EP1171708A1 - Buse d'injection - Google Patents

Buse d'injection

Info

Publication number
EP1171708A1
EP1171708A1 EP01913560A EP01913560A EP1171708A1 EP 1171708 A1 EP1171708 A1 EP 1171708A1 EP 01913560 A EP01913560 A EP 01913560A EP 01913560 A EP01913560 A EP 01913560A EP 1171708 A1 EP1171708 A1 EP 1171708A1
Authority
EP
European Patent Office
Prior art keywords
valve
injection nozzle
nozzle according
injection
piston
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
EP01913560A
Other languages
German (de)
English (en)
Other versions
EP1171708B1 (fr
Inventor
Detlev Potz
Gerhard Mack
Achim Brenk
Wolfgang Klenk
Thomas Kuegler
Roland Bleher
Uwe Gordon
Manfred Mack
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 DE10100512A external-priority patent/DE10100512A1/de
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1171708A1 publication Critical patent/EP1171708A1/fr
Application granted granted Critical
Publication of EP1171708B1 publication Critical patent/EP1171708B1/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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/042—The valves being provided with fuel passages
    • F02M61/045—The valves being provided with fuel 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • 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
    • 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
    • F02M47/025—Hydraulically 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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/06—Other fuel injectors peculiar thereto
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/042—The valves being provided with fuel passages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/08—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series the valves opening in direction of fuel flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/161—Means for adjusting injection-valve lift
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • F02M61/205—Means specially adapted for varying the spring tension or assisting the spring force to close the injection-valve, e.g. with damping of valve lift

Definitions

  • the invention relates to an injection nozzle which is provided with a nozzle body, a nozzle needle which can be displaced therein and two groups of nozzle holes. Depending on the size of the opening stroke of the nozzle needle, either only one group of the nozzle holes or both groups of the nozzle holes are used for the injection In this way, different injection cross sections can be used, so that the fuel injection can be better adapted to the respective operating conditions of the internal combustion engine supplied by the injection system
  • the opening stroke of the nozzle needle must be controlled as precisely as possible.
  • One way of controlling the opening stroke is to cause the opening and closing of the nozzle needle directly by a piezo actuator Almost any intermediate position within the needle stroke can be approached and held.
  • Another possibility for controlling the opening stroke is then to control the fuel pressure causing the opening of the nozzle needle so that the desired opening stroke occurs
  • the object of the invention is then to create a fuel injection nozzle in which the opening stroke of the nozzle needle can be limited to a desired value with little effort and high reliability
  • the invention then furthermore provides a fuel injection nozzle in which the spray cross section can be selected independently of all other parameters
  • An injection nozzle with the features of claim 1 has the advantage that the opening stroke of the nozzle needle can be limited in the desired manner with little effort. If only a small opening stroke is desired, the control valve is closed so that the fluid present in the stop chamber flows out The control valve controlling the exit of the stop chamber can be actuated with low energy, since it is not acted upon directly by the high pressure which causes the opening of the nozzle needle. Furthermore, the control valve can be actuated during the pauses in the injection of the injection nozzle, i.e. between two successive injection cycles, so that the switching operations take place in phases with low pressurization and the switching phases do not have to meet high requirements with regard to the point in time.
  • the opening and closing of the control valve between two injection points Before a nozzle needle stroke the size of the opening stroke should be determined.
  • the opening stroke had to be interrupted at a certain point in time, which is why high demands had to be made on the timing precision of the switching process
  • FIG. 3 is an enlarged sectional view of the control valve used in the injection nozzles shown in Figures 1 and 2
  • FIG. 3a shows, in an enlarged sectional view, an embodiment of the control valve shown in FIG. 3,
  • FIG. 5 is a schematic view of a hydraulic circuit as can be used in the control valve of Figure 3, and
  • FIG. 6 shows a schematic view of the hydraulic circuit corresponding to the variant of the control valve from FIG. 4,
  • FIG. 7a shows an injection nozzle according to a first variant of the second embodiment
  • FIG. 7c schematically, on an enlarged scale, a section of a variant of the control valve shown in FIG. 7b,
  • FIG. 7d shows the detail d from FIG. 7c, again on an enlarged scale
  • FIG. 7e schematically, on an enlarged scale, a section of a further variant of the control valve shown in FIG. 7b, 7f shows the detail f from FIG. 7e, again on an enlarged scale;
  • FIG. 7g schematically, on an enlarged scale, a section of a further variant of the control valve shown in FIG. 7b;
  • FIG. 7h shows the detail h from FIG. 7g on an enlarged scale
  • FIG. 8a shows an injection nozzle according to a second variant of the second embodiment
  • FIG. 1 shows an injection nozzle which has a nozzle body 10. This is provided at its combustion chamber end with two groups of spray holes 12, 14 through which fuel can be injected, which is supplied via a supply bore 16 and a pressure chamber 18.
  • a nozzle needle 20 is arranged displaceably in the nozzle body 10. This is acted upon by a return spring 22 in a position in which the spray holes 12, 14 are closed.
  • the nozzle needle 20 can be shifted upwards with respect to the action of the compression spring 22 with respect to FIG. 1, so that depending on the size of this opening stroke, either only the spray holes 14 or also the spray holes 12 are released become. Since the nozzle needle 20 moves into the interior of the nozzle body 10 to open the spray holes, this type of injection nozzle is referred to as the internal opening injection nozzle.
  • the nozzle needle 20 is provided with a piston 24 which is slidably arranged in a stop chamber 25 which is formed in the nozzle body 10.
  • the term "piston” is understood here to mean any suitable design, which at A stroke of the opening of the nozzle needle can cause a volume shift of a fluid, which in turn can be influenced for the purposes described below
  • the piston 24 divides the stop chamber 26 into two sections, the section of the stop chamber 26 facing away from the spray holes with respect to the piston being provided with an outlet 28.
  • a stop plate 29 is arranged between the piston 24 and the nozzle needle 20, which plate has the maximum opening stroke the nozzle needle is limited
  • the outlet 28 leads to a valve chamber 30 (see also FIG. 3) of a control valve 31.
  • a valve ball 32 is arranged in the valve chamber and is acted upon by a valve spring 34 against a valve seat 36
  • an actuating part which consists of an actuating piston 38 and an extension 40, engages on the actuating piston 38.
  • the actuating piston 38 is arranged in an actuating chamber 42, the portion of which facing away from the valve chamber 30 is connected to a control line 44 and the section facing the valve chamber 30 is connected to a return line 46.
  • the return line 46 leads into a leakage collecting space 48 in the nozzle body 10.
  • a leakage removal line 49 is also connected to the leakage collecting space 48, which is between the stop plate 29 and the piston 24 mouths
  • the injection nozzle described works in the following manner. Before the start of injection, it is determined as a function of external parameters whether a complete opening stroke of the nozzle needle is required so that two groups of spray holes 12 14 are opened, or whether only a partial opening stroke is required, so that only the spray holes 14 are released.
  • the control piston 44 is actuated by applying an appropriate pressure to the control line 44, for example a fuel pressure displaced in the direction of the valve chamber 30, so that the valve ball 32 is raised against the action of the valve spring 34 by means of the extension 40 from the valve seat 36.
  • an appropriate pressure for example a fuel pressure displaced in the direction of the valve chamber 30, so that the valve ball 32 is raised against the action of the valve spring 34 by means of the extension 40 from the valve seat 36.
  • the nozzle needle 20 is opened by applying a suitable fuel pressure to the supply bore 16, the fluid present in the stop chamber 26 above the piston 24 can escape past the valve ball 32 from the stop chamber 26.
  • the nozzle needle 20 can be fully opened because the piston 24 can move almost freely in the stop chamber 26, the maximum opening stroke being predetermined by the stop plate 29
  • the fluid contained in the stop chamber 26 above the piston 24 and in the valve chamber 30 acts as a hydraulic spring, which only opens to a limited extent Jet needle enables the rigidity of this hydraulic spring is adjusted so that the desired partial opening stroke is achieved, in which only the group of spray holes 14 is released
  • FIG. 5 shows how the control valves of all injection nozzles of an injection system can be switched together.
  • the control lines are controlled jointly by an actuator 50, which can connect the control lines either to a pre-supply line 52 or to a leakage collecting space if the control lines 44 are connected to the pre-supply line, the control pistons of the individual control valves are pressurized with fuel under pre-pressure. This leads to the control valve being opened, so that the outlet 28 of the stop chamber 26 is connected to the leakage collecting space is and a complete opening of the nozzle needles of the injection nozzles is possible. On the other hand, if the control lines 44 are connected to the leakage collecting space, the control valves 31 are closed, so that the opening stroke of the nozzle needles is limited
  • a special feature of this stroke limitation is that the opening and closing of the control valve takes place during the injection breaks and thus in the unloaded state of the valve, the forces for actuating the control valve are therefore very small.
  • the close proximity of the control valve to the stop chamber results in a small volume and thus a rigid characteristic curve of the hydraulic spring formed by the enclosed volume. Since the control valve can be actuated with fuel that does not have to be under injection pressure, but only under low pressure, for example pre-pressure, there is a low energy requirement and a simplified structure since there are no high-pressure lines Furthermore, there are no problems with pressure vibrations.
  • the low pressure can also be provided by a separate supply system or by a leakage current from the high pressure system
  • the injection nozzle according to the second embodiment is one externally opening injection nozzle, that is to say an injection nozzle in which the nozzle needle 20 is displaced outwardly towards the combustion chamber.
  • the outlet 28 is arranged in the section of the impact chamber 26 which, with respect to the piston 24, faces the spray holes
  • FIG. 4 shows a variant of the control valve shown in FIG. 3.
  • a piezo actuator 39 is used here, which together men with the extension forms the actuating part for the valve ball 32.
  • the piezo actuator 39 can move the extension 40 towards the valve spring 34 directly by length change so that the valve ball! 32 is lifted off the valve seat 36; instead of the control line 44, cables (not shown) are used to apply the necessary voltage to the piezo actuator.
  • control valve 31 is shown schematically according to the variant of Figure 4.
  • the piezo actuator 39 can open or close the connection of the outlet 28 to the return line 46 by actuating the valve ball 32, in order in this way to achieve a variable stroke of the nozzle needle 20 of the injection nozzle.
  • FIGS. 7a and 7b show a first variant of the second embodiment, that is to say an injection nozzle that opens outwards.
  • the same reference numerals are used and reference is made to the above explanations.
  • a second valve seat 37 is used, which is the first valve seat on the other side of the valve cone 32 '. opposite.
  • the control valve When the actuating piston 38 is subjected to low pressure, which is preferably less than 10 bar, the control valve is opened and the valve cone is lifted from the first valve seat and brought into contact with the second valve seat 37. As a result, the connection from the stop chamber via its outlet 28 to the return line is opened, so that the amount of fluid displaced by the piston 24 during the opening stroke of the nozzle needle can flow out of the stop chamber 26.
  • the second valve seat is used to prevent, in the event of a possible build-up of pressure in the control valve, that a closing force acts on the valve cone, which acts against the first valve seat and the control valve closes.
  • Such a build-up of pressure could be caused by the flow resistance acting upon a fluid pressure flow when the nozzle needle was opened During a pressure build-up, a closing force was generated, which is determined on the one hand by the pressure difference between the pressure acting on the actuating piston and the pressure on the side of the valve cone facing away from the actuating piston and on the other hand by the cross-sectional area of the actuating piston if the valve cone on the second valve seat is present, the area of the valve cone relevant for the closing force is decoupled from the pressure in the control valve, so that this area is ineffective when the pressure in the control valve increases counterpart an opening force, which supports the force provided by the control piston and presses the valve cone even more firmly against the second valve seat (self-holding function) .Therefore, it is not necessary to ensure that the low pressure acting on the control piston is able to open the valve cone in all operating conditions Hold position
  • FIGS. 7c and 7d show a variant of the control valve shown in FIG. 7b.
  • the valve cone 32 ' has a valve surface 60 assigned to the valve seat 36, which is shaped as a spherical section with a radius R.
  • the radius R is selected to be comparatively large Diameter of the valve seat of 2 mm, the radius R is of the order of 3 mm.
  • the valve seat is designed such that the cone it forms has an opening angle W1 of 70 ° with respect to the central axis of the valve cone
  • the extension 40 of the valve cone 32 ' is provided with a projection 62 which bears in the guide bore 64 for the valve cone 32'.
  • FIGS. 7e and 7f show a further variant of the control valve shown in FIG. 7b.
  • the valve cone 32 has a valve surface 60 assigned to the valve seat 36, which here is formed from two truncated cone surfaces 66, 68.
  • the valve seat is designed such that the cone formed by it has an opening angle W1 of 70 ° with respect to the central axis of the valve cone.
  • the two truncated cone surfaces 66 and 68 form an angle W2 or W3 with the central axis of the cone, which is of the order of 80 ° or 45 °
  • the double-cone valve surface leads to a pure line contact and thus to a high surface pressure, which has a positive effect on the sealing effect.
  • the double-cone valve surface can be manufactured better and more reproducibly in comparison to the ball valve surface, which in turn increases the reliability of the sealing effect and also leads to one Cost reduction leads
  • FIGS. 7g and 7h show yet another variant of the control valve shown in FIG. 7b.
  • the valve cone 32 has no extension here, so that no double guide is formed for the valve cone.
  • the valve surface 60 of the valve cone exists 32 'from two truncated cone surfaces 66, 68.
  • the opening angle W1 of the valve seat enclosed with the central axis here is 29.5 °, while the angles W2 and W3 of the truncated cone surfaces 66, 68 of the valve surface are 60 30 5 ° and 22.5 °, respectively
  • FIGS. 8a and 8b show a second variant of the second embodiment. To the extent that components are used in this variant that are known from the previous figures, the same reference numerals are used and reference is made to the above explanations
  • valve ball 32 is used here, which can be lifted from the actuating piston 38 via the extension 40 from the first valve seat 36 and can be pressed against the second valve seat 37
  • valve ball 32 which is movable relative to the extension 40, enables automatic tolerance compensation between the guide for the actuating piston and the valve seats

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 buse d'injection d'un système d'injection de carburant. La course d'ouverture de l'aiguille doit être sélectivement limitée pour permettre l'utilisation de différentes sections d'injection. A cet effet, la buse d'injection comprend un corps (10), une aiguille (20) mobile dans ce corps, deux groupes de trous (12, 14) pouvant être libérés en fonction d'une course d'ouverture de l'aiguille, un piston (24) relié à l'aiguille, une chambre de butée (26) placée dans le piston et dotée d'une sortie (28), et une valve de commande (31) pouvant ouvrir et fermer la sortie de la chambre de butée, ce qui permet de limiter la course du piston dans la chambre de butée et donc de limiter sélectivement la course d'ouverture de l'aiguille.
EP01913560A 2000-02-07 2001-02-02 Buse d'injection Expired - Lifetime EP1171708B1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE10005373 2000-02-07
DE10005373 2000-02-07
DE10100512A DE10100512A1 (de) 2000-02-07 2001-01-08 Einspritzdüse
DE10100512 2001-01-08
PCT/DE2001/000394 WO2001059293A1 (fr) 2000-02-07 2001-02-02 Buse d'injection

Publications (2)

Publication Number Publication Date
EP1171708A1 true EP1171708A1 (fr) 2002-01-16
EP1171708B1 EP1171708B1 (fr) 2005-09-14

Family

ID=26004230

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01913560A Expired - Lifetime EP1171708B1 (fr) 2000-02-07 2001-02-02 Buse d'injection

Country Status (6)

Country Link
US (1) US6691935B1 (fr)
EP (1) EP1171708B1 (fr)
JP (1) JP2003522882A (fr)
CZ (1) CZ296968B6 (fr)
DE (1) DE50107401D1 (fr)
WO (1) WO2001059293A1 (fr)

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Publication number Priority date Publication date Assignee Title
DE102004061800A1 (de) * 2004-12-22 2006-07-06 Robert Bosch Gmbh Injektor eines Kraftstoffeinspritzsystems einer Brennkraftmaschine
JP4412241B2 (ja) * 2005-06-15 2010-02-10 株式会社デンソー 燃料噴射弁
DE102006026877A1 (de) * 2006-06-09 2007-12-13 Robert Bosch Gmbh Kraftstoff-Einspritzvorrichtung für eine Brennkraftmaschine
CN101558231B (zh) 2006-12-15 2012-01-04 曼柴油机涡轮机欧洲股份公司曼柴油机涡轮机德国分公司 内燃机用的燃料喷射器
WO2008071187A1 (fr) * 2006-12-15 2008-06-19 Man Diesel A/S Injecteur de carburant conçu pour un moteur thermique
EP2239451B1 (fr) * 2009-03-30 2011-09-07 Wärtsilä Switzerland Ltd. Injecteur de carburant pour moteurs à combustion interne
KR101328757B1 (ko) * 2009-10-28 2013-11-13 현대중공업 주식회사 디젤 엔진용 2단 연료 분사밸브
DE102010063379B4 (de) * 2010-12-17 2017-04-06 Robert Bosch Gmbh Expansionsmaschine und Verfahren zur Abwärmenutzung von Verbrennungskraftmaschinen
DK178656B1 (en) * 2015-03-20 2016-10-17 Man Diesel & Turbo Filial Af Man Diesel & Turbo Se Tyskland Fuel valve for injecting a low flashpoint fuel into a combustion chamber of a large self-igniting turbocharged two-stroke internal combustion engine
KR101638815B1 (ko) * 2016-01-07 2016-07-25 한빛정공(주) 4 행정용 인젝션 밸브
US10544771B2 (en) * 2017-06-14 2020-01-28 Caterpillar Inc. Fuel injector body with counterbore insert

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Publication number Priority date Publication date Assignee Title
US4640252A (en) 1984-01-28 1987-02-03 Mazda Motor Corporation Fuel injection system for diesel engine
AT407428B (de) * 1989-04-12 2001-03-26 Avl Verbrennungskraft Messtech Hydraulisch betätigbares ventil mit steuerbarem hub
DE19504849A1 (de) * 1995-02-15 1996-08-22 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen
US5682858A (en) * 1996-10-22 1997-11-04 Caterpillar Inc. Hydraulically-actuated fuel injector with pressure spike relief valve
JPH10281038A (ja) * 1997-04-01 1998-10-20 Denso Corp 燃料噴射弁
DE19739905A1 (de) * 1997-09-11 1999-03-18 Bosch Gmbh Robert Kraftstoffeinspritzventil

Non-Patent Citations (1)

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Title
See references of WO0159293A1 *

Also Published As

Publication number Publication date
CZ20013596A3 (cs) 2003-02-12
WO2001059293A1 (fr) 2001-08-16
DE50107401D1 (de) 2005-10-20
CZ296968B6 (cs) 2006-08-16
EP1171708B1 (fr) 2005-09-14
US6691935B1 (en) 2004-02-17
JP2003522882A (ja) 2003-07-29

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