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EP1363015A1 - Système d'injection de carburant pour un moteur à combustion interne - Google Patents

Système d'injection de carburant pour un moteur à combustion interne Download PDF

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Publication number
EP1363015A1
EP1363015A1 EP03004642A EP03004642A EP1363015A1 EP 1363015 A1 EP1363015 A1 EP 1363015A1 EP 03004642 A EP03004642 A EP 03004642A EP 03004642 A EP03004642 A EP 03004642A EP 1363015 A1 EP1363015 A1 EP 1363015A1
Authority
EP
European Patent Office
Prior art keywords
control
injection
valve member
pressure
injection valve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP03004642A
Other languages
German (de)
English (en)
Inventor
Peter Boehland
Godehard Nentwig
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 EP1363015A1 publication Critical patent/EP1363015A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • 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
    • 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically
    • 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

Definitions

  • the invention is based on one Fuel injection device for an internal combustion engine according to the preamble of claim 1.
  • Such a fuel injector is due to the EP 0 957 261 A1 is known.
  • This Fuel injector has the for each cylinder Internal combustion engine with a high pressure fuel pump and with this connected fuel injector.
  • the High pressure fuel pump has a through Internal combustion engine driven in one stroke Pump piston that delimits a pump workspace that connected to a pressure chamber of the fuel injector is.
  • the fuel injector has one Injection valve member through which at least one Injection opening is controlled and that of that in the pressure chamber prevailing pressure against a closing force in an opening direction is movable.
  • a first electrically controlled control valve is used to control the Fuel injection a connection of the Pump work room controlled with a relief room.
  • the Injector member is one of those in one pressure in the fuel-filled control pressure chamber assigned area, over which by the im Control pressure prevailing pressure a force in Closing direction is generated on the injection valve member.
  • the control pressure chamber has a connection with the Pump workspace open and one electrically by a second actuated control valve controlled connection with a Relief chamber. If the pressure in the Pump work space and thus in the pressure chamber of the Fuel injection valve in the opening direction on the Injector member force is greater than that generated by the pressure generated in the control pressure chamber and the closing force on the injector member so moved the injection valve member is in the opening direction and there the at least one injection opening free.
  • the Injection cross section through the injector member being controlled is always the same size. This makes possible not under all operating conditions of the internal combustion engine optimal fuel injection.
  • the fuel injection device with the Features according to claim 1 has the advantage that through the second injection valve member with the at least a second injection port additional Injection cross section can be released or closed can, so that the injection cross section to the Operating conditions of the internal combustion engine optimally adapted can be.
  • the control of the injection cross section takes place thereby in a simple manner by means of the second electrically operated control valve controlled pressure in the Control pressure chamber.
  • Training according to claim 2 allows a staggered opening of the second injector member to the first Injection valve member.
  • the training according to claim 3 enables an optimal pre-injection of a low Fuel quantity.
  • the training according to claim 4 enables it that the first injector member based on its with maximum opening stroke open position by the in Control pressure chamber pressure no longer closed can be and thus independently the opening of the second Injection valve member through the in the control pressure chamber prevailing pressure can be controlled.
  • Training according to claim 5 enables an optimal main injection, if only a relatively small amount of fuel to be injected.
  • the training according to claim 6 allows an optimal main injection, if with this a relatively large amount of fuel is to be injected.
  • FIG. 1 shows a Fuel injection device for an internal combustion engine in a schematic representation in a longitudinal section
  • Figure 2 in an enlarged view one in Figure 1 with II designated section of the fuel injection device
  • 3 shows an enlarged view of a III in FIG designated section of the fuel injector with closed injection valve members
  • Figure 4 den Section III with open injection valve members
  • Figure 5 stroke profiles of the injection valve members Fuel injector over time during one Injection cycle.
  • FIG. 1 to 4 is one Fuel injection device for an internal combustion engine shown a motor vehicle.
  • the internal combustion engine is preferably a self-igniting internal combustion engine.
  • the Fuel injection device is a so-called pump-nozzle system or designed as a pump-line-nozzle system and points for each cylinder of the internal combustion engine a high pressure fuel pump 10 and one with this connected fuel injector 12.
  • At a Training as a pump-line-nozzle system is the High pressure fuel pump 10 removed from Fuel injector 12 arranged and with this over a line connected.
  • the exemplary embodiment is the fuel injection device designed as a pump-nozzle system, the High pressure fuel pump 10 and that Fuel injection valve 12 directly connected to each other are and form a structural unit.
  • the High-pressure fuel pump 10 has one in one Cylinder bore 16 in a pump body 14 tightly guided Pump piston 18 on by a cam 20 one Camshaft of the internal combustion engine against the force of one Return spring 19 is driven in one stroke.
  • the Pump piston 18 limits one in the cylinder 16 Pump working space 22 in which the delivery stroke of Pump piston 18 fuel is compressed under high pressure.
  • the pump working space 22 is during the suction stroke of the pump piston 18 fuel in a manner not shown Fuel tank 24 of the motor vehicle supplied.
  • the fuel injection valve 12 has a valve body 26 on, which can be formed in several parts, in which a first Injection valve member 28 in a bore 30 is guided longitudinally.
  • a first Injection valve member 28 in a bore 30 is guided longitudinally.
  • Figure 2 has the valve body 26 on the combustion chamber of the End cylinder facing the engine at least one first, preferably several first Injection openings 32 on the circumference of the Valve body 26 are arranged distributed.
  • the first Injection valve member 28 faces the combustion chamber facing end region, for example an approximately conical one Sealing surface 34, which with a in the valve body 26 in the end region facing the combustion chamber Valve seat 36 cooperates, by or after which remove first injection openings 32.
  • valve body 26 In the valve body 26 is between the injection valve member 28 and the bore 30 to the valve seat 36 towards an annular space 38, which in its end area facing away from the valve seat 36 by a radial expansion of the bore 30 in a the first Injection valve member 28 passes surrounding pressure chamber 40.
  • the first injection valve member 28 has the level of Pressure chamber 40 by reducing a cross section Pressure shoulder 42 on.
  • first injection valve member 28 At the end facing away from the combustion chamber first injection valve member 28 indirectly engages a first one biased closing spring 44 through which the first Injection valve member 28 is pressed toward the valve seat 36.
  • the first closing spring 44 is in contact with the bore 30 adjoining spring chamber 46 arranged in Valve body 26 or in the pump body 14 or in one between the valve body 26 and the pump body 14 arranged intermediate body 45 is formed.
  • the first injection valve member 28 of the Fuel injection valve 12 is as in FIGS. 1 and 2 shown hollow and in this is in a A bore formed coaxially in the injection valve member 28 second injection valve member 128 guided.
  • the second injector member 128 becomes at least one controlled second injection opening 132 in the valve body 26.
  • the at least one second injection opening 132 is in Direction of the longitudinal axis of the injection valve members 28, 128 the at least one first injection opening 32 for Combustion chamber arranged offset.
  • the second Injection valve member 128 faces the combustion chamber facing end region, for example an approximately conical one Sealing surface 134, which with a in the valve body 26 in the end region facing the combustion chamber Valve seat 136 cooperates, by or after which discharge second injection openings 132.
  • a pressure surface 142 is formed on this, at opened first injection valve member 28 of the pressure chamber 40 prevailing pressure acts.
  • the first injection valve member 28 is connected as in FIG 1 shows a protruding into the spring chamber 46 Support sleeve 48 on which the Injection valve member 28 side facing a cup-shaped Sleeve 50 supports, on which the support sleeve 48 facing away In turn, the first closing spring 44 is supported.
  • the on the other hand, the first closing spring 44 is supported on an in from the spring chamber 46 inserted spring plate 52.
  • a first control piston 54 from the diameter is graduated.
  • the first control piston 54 is with a small diameter section 54a in the spring chamber 46 arranged and protrudes with a large diameter Section 54b in an adjoining the spring chamber 46 Hole 56 in.
  • the first control piston 54 joins its section 54a through the spring plate 52.
  • the first control piston 54 is hollow and its Section 54b is tightly guided in the bore 56 and delimited in this with its annular end face 55 partially a control pressure chamber 58.
  • Injector member 128 supports a second one Control piston 154 from the through the support sleeve 48, the Sleeve 50 and the first control piston 54 into the bore 56 protrudes and there also with its end face 155 den Control pressure chamber 58 partially limited.
  • the second Spool 154 is in its end portion 54b of the first control piston 54 tightly guided.
  • the second Control piston 154 has in its sleeve 50 arranged area an enlarged in diameter Collar 152 on, between and that of the support sleeve 48th bottom of the sleeve 50 facing away from it, a second closing spring 144 is clamped. The second closing spring 144 will second injector member 128 via the second Control piston 154 acted upon in the closing direction.
  • a first electrically operated control valve 62 becomes one Connection 64 of the pump workspace 22 with a Relief chamber controlled, for example, at least indirectly the fuel tank 24 or the Pressure side of a feed pump 23 can serve through Fuel from the fuel tank 24 in the Pump work room 22 is promoted. As long as none Fuel injection is to be done through the Control valve 62 the connection 64 of the pump workspace 22nd opened with the relief chamber, so that in Pump work room 22 can not build up high pressure.
  • Control valve 62 When a Fuel injection is to take place, so by Control valve 62 of the pump work chamber 22 from the relief chamber separated so that the delivery stroke of the pump piston 18 in Pump workspace 22 can build up high pressure.
  • the Control valve 62 can be an electromagnetic actuator or have a piezo actuator.
  • the control valve 62 is For example, designed as a 2/2-way valve and between an open and a closed switch position switchable and is made by an electronic Control device 63 controlled.
  • the control pressure chamber 58 has a bore 66 Connection with the channel 60 and thus with the Pump work room 22. In the bore 66 is one Throttle point 67 arranged. The control pressure chamber 58 has also via a bore 68 a connection with a Relief space on than the at least indirectly the Fuel reservoir 24 is used. In the bore 68 is a throttle point 69 is arranged. The throttling points 67 and 69 are coordinated in their dimensioning to specifically filling the control pressure chamber 58 with Fuel from the pump workspace 22 and relief of the control pressure chamber 58 to the relief chamber 24 enable. The connection of the Steuerdruckruams 58 with the Relief chamber 24 becomes electrical by a second one operated control valve 70 controlled like the first Control valve 62 can be formed and by the Control device 63 is controlled.
  • the bore 68 through which the control pressure chamber 58 Has connection to the relief chamber 24 is in Smaller diameter than the bore 56 in the the control pressure chamber 58 is formed so that at the transition from Control pressure chamber 58 to bore 68 an annular Limitation 59 of the control pressure chamber 58 is formed.
  • the first control piston 54 points as in FIGS. 3 and 4 shown on its boundary 59 facing End face 55 has an annular elevation 53, the compared to the end face 55 a smaller width in has radial direction of the control piston 54.
  • the Survey 53 can be formed, for example, in that the end of the first control piston 54 as in FIGS. 3 and 4 has opposite bevels shown.
  • first injector member 28 a stroke in Executes opening direction 29, so is on the support sleeve 48 and the sleeve 50 also the first control piston 54 in Arrow direction 29 moves.
  • the maximum opening stroke of the first Injection valve member 28 is limited in that the first Control piston 54 with its elevation 53 at the limit 59 of the control pressure chamber 58 comes to rest.
  • Figure 3 are the control pistons 54,154 in their position in their Injection valve members 28, 128 arranged in the closed position 4 and the control pistons 54, 154 in their position in their with maximum opening stroke Injector members arranged in the open position 28, 128.
  • Both control valves 62 and 70 are operated by the electronic Control device 63 controlled.
  • the control device 63 signals about operating parameters of the Internal combustion engine, such as in particular speed, load, Temperature and other parameters such as Air temperature, air pressure and possibly other Parameters supplied.
  • the control valves 62 and 70 depending on these parameters controlled to control the fuel injection.
  • a pre-injection of a small amount of fuel becomes the second control valve 70 by the control device 63 opened so that the control pressure chamber 58 with the Relief chamber 24 is connected and the pressure in Control pressure chamber 58 drops. If the pressure in the Pump work chamber 22 and thus in the pressure chamber 40 of the Fuel injector 12 is so high that through this over the pressure shoulder 42 to the first Injection valve member 28 generated pressure force is greater than the buzzer of the force of the first closing spring 44 and the by the residual pressure prevailing in the control pressure chamber 58 the first spool 54 to the first Injection valve member 28 generated force, so that opens Fuel injector 12 by the first Injection valve member 28 with its sealing surface 34 from Valve seat 36 lifts off and the at least one first Injection opening 32 releases.
  • the through the in the pressure room 40 prevailing pressure over the pressure shoulder 142 on the second Injection valve member 128 generated compressive force is less than the sum of the by the second closing spring 144 and the via the second control piston 154 by the in Control pressure chamber 58 prevailing residual pressure on the second Injection valve member 128 force generated in the closing direction, so that the second injector member 128 in its The closed position remains.
  • On the fuel injector 12 is thus only a part with the first injection openings 32 of the entire injection cross section opened so that accordingly only a small amount of fuel is injected becomes.
  • the second Control valve 70 closed by the control device 63, so that the pressure in the control pressure chamber 58 rises again and that first injector member 28 as a result of the first Control piston 54 on this generated higher force in Closing direction is moved back to its closed position.
  • the time period for which the second control valve 70 is Pre-injection is opened is very short, so that first injection valve member 28 opens only with a partial stroke and the first control piston 54 does not have its elevation 53 at the boundary 59 of the control pressure chamber 58 to the system comes.
  • the entire end face 55 is the first Control piston 54 from the prevailing in the control pressure chamber 58 Pressurized and with the second closed Control valve 70 generates that in control pressure chamber 58 prevailing rising pressure is a force at first Control piston 54, which is sufficient to the first Injection valve member 28 against that in pressure chamber 40 prevailing pressure to move into its closed position. If the first injection valve member 28 only with a partial stroke is open, so there is also between its Sealing surface 34 and the valve seat 36 only a narrow gap, in which throttles the fuel flowing through, so that the injection valve member 28 in Opening direction 29 force is less than with maximum opening stroke of opened injection valve member 28.
  • the first Control valve 62 preferably kept closed, so that in Pump work chamber 22, a further pressure build-up takes place.
  • the second control valve 70 by the control device 63 at a certain time opened so that the control pressure chamber 58 with the Relief chamber 24 is connected and the pressure in Control pressure chamber 58 drops.
  • the first injector member 28 then open and give at least one first Injection port 32 free.
  • the first injector member 28 opens with its maximum opening stroke, so that the first control piston 54 with its elevation 53 on the Limitation 59 of the control pressure chamber 58 comes to rest.
  • the second control valve 70 is through the control device 63 closed again, so that the Pressure in the control pressure chamber 58 rises again before that second injection valve member 128 through the in the pressure chamber 40th prevailing pressure is moved in the opening direction 29.
  • the second injection valve member 128 is then by the on second control piston 154 acting high pressure in its Closed position maintained.
  • the first injector member 28 remains open with its maximum opening stroke Position, since only the part lying within the survey 53 the end face 55 of the first control piston 54 of the im Control pressure chamber 58 prevailing pressure and thus only one force in the closing direction at first Control piston 54 and thus the first injection valve member 28 results that is less than that in the pressure chamber 40 prevailing pressure in the opening direction 29 force generated.
  • the Control device 63 then the first control valve 62 opened so that the pressure in the pressure chamber 40 drops and that first injector member 28 by the force of the first Closing spring 44 and by the on the first control piston 54th generated by the pressure prevailing in the control pressure chamber 58 Power closes.
  • the amount of fuel to be injected is determined by the Control device 63 the second control valve 70 open longer held so that the second injection valve member 128 by the pressure prevailing in the pressure chamber 40 against the force the second closing spring 144 and by the im Control pressure chamber 58 prevailing residual pressure over the second Control piston 154 generated force opens and at least a second injection opening 132 opens.
  • the second Injection valve member 128 opens with time Delay after the first injector member 28 so that only the first one at the beginning of the main injection Injection valve member 28 is open. If the second Injection valve member 128 is open, so is on Fuel injector 12 the whole Injection cross section released and it becomes a larger one Amount of fuel injected.
  • the Main injection is the first control valve 62 through the Control device 63 opened so that the pressure in the pressure chamber 40 drops and the first and second injection valve members 28,128 by the closing forces acting on them Close the closing springs 44, 144 and the control piston 54, 154.
  • the second control valve 70 is thereby Control device 63 closed.
  • first Injection ports 32 and the second injection ports 132 formed injection cross sections at least approximately the same are large so that when opening only the first Injector member 28 half of the total Injection cross section is released.
  • first injection openings 32 a form larger or smaller injection cross-section than that second injection ports 132.
  • FIG. 5 shows the course of the opening stroke h for the first one Injection valve member 28 with a solid line and for that second injection valve member 128 with a broken line represented over an time t during an injection cycle.
  • I is the pilot injection and with II the Main injection called.
  • pre-injection I only opens the first one, as explained above Injector valve member 28. Opens at main injection II either only the first injection valve member 28 or with time delay also the second injector member 128.
  • the time delay when opening the second Injector valve member 128 can through the second control valve 70 can be influenced by this after opening the first injection valve member 28 with maximum opening stroke is closed again, so the second Injector valve member 128 because of the high pressure in the Control pressure chamber 58 initially remains closed, and with time delay is opened again, so that second injection valve member 128 can open.
  • shut-off valve 80 in channel 60 be arranged.
  • the shut-off valve 80 is between the Connection 64 of the pump workspace 22 with the Relief chamber 24 and the connection 66 of the Control pressure chamber 58 arranged with the channel 60.
  • the Shut-off valve 80 can be opened towards the pressure chamber 40 Check valve or as an electrically operated valve be formed by the control device 63 is controlled.
  • Pressure chamber 40 and the control pressure chamber 58 from Pump work space 22 are separated.
  • When closed Shut-off valve 80 can be in the pump work space 22 opened first control valve 62 with the relief chamber 24 connected and thus relieved while at closed second control valve 70 fuel under pressure can be stored in the pressure chamber 40 and in the control pressure chamber 58 can.
  • By opening the second control valve 70 a Pre-injection or post-injection of fuel after the main injection take place at no time the fuel injection fuel through the pump piston 18 needs to be promoted.

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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)
EP03004642A 2002-05-14 2003-03-03 Système d'injection de carburant pour un moteur à combustion interne Withdrawn EP1363015A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10221384 2002-05-14
DE10221384A DE10221384A1 (de) 2002-05-14 2002-05-14 Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine

Publications (1)

Publication Number Publication Date
EP1363015A1 true EP1363015A1 (fr) 2003-11-19

Family

ID=29265285

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03004642A Withdrawn EP1363015A1 (fr) 2002-05-14 2003-03-03 Système d'injection de carburant pour un moteur à combustion interne

Country Status (4)

Country Link
US (1) US6810857B2 (fr)
EP (1) EP1363015A1 (fr)
JP (1) JP2003328898A (fr)
DE (1) DE10221384A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005026525A1 (fr) * 2003-08-25 2005-03-24 Robert Bosch Gmbh Soupape d'injection de carburant pour moteur a combustion interne
EP1589217A1 (fr) * 2004-04-23 2005-10-26 Robert Bosch Gmbh Injecteur de carburant pour moteur à combustion interne
EP1686257A3 (fr) * 2005-01-28 2007-11-07 Cummins Inc. Injecteur de caburant à régulation du débit d'injection
EP2085604A1 (fr) * 2008-02-04 2009-08-05 Robert Bosch GmbH Injecteur de carburant

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Publication number Priority date Publication date Assignee Title
DE10122241A1 (de) * 2001-05-08 2002-12-05 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
KR20050026035A (ko) * 2002-07-29 2005-03-14 로베르트 보쉬 게엠베하 조절 가능한 니들 속도에 의해 압력이 증폭되거나 압력이증폭되지 않는 연료 분사기 및 상기 연료 분사기의 조절방법
DE10352504A1 (de) * 2003-11-11 2005-06-02 Robert Bosch Gmbh Einspritzdüse
DE10355806A1 (de) * 2003-11-28 2005-06-23 Robert Bosch Gmbh Einspritzdüse
US6928986B2 (en) * 2003-12-29 2005-08-16 Siemens Diesel Systems Technology Vdo Fuel injector with piezoelectric actuator and method of use
JP4167230B2 (ja) 2004-01-13 2008-10-15 デルファイ・テクノロジーズ・インコーポレイテッド 燃料噴射装置
DE502005010478D1 (de) * 2004-02-25 2010-12-16 Ganser Hydromag Brennstoffeinspritzventil für verbrennungskraftmaschinen
DE102004010760A1 (de) * 2004-03-05 2005-09-22 Robert Bosch Gmbh Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen mit Nadelhubdämpfung
DE102004018931A1 (de) * 2004-04-20 2005-11-17 Robert Bosch Gmbh Common-Rail-Injektor
WO2005119045A1 (fr) * 2004-06-03 2005-12-15 Siemens Aktiengesellschaft Soupape d'injection
ATE494477T1 (de) * 2005-10-25 2011-01-15 Crt Common Rail Technologies Ag Injektor für eine kraftstoffeinspritzanlage sowie kraftstoffeinspritzanlage mit einem solchen injektor
JP5043761B2 (ja) * 2008-06-18 2012-10-10 本田技研工業株式会社 燃料噴射装置
CN101457726B (zh) * 2008-11-20 2011-07-27 浙江飞亚电子有限公司 一种针阀动力喷嘴
DE102021203088A1 (de) 2021-03-29 2022-09-29 Robert Bosch Gesellschaft mit beschränkter Haftung Brennstoffeinspritzventil

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DE3824467A1 (de) * 1988-07-19 1990-01-25 Man B & W Diesel Ag Einspritzventil
DE4123721C1 (en) * 1991-07-17 1992-06-17 Steyr-Daimler-Puch Ag, Wien, At Fuel injection system with pump and nozzle units - has laterally coupled pump duct to chamber in piston bush
EP0957261A2 (fr) 1998-05-15 1999-11-17 LUCAS INDUSTRIES public limited company Système de carburant et pompe utilisable dans ce système
EP0967383A2 (fr) * 1998-06-24 1999-12-29 LUCAS INDUSTRIES public limited company Injecteur de combustible

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JPS60192872A (ja) * 1984-03-15 1985-10-01 Nippon Denso Co Ltd 蓄圧式燃料噴射弁
DE59903599D1 (de) * 1998-11-10 2003-01-09 Ganser Hydromag Ag Zuerich Brennstoffeinspritzventil für verbrennungskraftmaschinen
DE19947194A1 (de) * 1999-10-01 2001-04-05 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
EP1118765A3 (fr) * 2000-01-19 2003-11-19 CRT Common Rail Technologies AG Injecteur de combustible pour moteur à combustion interne
DE10123993A1 (de) * 2001-05-17 2002-11-21 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3824467A1 (de) * 1988-07-19 1990-01-25 Man B & W Diesel Ag Einspritzventil
DE4123721C1 (en) * 1991-07-17 1992-06-17 Steyr-Daimler-Puch Ag, Wien, At Fuel injection system with pump and nozzle units - has laterally coupled pump duct to chamber in piston bush
EP0957261A2 (fr) 1998-05-15 1999-11-17 LUCAS INDUSTRIES public limited company Système de carburant et pompe utilisable dans ce système
EP0967383A2 (fr) * 1998-06-24 1999-12-29 LUCAS INDUSTRIES public limited company Injecteur de combustible

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005026525A1 (fr) * 2003-08-25 2005-03-24 Robert Bosch Gmbh Soupape d'injection de carburant pour moteur a combustion interne
EP1589217A1 (fr) * 2004-04-23 2005-10-26 Robert Bosch Gmbh Injecteur de carburant pour moteur à combustion interne
EP1686257A3 (fr) * 2005-01-28 2007-11-07 Cummins Inc. Injecteur de caburant à régulation du débit d'injection
EP2085604A1 (fr) * 2008-02-04 2009-08-05 Robert Bosch GmbH Injecteur de carburant

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JP2003328898A (ja) 2003-11-19
DE10221384A1 (de) 2003-11-27
US20040011882A1 (en) 2004-01-22
US6810857B2 (en) 2004-11-02

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