EP1650427A1 - Soupape d'injection de carburant pour des moteurs à combustion interne - Google Patents

Soupape d'injection de carburant pour des moteurs à combustion interne Download PDF

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Publication number
EP1650427A1
EP1650427A1 EP05109414A EP05109414A EP1650427A1 EP 1650427 A1 EP1650427 A1 EP 1650427A1 EP 05109414 A EP05109414 A EP 05109414A EP 05109414 A EP05109414 A EP 05109414A EP 1650427 A1 EP1650427 A1 EP 1650427A1
Authority
EP
European Patent Office
Prior art keywords
valve
needle
throttle
chamber
fuel injection
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
EP05109414A
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German (de)
English (en)
Other versions
EP1650427B1 (fr
Inventor
Stefan Schuerg
Wolfgang Stoecklein
Holger Rapp
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 EP1650427A1 publication Critical patent/EP1650427A1/fr
Application granted granted Critical
Publication of EP1650427B1 publication Critical patent/EP1650427B1/fr
Ceased 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
    • 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
    • F02M45/04—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 with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/08—Injectors peculiar thereto
    • F02M45/086—Having more than one injection-valve controlling discharge orifices
    • 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
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
    • 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
    • F02M63/0045—Three-way valves
    • 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
    • F02M2200/46—Valves, e.g. injectors, with concentric valve bodies
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/001—Control chambers formed by movable sleeves
    • 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
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators

Definitions

  • the invention is based on a fuel injection valve, as is known, for example, from document DE 103 38 228 A1.
  • the known fuel injection valve for internal combustion engines has a valve body in which a valve outer needle and therein a longitudinally displaceably guided inner valve needle are arranged. Both the valve outer needle and the valve inner needle cooperate with a valve seat and thereby control the opening of at least one injection port. If the valve needles release the respective injection openings as a result of their longitudinal movement, fuel is injected from the pressure chamber through the injection openings into the combustion chamber of the corresponding internal combustion engine.
  • valve needles limit by their valve faces facing away from the end faces a control chamber in which via an inner inlet throttle and an outer inlet throttle fuel can be introduced under high pressure.
  • the valve inner needle closes during its opening stroke when it arrives with its end face to a stop, the inner inlet throttle and thereby reduces the flow of fuel under high pressure in the control room, because now only still the outer inlet throttle is open. This makes it possible to control only one of the two valve pins, while the other remains in its closed position.
  • the fuel injection then takes place only through part of the injection openings, which results in more favorable conditions in the combustion chamber especially in the partial load range.
  • the fuel injection valve known from DE 103 38 228 A1 operates in such a manner that, when the valve outer needle and the inner valve needle bear against the respective stop, the control chamber is separated into an outer subspace and an inner subspace. Both the inner subspace and the outer subspace are connected via a respective outlet throttle with a control valve, so that can be set on the flow of pressure in the control room and thus the pressure in the respective subspaces.
  • a control valve so that can be set on the flow of pressure in the control room and thus the pressure in the respective subspaces.
  • two flow restrictors must be formed, which are each very expensive to manufacture, since they are to be produced with very high precision.
  • the controller shown there does not allow the opening of the valve inner needle in front of the valve outer needle, which is often desired.
  • the erfmdungssiee fuel injection valve with the characterizing features of claim 1 has the opposite on the advantage that an accurate control of the opening stroke both the valve inner needle and the valve outer needle is possible precisely and with little effort.
  • the control chamber is connected via exactly one outlet throttle with a valve chamber of a control valve, wherein the valve space in turn is connectable by the control valve with a leakage oil space in which a correspondingly lower pressure prevails.
  • pressure conditions in the control chamber can be generated, which allow either only the valve inner needle or the valve inner needle to open together with the valve outer needle and thus to inject fuel into the combustion chamber either through a part or through all the injection openings.
  • control chamber is separated by the system of the valve inner needle to a corresponding throttle plate, which includes the inner inlet throttle in an inner subspace bounded by the end face of the valve inner needle and the throttle plate, and an outer subspace.
  • a throttle plate which includes the inner inlet throttle in an inner subspace bounded by the end face of the valve inner needle and the throttle plate, and an outer subspace.
  • control valve includes a valve chamber in which a valve element is arranged, which can be moved by an actuator.
  • the valve element can assume at least two switching positions, wherein in a first switching position, the connection of the valve chamber is interrupted with the leakage oil space, while this connection is open in a second switching position of the valve element.
  • Particularly advantageous in this case is the configuration in which an additional bypass throttle opens into the valve space, via which the valve space can be connected to a high-pressure region of the fuel injection valve.
  • the valve element closes the bypass throttle in its second switching position while it is released in the first switching position, so that the valve space is connected not only via the outlet throttle to the control chamber but also to the high-pressure region of the fuel injection valve.
  • valve element has a circular sealing surface whose diameter corresponds at least approximately to the diameter of the junction of the bypass throttle in the valve chamber.
  • valve outer needle is guided in a region remote from the valve seat in a sleeve which limits the control chamber to the outside.
  • the outer inlet throttle is formed, via which the control chamber is connected to the high-pressure region of the fuel injection valve.
  • the inner inlet throttle opens when the valve inner needle rests with its end face in the open position on the stop, in a formed on the end face of the valve inner needle recess.
  • the recess is in turn connected via the outer inlet throttle, which is formed in the valve inner needle, with the second subspace of the control chamber. This comes into play when the valve inner needle is in its open position and the outer subspace is filled with fuel via this outer inlet throttle.
  • the design of the outer inlet throttle in the valve inner needle has the advantage that the components of the fuel injection valve is easier to manufacture, since an inlet throttle is formed on the easily accessible valve inner needle, which is less expensive and can be produced with higher precision than corresponding recesses in the valve body.
  • FIG. 1 shows a schematic representation of a longitudinal section through a fuel injection valve according to the invention.
  • the fuel injection valve has a valve body 1, a throttle disk 2, a valve disk 4 and a holding body 6. These components of the fuel injection valve are arranged in this order and are pressed against each other by a mechanical tensioning device, not shown in the drawing.
  • a pressure chamber 3 is formed which can be filled with fuel under high pressure via a feed channel 12 extending in the throttle plate 2 and the valve disk 4 and the holding body 6.
  • the pressure space 3 is delimited at the combustion-chamber-side end of the fuel injection valve by a conical valve seat 14, from which outer injection openings 20 and inner injection openings 22 originate.
  • the inner injection openings 22 have in the embodiment shown here a smaller diameter than the outer injection openings 20, but these ratios may also be reversed.
  • a valve outer needle 5 is arranged longitudinally displaceable, which has a substantially sleeve shape and having an outer sealing surface 24 at its valve seat side end.
  • the valve outer needle 5 cooperates with its outer sealing surface 24 with the valve seat 14 and closes this by contact with the valve seat 14, the outer injection ports 20 so that the outer injection ports 20 are sealed both against the inner region of the valve outer needle 5, as well as against the outer region.
  • the valve outer needle 5 is guided in a central portion on the wall of the pressure chamber 3, wherein it is ensured via recesses 19 that the upstream and the downstream part of the pressure chamber 3 are hydraulically connected to each other to allow fuel flow to the injection ports 20, 22.
  • a sleeve 16 which is supported at one end to the throttle plate 2 and which is acted upon at the other end by a closing spring 17 which presses the sleeve 16 against the throttle plate 2.
  • the closing spring 17 is supported here on a shoulder 18 formed on the valve outer needle 5 and has a compressive prestress, so that in each position of the valve outer needle 5 a corresponding force is exerted on the sleeve 16 and correspondingly on the valve outer needle 5.
  • a valve inner needle 7 is arranged longitudinally displaceable, which is formed substantially piston-shaped and is guided in the valve seat facing away from the valve outer needle 5.
  • the inner valve needle 7 tapers, starting from the guided section to form an inner pressure shoulder 30 and merges at its valve seat side end into an inner sealing surface 26, with which the inner valve needle 7 so cooperates with the valve seat 14 that when the valve inner needle 7 on the valve seat 14, the inner injection openings 22 are closed.
  • the intermediate space 9 formed between the valve inner needle 7 and the valve outer needle 5 is connected to the pressure space 3 via a connecting throttle 11 formed in the valve outer needle 5, so that, when the inner valve needle 7 has lifted off the valve seat 14, fuel from the pressure chamber 3 via the connecting throttle 11 flows into the intermediate space 9 and is injected from there via the inner injection openings 22 into the combustion chamber.
  • the valve inner needle 7 has an inner end face 34 at its end facing away from the valve seat, just as the valve outer needle 5 has an outer end face 36.
  • the end faces 34, 36 of the valve needles 5,7 limit together with the sleeve 16 and the throttle plate 2 a control chamber 27, wherein depending on the pressure in the control chamber 27, a hydraulic force in the direction of the valve seat 14 on the valve inner needle 7 and the valve outer needle 5 is exercised.
  • the control chamber 27 is connected via an inner inlet throttle 40 and an outer inlet throttle 42 with the high-pressure region of the fuel injection valve, wherein the high-pressure region comprises the pressure chamber 3 and the inlet channel 12, in which there is always a high, predetermined fuel pressure.
  • the control chamber 27 is also connected via an outlet throttle 44 with a valve chamber 51 of a control valve 50.
  • the valve chamber 51 is in turn connected via a leakage oil connection 54 with a leakage oil space, not shown in the drawing and on the other hand via a bypass throttle 46 to the pressure chamber 3, wherein the bypass throttle 46 forms an inlet port 146 in the valve chamber 51.
  • a valve element 52 is arranged, which is connected to a likewise not shown in the drawing, electrically operated actuator.
  • This actuator can, for example a piezo actuator, which allows the valve element 52 in the valve chamber 51 to move so that it is closed between a first switching position in which the leak oil connection 54 is closed, and a second switching position in which the bypass throttle 46 and the Leakage oil connection 54 is opened, can be moved back and forth. If a piezoelectric actuator is used, any position between the first and the second switching position of the valve element 52 can also be approached.
  • the valve element 52 in this case has an end face 53, which is opposite to the inlet opening 146 of the bypass throttle 46. If the end face 53 rests on the throttle disk 2, the inlet opening 146 is closed while it is otherwise released by the valve element 52.
  • valve element 52 is located at the beginning in the first switching position, in which the leak oil connection 54 is closed.
  • the valve chamber 51 is flooded via the bypass throttle 46 with the fuel pressure in the pressure chamber 3 and on the other hand prevails in the control chamber 27 also the high pressure from the inlet channel 12 and the pressure chamber 3, as he via the inner inlet throttle 40 and the outer inlet throttle 42 associated with it.
  • the pressure in the control chamber 27 results in a hydraulic force on the outer end face 36 of the valve outer needle 5 and also on the inner end face 34 of the valve inner needle 7, so that both valve needles 5, 7 are pressed against the valve seat 14 and thus the outer injection openings 20 and Close the inner injection openings 22.
  • By the connecting throttle 11 and the recesses 19 prevails both in the pressure chamber 3, as well as in the space 9, a uniformly high fuel pressure. If an injection takes place, then the valve element 52 is moved from the first switching position to the second switching position via the actuator, so that the leakage oil connection 54 is opened, while at the same time the bypass throttle 46 is closed. As a result, the pressure in the valve chamber 51 decreases and thus because of the outlet throttle 44 in the control chamber 27.
  • valve inner needle 7 moves away from the valve seat 14 and releases the inner injection openings 22, which are supplied with fuel from the gap 9.
  • the pressure rises there again, as shown in FIG. 2 between the times t 1 and t 2 .
  • stroke h i of the valve inner needle 7 is shown, which reaches its maximum at the time t 2 , that is, the valve inner needle 7 has reached its stop, ie on the throttle plate 2.
  • the inner end face 34 of the valve inner needle 7 is here structured and has a sealing region 38 which is formed as an annular edge.
  • the control chamber 27 Upon installation of the valve inner needle 7 on the throttle plate 2, the control chamber 27 is so separated into an inner subspace 127 and an outer subspace 227, wherein the inner subspace 127 is limited by lying within the sealing portion 38 of the inner end face 34 and the throttle plate 2, while the outer subspace 227 includes the remaining control space 27.
  • the inner inlet throttle 40 is thus hydraulically separated by the system of the inner valve needle 7 on the throttle plate 2 from the outer subspace 227.
  • the pressure in the inlet channel 12 is immediately set again via the inner inlet throttle 40.
  • the reduced pressure in the outer subspace 227 is sufficient to keep the inner valve needle 7 in its open position.
  • the control valve 50 is actuated again by the valve element 52 moves to an intermediate position, ie between the first and the second switching position.
  • the bypass throttle 46 is slightly opened, while the drain connection 54 is slightly closed. Since a lower pressure prevails in the valve chamber 51 than in the inlet channel 12, the pressure in the outer sub-chamber 227 decreases again and reaches a pressure p 2 after a certain time, which is so low that the valve inner needle 7 remains in its open position , while the valve outer needle 5 by the hydraulic pressure in the outer subspace 227 is still held in its closed position.
  • the control valve 50 is actuated again and the valve element 52 moves back into its first switching position.
  • valve element 52 is likewise moved from the first to the second switching position at the beginning of the injection.
  • the course of pressure p s , stroke h v of the valve element 51, stroke h i of the valve inner needle 7 and stroke h a of the valve outer needle 5 is shown in FIG.
  • the course up to the time t 2 corresponds to the course that has already been shown during the injection through the inner injection openings 22.
  • the control valve 50 is not actuated, but remains in its second switching position.
  • the pressure p s in the outer subspace 227 decreases further below the opening pressure p oe2 of the valve outer needle 5, so that the outer pressure shoulder 32 and parts of the outer pressure surface 24 are now moved away from the valve seat 14 on the valve outer needle 5 by the hydraulic forces and the outer injection openings 20 releases.
  • the point in time at which the valve outer needle 5 starts to move is designated t 2 'in FIG.
  • the valve outer needle 5 reaches its maximum stroke, that is, it comes into abutment against the throttle plate 2.
  • the outer end face 36 of the valve outer needle 5 in this case is slightly bevelled, so that the outer end face 36 still remains acted upon by the fuel pressure of the outer sub-space 227.
  • the valve element 52 is moved back into the first switching position and the fuel pressure builds up again in the control chamber 27 and pushes the valve inner needle 7 and the valve outer needle 5 back into their respective closed position.
  • the position of the outer inlet throttle 42 can also be varied. 4 shows a further embodiment is shown schematically, wherein only the area of the control chamber 27 is shown.
  • the outer inlet throttle 42 is in this case formed in the sleeve 16 and thus connects directly the pressure chamber 3 with the control chamber 27.
  • the outer end face 36 is, unlike in the embodiment of Figure 1, chamfered so that on the inner edge of the outer end face 36, an edge is formed, which rests in the open position of the valve outer needle 5 on the throttle plate 2. Care must be taken to provide a corresponding recess in the throttle plate 2, so that the outlet throttle 44 remains in communication both with the outer subspace 227 and in the inner subspace 127.
  • FIG. 5 shows a further exemplary embodiment, in which the second inlet throttle 42 is formed in the valve inner needle 7.
  • a recess 47 is formed on the inner end face 34, which has the shape of a blind bore.
  • the outer inlet throttle 42 is radially outward and connects so when planting the valve inner needle 7 at the stop, so on the throttle plate 2, the inner subspace 127 with the outer subspace 227.
  • the filling of the outer subspace 227 is thus carried out by in Series switched reactors, namely the inner inlet throttle 40 and the outer inlet throttle 42. Otherwise, the function of both the embodiment shown in Figure 4, and the embodiment shown in Figure 5 as described above.
  • I is the course of the force F over the stroke h v , as it results when the circular end face 53 of the valve member 52 is significantly larger than the diameter of the mouth 146 of the bypass throttle 46.
  • a voltage U 1 must be applied to the piezo actuator, which is to move the valve element 52 here.

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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)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)
EP20050109414 2004-10-23 2005-10-11 Soupape d'injection de carburant pour des moteurs à combustion interne Ceased EP1650427B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200410051756 DE102004051756A1 (de) 2004-10-23 2004-10-23 Kraftstoffeinspritzventil für Brennkraftmaschinen

Publications (2)

Publication Number Publication Date
EP1650427A1 true EP1650427A1 (fr) 2006-04-26
EP1650427B1 EP1650427B1 (fr) 2007-11-07

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Family Applications (1)

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EP20050109414 Ceased EP1650427B1 (fr) 2004-10-23 2005-10-11 Soupape d'injection de carburant pour des moteurs à combustion interne

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EP (1) EP1650427B1 (fr)
DE (2) DE102004051756A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007098988A1 (fr) * 2006-02-28 2007-09-07 Robert Bosch Gmbh Soupape d'injection de carburant
EP2050951A1 (fr) * 2007-10-18 2009-04-22 Delphi Technologies, Inc. Injecteur à carburant
US8925524B2 (en) 2009-06-15 2015-01-06 Delphi International Operations Luxembourg S.A.R.L. Fuel injector
CN111502880A (zh) * 2020-03-17 2020-08-07 成都威特电喷有限责任公司 一种防止动态泄漏的电控高压燃油喷射装置

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2002090754A1 (fr) * 2001-05-08 2002-11-14 Robert Bosch Gmbh Soupape d'injection de carburant pour moteurs a combustion
DE10246974A1 (de) * 2002-10-09 2004-04-22 Robert Bosch Gmbh Kraftstoffeinspritzvorrichtung für eine Brennkraftmaschine
US20040129804A1 (en) * 2002-02-14 2004-07-08 Detlev Potz Fuel injection valve for internal combustion engines
WO2004070192A1 (fr) * 2003-02-05 2004-08-19 Robert Bosch Gmbh Soupape d'injection de carburant pourvue de deux pointeaux coaxiaux
WO2005019638A1 (fr) * 2003-08-20 2005-03-03 Robert Bosch Gmbh Soupape d'injection de carburant pour des moteurs a combustion interne

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2002090754A1 (fr) * 2001-05-08 2002-11-14 Robert Bosch Gmbh Soupape d'injection de carburant pour moteurs a combustion
US20040129804A1 (en) * 2002-02-14 2004-07-08 Detlev Potz Fuel injection valve for internal combustion engines
DE10246974A1 (de) * 2002-10-09 2004-04-22 Robert Bosch Gmbh Kraftstoffeinspritzvorrichtung für eine Brennkraftmaschine
WO2004070192A1 (fr) * 2003-02-05 2004-08-19 Robert Bosch Gmbh Soupape d'injection de carburant pourvue de deux pointeaux coaxiaux
WO2005019638A1 (fr) * 2003-08-20 2005-03-03 Robert Bosch Gmbh Soupape d'injection de carburant pour des moteurs a combustion interne
DE10338228A1 (de) 2003-08-20 2005-03-10 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007098988A1 (fr) * 2006-02-28 2007-09-07 Robert Bosch Gmbh Soupape d'injection de carburant
EP2050951A1 (fr) * 2007-10-18 2009-04-22 Delphi Technologies, Inc. Injecteur à carburant
US7967223B2 (en) 2007-10-18 2011-06-28 Delphi Technologies Holdings S.arl Fuel injector
CN101429911B (zh) * 2007-10-18 2012-12-12 德尔福技术控股有限公司 燃油喷射器
US8925524B2 (en) 2009-06-15 2015-01-06 Delphi International Operations Luxembourg S.A.R.L. Fuel injector
CN111502880A (zh) * 2020-03-17 2020-08-07 成都威特电喷有限责任公司 一种防止动态泄漏的电控高压燃油喷射装置

Also Published As

Publication number Publication date
DE102004051756A1 (de) 2006-04-27
EP1650427B1 (fr) 2007-11-07
DE502005001871D1 (de) 2007-12-20

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