opening behavior of the preferably needle-shaped injection valve member 42 can be optimized by means of the throttle point 56, which is formed on the circumference thereof and has at least one preferably formed as a bevel.
  • the at least one throttle point 56 formed on the circumference of the preferably needle-shaped injection valve member 42 provides a hydraulic connection with the annular space 52 under system pressure p sys in the injector body 16 with the nozzle chamber 50 formed in the nozzle body 18 of the fuel injector 10.
  • the pressure compensated solenoid valve 22 is employed in fuel injection injection systems as a servo-controlled fuel injector control valve applicable to high-pressure common-rail injection systems.

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)
  • Magnetically Actuated Valves (AREA)

Claims (6)

  1. Injecteur de carburant (10) pour l'injection de carburant dans la chambre de combustion d'un moteur à combustion interne, dans lequel un organe de soupape d'injection (42) est actionné par le biais d'une détente de pression d'un espace de commande (36) qui est sollicité avec une pression de système psys et dans lequel la détente de pression de l'espace de commande (36) s'effectue par le biais d'une électrovanne à compensation de pression (22), dont l'organe de soupape (62) ouvre ou ferme un siège de soupape (80), caractérisé en ce que,
    - une surface de forme sphérique (86) est réalisée sur l'organe de soupape (62), laquelle forme avec une surface conique (82) dans une pièce de soupape (32) un siège de soupape (80).
  2. Injecteur de carburant (10) selon la revendication 1, caractérisé en ce que l'organe de soupape (62) est guidé sur une tige de pression (66) et limite avec celle-ci un espace de compensation de pression (78).
  3. Injecteur de carburant (10) selon la revendication 2, caractérisé en ce que l'organe de soupape (62) présente une connexion d'écoulement (74) entre l'espace de compensation de pression ou l'espace d'amortissement (78) et le siège de soupape (80).
  4. Injecteur de carburant (10) selon la revendication 3, caractérisé en ce qu'un point d'étranglement (76) est réalisé dans la connexion d'écoulement (74).
  5. Injecteur de carburant (10) selon la revendication 1, caractérisé en ce que l'organe de soupape (62) est guidé sur une tige de pression (66) dont le diamètre de guidage (68) correspond à un diamètre intérieur de l'organe de soupape (62).
  6. Injecteur de carburant (10) selon la revendication 1, caractérisé en ce que le siège de soupape (80) est réalisé sur une pièce de soupape (32) qui limite l'espace de commande (36) et qui ferme un espace de pression (34) dans le corps d'injecteur (16) vis-à-vis d'une région à basse pression.
EP07821236A 2006-12-04 2007-10-12 Injecteur de carburant avec électrovanne à siège sphérique Not-in-force EP2100026B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006057025A DE102006057025A1 (de) 2006-12-04 2006-12-04 Magnetventil mit Kugelsitz
PCT/EP2007/060869 WO2008068093A1 (fr) 2006-12-04 2007-10-12 Injecteur de carburant avec électrovanne à siège sphérique

Publications (2)

Publication Number Publication Date
EP2100026A1 EP2100026A1 (fr) 2009-09-16
EP2100026B1 true EP2100026B1 (fr) 2010-12-22

Family

ID=39111887

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07821236A Not-in-force EP2100026B1 (fr) 2006-12-04 2007-10-12 Injecteur de carburant avec électrovanne à siège sphérique

Country Status (5)

Country Link
EP (1) EP2100026B1 (fr)
CN (1) CN101548092B (fr)
AT (1) ATE492719T1 (fr)
DE (2) DE102006057025A1 (fr)
WO (1) WO2008068093A1 (fr)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007011685A1 (de) * 2007-03-09 2008-09-11 Robert Bosch Gmbh Kraftstoffinjektor mit verbessertem Steuerventil
DE102007035698A1 (de) * 2007-07-30 2009-02-05 Robert Bosch Gmbh Kraftstoffeinspritzventil mit verbesserter Dichtheit am Dichtsitz eines druckausgeglichenen Steuerventils
DE102008001600A1 (de) * 2008-05-06 2009-11-12 Robert Bosch Gmbh Kraftstoff-Injektor mit einem eine Druckstufe aufweisenden Steuerventil
DE102009046563A1 (de) * 2009-11-10 2011-05-12 Robert Bosch Gmbh Kraftstoffinjektor
DE102009060029A1 (de) * 2009-12-21 2011-06-22 Robert Bosch GmbH, 70469 Elektromagnetisch schaltbares Ventil zum Einbau in einen Einbaublock
CN102213165B (zh) * 2010-04-08 2013-02-13 北京亚新科天纬油泵油嘴股份有限公司 高压共轨电控喷油器
DE102013206383A1 (de) * 2013-04-11 2014-10-16 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen
DE102018109206A1 (de) * 2018-04-18 2019-10-24 Liebherr-Components Deggendorf Gmbh Injektor zum Einspritzen von Kraftstoff

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008055724A1 (fr) * 2006-11-10 2008-05-15 Robert Bosch Gmbh Injecteur pour l'injection de carburant

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3555264B2 (ja) * 1995-07-14 2004-08-18 いすゞ自動車株式会社 内燃機関の燃料噴射装置
DE29807601U1 (de) * 1998-04-27 1998-08-20 FEV Motorentechnik GmbH & Co. KG, 52078 Aachen Hydraulisches Schiebersitzventil
DE19952511B4 (de) 1999-10-30 2004-09-30 Robert Bosch Gmbh Common-Rail-Injektor
ES2277229T3 (es) * 2004-06-30 2007-07-01 C.R.F. Societa Consortile Per Azioni Servovalvula para controlar el inyector de combustible de un motor de combustion interna.
AT500889B8 (de) * 2004-08-06 2007-02-15 Bosch Gmbh Robert Vorrichtung zum einspritzen von kraftstoff in den brennraum einer brennkraftmaschine
CN1773098A (zh) * 2005-07-25 2006-05-17 无锡油泵油嘴研究所 共轨喷油系统电控喷油器
DE102005062549A1 (de) * 2005-12-27 2007-07-05 Robert Bosch Gmbh Kraftstoffinjektor für eine Brennkraftmaschine, sowie Verfahren zum Herstellen eines Steuerventils für einen Kraftstoffinjektor

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008055724A1 (fr) * 2006-11-10 2008-05-15 Robert Bosch Gmbh Injecteur pour l'injection de carburant

Also Published As

Publication number Publication date
ATE492719T1 (de) 2011-01-15
WO2008068093A1 (fr) 2008-06-12
EP2100026A1 (fr) 2009-09-16
CN101548092B (zh) 2012-12-19
DE502007006059D1 (de) 2011-02-03
DE102006057025A1 (de) 2008-06-05
CN101548092A (zh) 2009-09-30

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