EP1407136B1 - Soupape d'injection de carburant - Google Patents
Soupape d'injection de carburant Download PDFInfo
- Publication number
- EP1407136B1 EP1407136B1 EP02745049A EP02745049A EP1407136B1 EP 1407136 B1 EP1407136 B1 EP 1407136B1 EP 02745049 A EP02745049 A EP 02745049A EP 02745049 A EP02745049 A EP 02745049A EP 1407136 B1 EP1407136 B1 EP 1407136B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- coupler
- fuel injection
- valve
- pressure cylinder
- 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.)
- Expired - Lifetime
Links
- 239000000446 fuel Substances 0.000 title claims description 84
- 238000002347 injection Methods 0.000 title claims description 39
- 239000007924 injection Substances 0.000 title claims description 39
- 238000007789 sealing Methods 0.000 claims description 9
- 238000002485 combustion reaction Methods 0.000 claims description 7
- 230000008878 coupling Effects 0.000 claims description 3
- 238000010168 coupling process Methods 0.000 claims description 3
- 238000005859 coupling reaction Methods 0.000 claims description 3
- 230000036316 preload Effects 0.000 claims 1
- 239000012530 fluid Substances 0.000 description 7
- 230000002349 favourable effect Effects 0.000 description 4
- 230000005540 biological transmission Effects 0.000 description 3
- 238000001704 evaporation Methods 0.000 description 2
- 230000003044 adaptive effect Effects 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 230000016507 interphase Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
Images
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
-
- 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
- F02M51/00—Fuel-injection apparatus characterised by being operated electrically
- F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
- F02M51/0603—Injectors peculiar thereto with means directly operating the valve needle using piezoelectric or magnetostrictive operating means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- 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
- F02M61/167—Means for compensating clearance or thermal expansion
-
- 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
- F02M2200/16—Sealing of fuel injection apparatus not otherwise provided for
Definitions
- the invention relates to a fuel injection valve according to the preamble of the main claim.
- US 6 142 443 A discloses a hydraulically fixed coupler with a movable piston with an internal inlet bore.
- a displacement transformer for a piezoelectric actuator in which the actuator transmits a lifting force to a master cylinder, which is closed by a cylinder carrier.
- a slave piston In this master cylinder, a slave piston is guided, which also closes the master cylinder and thereby forms the hydraulic chamber.
- a spring In the hydraulic chamber, a spring is arranged, the master cylinder and the slave piston pushes apart.
- the slave piston mechanically transfers a lifting movement to, for example, a valve needle.
- DE 195 19 191 A1 discloses a hydraulic travel translating movable coupler having a bore in the pressure cylinder carrier which connects the pressure space in the coupler to the low pressure return of the injector.
- a disadvantage of this known prior art is that the hydraulic chamber can be filled only slowly. Especially during the cold start with low pressure occur long injection times, so that more hydraulic fluid escapes through the annular gap and then must be replenished in a shorter time at low pressure again. If this does not happen, the injector will lose lift per injection until it completely loses its function.
- a further disadvantage is that the hydraulic fluid can evaporate if there is no sufficiently high pressure in the hydraulic chamber.
- a gas is compressible and only builds up a correspondingly high pressure after a strong reduction in volume.
- the fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage that the moving coupler valve seat body lifts off from the Kopplerventilsitz when the moving coupler does not take the possible length as a transmission element between the actuator and the valve needle and thus for the fuel an inflow over the Zulaufbohrung to the pressure chamber releases. Since the cross-sectional area occupied by the Kopplerventlditzitz is smaller than the Quremales Stimbalsky, both the Kopplerfederelement as well as the increased pressure when operating in the coupler space closing on the Kopplerventildichtsitz.
- the Kopplerventildsitzitz is released when resetting the actuator.
- the coupler space is filled quickly until it reaches its original position again and closes the Kopplungerveldilditz.
- the fuel injection valve according to the invention that are automatically compensated by changes in temperature and by changes in the pressure of the fuel expansions of the fuel injection valve on the transmission path between the actuator and valve needle.
- the stroke of the valve needle can always be the same size.
- the Kopplerventilsch manyharmonics can be formed as a spherical surface and the corresponding Kopplerventilsitz requirements on the valve needle as a conical surface.
- the inlet bore are formed in the pressure cylinder carrier and the Coupling valve closing body integrally formed with the pressure cylinder carrier and the pressure cylinder.
- the Kopplerventilsitz preparation is formed on the valve needle and the pressure piston connected to a guide piston, which is guided in a bore in a cutting disc, which separates the fuel inlet from an actuator chamber. It is also favorable to provide a corrugated tube for sealing this actuator chamber on the guide piston.
- the stroke of the valve needle can be limited by a stop of an actuator head or alternatively by a stop of the valve needle or alternatively by a stop of the pressure piston or the pressure cylinder.
- an always the same and defined stroke of the valve needle can be achieved, regardless of expansion and expansion of a valve body of the fuel injection valve when the stroke limited by the stop is always smaller than the minimum stroke of the actuator under all operating conditions.
- FIG. 1 schematically illustrated fuel injector 1 has a valve needle 2, which is connected to a valve closing body 3 and cooperates via this valve closing body 3 with a formed in a valve body 4 valve seat surface 5 to a valve sealing seat.
- the fuel injection valve 1 is an outwardly opening fuel injection valve, which has an outwardly opening valve needle 2.
- the valve needle 2 is guided by a guide section 7, which has a spring system 8 for a valve closing spring 9, in a valve needle guide 10.
- the valve closing spring 9 is supported against a second spring system 11 on the valve body 4 and biases the valve needle 2 with a force that presses the valve closing body 3 against the valve seat surface 5.
- a groove 12 arranged in a sealing ring 13 a seal of the annular gap, not shown here between the valve body 4 and a bore, also not shown in a cylinder head of an internal combustion engine.
- a piezoelectric or magnetostrictive actuator 14 is arranged in a valve body upper part 17, which can be supplied via a bore 15 in the valve body upper part 17 and an electrical supply line 16 with a voltage.
- the actuator 14 has a greater length to a noticeable stroke when applying a voltage to the actuator 14 to achieve.
- the largest part of the length of the actuator 14 is in the Fig. 1 not shown.
- an actuator head 18 connects, which has a spring contact surface 19 to which an actuator clamping spring 20 is applied, which in turn is supported against a cutting disc 21.
- a bias voltage is applied to the actuator 14, so that upon application of a voltage to the electrical supply line 16, the stroke of the actuator 14 transmits to the actuator head 18.
- a plunger 22 is formed integrally with the actuator head 18, which transmits the stroke of the actuator 14.
- the actuator head 18 is guided through an actuator head sleeve 23 in the valve body upper part 17 and this actuator head sleeve 23 strikes after a maximum stroke h on the cutting disk 21 at. As a result, the maximum stroke h of the actuator 14 is limited.
- the actuator head tappet 22 transmits the lifting movement of the actuator 14 to a pressure piston carrier 24 into which a blind hole 25 is centrally introduced.
- the pressure piston carrier 24 is guided by a guide bore 27 which penetrates the carrier plate 21.
- the support plate 21 is sealed by a sealing ring 26 opposite the valve body upper part 17.
- a corrugated tube 28 concentrically surrounds the pressure piston carrier 24 and is fastened to the pressure piston carrier 24 with a weld seam 29.
- the corrugated tube 28 is on the other hand fixed to the support plate 21 with a weld 30.
- the pressure piston carrier 24 integrally acting as a master piston piston piston 33 is formed in a pressure cylinder 34 acting as a slave cylinder is guided.
- the printing cylinder 34 is formed integrally with a printing cylinder carrier 35.
- an inlet bore 36 is guided centrally.
- Pressure piston 33, pressure cylinder 34 and pressure cylinder carrier 35 form the hydraulic coupler 35a.
- the hydraulic coupler 35a Concentric about the pressure piston 33 and the Druckzlinder 34, the hydraulic coupler 35a has a Kopplerspiralfeder 38 between a spring stop 39 on the pressure cylinder carrier 35 and another spring stop 40 on the pressure piston carrier 24.
- the inlet bore 36 is separated from the fuel chamber 32 by a Kopplerventilsch basicallyintelligence which is formed as a hemispherical surface on the pressure cylinder carrier 35, and with a Kopplerventilsitz composition 42 which is formed as a conical surface on the guide portion 7 of the valve needle 2, to a Kopplerventldichtsitz.
- a Kopplerventildsitzitz results in a disc-shaped surface with the diameter d, which is not acted upon by the pressure of the fuel, which is located in the fuel chamber 32.
- the actuator 14 expands in the longitudinal direction of the fuel injection valve 1 and pushes the actuator head 18 with the molded on this actuator ram 22 in the direction of the valve seat 6.
- the stroke is by the stop the actuator head sleeve 23 is limited to the cutting disk 21 for a distance h.
- the movement is transferred to the pressure piston carrier 24 and the pressure piston 33.
- the fuel contained in the pressure chamber 37 is incompressible as a liquid and therefore transmits the movement further to the pressure cylinder carrier 35.
- the spring force of the coupler coil spring 38 and the force of the actuator 14 is the Coupling valve closing body 41 on the Coupler valve seat surface 42 is pressed.
- the Kopplerventildsitzitz 43 sealingly closes and it can escape fuel from the pressure chamber 37.
- the valve needle 2 opens outwardly from the valve seat 6 lifting. From the pressure chamber 37, only a gap loss amount of fuel can escape through the annular gap between the pressure piston 33 and the pressure cylinder 34 during the stroke.
- the actuator spring 20 Upon completion of the stroke of the actuator is pushed back by the actuator spring 20 and the valve needle 2 is pressed by the valve needle spring 9 in its valve seat 6. Due to the prestressed corrugated tube 28 of the pressure piston carrier 24 is held adjacent to the Aktorkopfstumbleel 22.
- the coupler valve seat face 43 now opens because the diameter of the cross-sectional area facing the coupler valve seat face 43 is increased Fuel pressure in the fuel chamber 32 is completed, is smaller than the diameter of the pressure piston 33 and the spring force of the coupler coil spring 38 is overcome. From the fuel chamber 32, pressurized fuel can now pass past the coupler valve seat 43 through the inlet bore 36 into the pressure chamber 37.
- the coupler coil spring 38 pulls the pressure piston 33 out of the pressure cylinder 34 until the coupler valve closing body 41 sits on the coupler valve seat surface 42 and the coupler valve seat 43 is again closed.
- the fuel injection valve 1 according to the invention with the described transmission path of the lifting force of the actuator 14 to the valve needle 2 thus automatically adapts to the expansions of the valve body 4 and the valve body shell 17 at pressure fluctuations of the fuel pressure. Likewise, temperature-related expansions are compensated.
- a failure of the fuel injection valve 1, z. B. can be prevented at a restart after an internal combustion engine has been turned off in the hot condition.
- the fuel chamber 32 slowly loses fuel pressure. This can lead to evaporation of fuel in the pressure chamber 37.
- the vaporized fuel in the pressure chamber 37 would be compressed as gas without building up the pressure necessary to open the valve needle 2.
- the fuel in the fuel chamber 32 is first pressurized by an external pump, not shown here, and thus the coupler valve seat 43 is opened as described above in a fuel injection valve 1 according to the invention and fuel flows through the inlet bore 36 into the pressure chamber 37. As a result, a cooling and the evaporated fuel is condensed.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
Claims (12)
- Injecteur de carburant notamment injecteur pour des systèmes d'injection de carburant dans des moteurs à combustion interne comportant un actionneur (14) piézo-électrique ou magnétostrictif, qui commande par l'intermédiaire d'un coupleur hydraulique (35a), un organe d'obturation de soupape (3) installé sur une aiguille d'injecteur (2), cet organe d'obturation de soupape coopérant avec une surface de siège de soupape (5) pour former un siège d'étanchéité (6),
l'organe de couplage (35a) comprenant un cylindre de pression (34), un support de cylindre de pression (35) relié au cylindre de pression (34) ainsi qu'un piston de pression (33) guidé dans ce cylindre de pression (34), et qui forme une chambre de pression (37) ainsi qu'un élément de ressort de couplage (38) générant une force de précontrainte entre le piston de pression (33) et le cylindre de pression (34), cette force de précontrainte entraînant le piston de pression (33) pour le sortir du cylindre de pression (34),
caractérisé en ce qu'
un organe d'obturation de soupape de couplage (41), mobile et une surface de siège de soupape de couplage (42), mobile, coopèrent par l'intermédiaire de la force de ressort développée par l'élément de ressort de couplage (38) pour former un siège d'étanchéité de soupape de couplage (43), et
la chambre de pression (37) du coupleur mobile (35a) est reliée par un perçage d'alimentation (36) dans le piston de pression (33), mobile ou dans le support de cylindre de pression (35 et par le siège d'étanchéité de soupape de couplage (43) avec une arrivée de carburant (44), et
la surface de la section prise par le siège d'étanchéité (43) de la soupape de couplage est inférieure à la surface de la section du piston de pression (33). - Injecteur de carburant selon la revendication 1,
caractérisé en ce que
la surface de siège de soupape de couplage (42) est formée sur l'aiguille d'injecteur (2). - Injecteur de carburant selon la revendication 2,
caractérisé en ce que
la surface de siège de soupape de couplage (42) de l'aiguille d'injecteur (2) est une surface conique. - Injecteur de carburant selon la revendication 3,
caractérisé en ce que
l'organe d'obturation de soupape de couplage (41) a une forme de surface sphérique. - Injecteur de carburant selon l'une des revendications 1 à 4,
caractérisé en ce que
le perçage d'alimentation (36) est réalisé dans le support de cylindre de pression (35). - Injecteur de carburant selon la revendication 5,
caractérisé en ce que
l'organe d'obturation de soupape de couplage (41) est formé en une seule pièce avec le support de cylindre de pression (35) et le cylindre de pression (34). - Injecteur de carburant selon la revendication 5 ou 6,
caractérisé en ce que
la surface de siège de soupape de couplage (43) est formée sur l'aiguille d'injecteur (2) et le piston de pression (33) est relié à un piston de guidage (24) guidé dans un perçage d'un disque de séparation (21). - Injecteur de carburant selon la revendication 7,
caractérisé en ce qu'
un tube ondulé (28) est fixé au piston de guidage (24) pour assurer l'étanchéité d'une chambre d'actionneur (31). - Injecteur de carburant selon l'une des revendications 1 à 8,
caractérisé en ce que
l'élément de ressort de couplage (38) est constitué par un ressort hélicoïdal (38) installé concentriquement autour du piston de pression (38) et du cylindre de pression (34). - Injecteur de carburant selon l'une des revendications 1 à 9,
caractérisé en ce qu'
une butée de tête d'actionneur (18) limite la course maximale (h) de l'actionneur (14). - Injecteur de carburant selon l'une des revendications 1 à 9,
caractérisé en ce qu'
une butée de l'aiguille d'injecteur (2) limite la course maximale de l'aiguille d'injecteur (2). - Injecteur de carburant selon l'une des revendications 1 à 9,
caractérisé en ce que
le piston de pression (33) ou le cylindre de pression (34) sont limités dans leur course par une butée.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10133265 | 2001-07-09 | ||
DE10133265A DE10133265A1 (de) | 2001-07-09 | 2001-07-09 | Brennstoffeinspritzventil |
PCT/DE2002/001640 WO2003006820A1 (fr) | 2001-07-09 | 2002-05-07 | Soupape d'injection de carburant |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1407136A1 EP1407136A1 (fr) | 2004-04-14 |
EP1407136B1 true EP1407136B1 (fr) | 2008-07-02 |
Family
ID=7691147
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP02745049A Expired - Lifetime EP1407136B1 (fr) | 2001-07-09 | 2002-05-07 | Soupape d'injection de carburant |
Country Status (6)
Country | Link |
---|---|
US (1) | US6883725B2 (fr) |
EP (1) | EP1407136B1 (fr) |
JP (1) | JP4116542B2 (fr) |
KR (1) | KR100853645B1 (fr) |
DE (2) | DE10133265A1 (fr) |
WO (1) | WO2003006820A1 (fr) |
Families Citing this family (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10310499A1 (de) * | 2003-03-11 | 2004-09-23 | Robert Bosch Gmbh | Brennstoffeinspritzventil |
DE10310790A1 (de) | 2003-03-12 | 2004-09-23 | Robert Bosch Gmbh | Brennstoffeinspritzventil |
DE10310788A1 (de) * | 2003-03-12 | 2004-09-23 | Robert Bosch Gmbh | Brennstoffeinspritzventil und Verfahren zu dessen Montage |
DE10341810B4 (de) * | 2003-09-10 | 2016-04-07 | Robert Bosch Gmbh | Brennstoffeinspritzventil und Verfahren zum Betrieb eines Brennstoffeinspritzventils |
DE10344880A1 (de) * | 2003-09-26 | 2005-04-14 | Robert Bosch Gmbh | Brennstoffeinspritzventil |
DE10353639A1 (de) * | 2003-11-17 | 2005-06-16 | Robert Bosch Gmbh | Brennstoffeinspritzventil |
DE10353641B4 (de) * | 2003-11-17 | 2016-12-01 | Robert Bosch Gmbh | Brennstoffeinspritzventil |
DE102004009460A1 (de) * | 2004-02-27 | 2005-09-15 | Robert Bosch Gmbh | Ventil |
DE102004010183A1 (de) * | 2004-03-02 | 2005-09-29 | Siemens Ag | Einspritzventil |
DE102005025952B4 (de) * | 2005-06-06 | 2009-01-29 | Continental Automotive Gmbh | Verfahren zum Herstellen eines Ventils |
US7665445B2 (en) * | 2008-04-18 | 2010-02-23 | Caterpillar Inc. | Motion coupler for a piezoelectric actuator |
DE102008042850A1 (de) * | 2008-10-15 | 2010-04-22 | Robert Bosch Gmbh | Einspritzvorrichtung |
US8201543B2 (en) * | 2009-05-14 | 2012-06-19 | Cummins Intellectual Properties, Inc. | Piezoelectric direct acting fuel injector with hydraulic link |
DE102013219225A1 (de) * | 2013-09-25 | 2015-03-26 | Continental Automotive Gmbh | Piezo-Injektor zur Kraftstoff-Direkteinspritzung |
US10484598B2 (en) * | 2015-08-20 | 2019-11-19 | Sony Corporation | System and method for controlling capture of images |
DE102015219912B3 (de) * | 2015-10-14 | 2017-04-06 | Continental Automotive Gmbh | Piezo-Injektor zur Kraftstoffeinspritzung |
Family Cites Families (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
ATE192263T1 (de) * | 1990-09-25 | 2000-05-15 | Siemens Ag | Anordnung für einen in hubrichtung wirkenden adaptiven, mechanischen toleranzausgleich für den wegtransformator eines piezoelektrischen aktors |
DE19519191C2 (de) * | 1995-05-24 | 1997-04-10 | Siemens Ag | Einspritzventil |
DE19743640A1 (de) * | 1997-10-02 | 1999-04-08 | Bosch Gmbh Robert | Ventil zum Steuern von Flüssigkeiten |
DE19743669A1 (de) * | 1997-10-02 | 1999-04-08 | Bosch Gmbh Robert | Ventil zum Steuern von Flüssigkeiten |
DE19746143A1 (de) | 1997-10-18 | 1999-04-22 | Bosch Gmbh Robert | Ventil zum Steuern von Flüssigkeiten |
GB9725804D0 (en) * | 1997-12-06 | 1998-02-04 | Lucas Ind Plc | Fuel injector |
DE19817320C1 (de) * | 1998-04-18 | 1999-11-11 | Daimler Chrysler Ag | Einspritzventil für Kraftstoffeinspritzsysteme |
DE19946732B4 (de) * | 1999-09-29 | 2004-07-15 | Siemens Ag | Vorrichtung zum Übertragen einer Auslenkung eines Aktors auf ein Stellglied und Kraftstoffinjektor mit einer solchen Vorrichtung |
DE19950760A1 (de) * | 1999-10-21 | 2001-04-26 | Bosch Gmbh Robert | Brennstoffeinspritzventil |
DE19954802A1 (de) * | 1999-11-13 | 2001-05-17 | Bosch Gmbh Robert | Brennstoffeinspritzventil |
DE19958704C2 (de) * | 1999-12-06 | 2002-10-02 | Siemens Ag | Vorrichtung zum Übertragen einer Aktorbewegung und Fluiddosierer mit einer solchen Vorrichtung |
LU90684B1 (en) * | 2000-11-28 | 2002-05-29 | Delphi Tech Inc | Fuel injector with piezoelectric actuator |
-
2001
- 2001-07-09 DE DE10133265A patent/DE10133265A1/de not_active Withdrawn
-
2002
- 2002-05-07 DE DE50212447T patent/DE50212447D1/de not_active Expired - Lifetime
- 2002-05-07 EP EP02745049A patent/EP1407136B1/fr not_active Expired - Lifetime
- 2002-05-07 WO PCT/DE2002/001640 patent/WO2003006820A1/fr active IP Right Grant
- 2002-05-07 JP JP2003512553A patent/JP4116542B2/ja not_active Expired - Fee Related
- 2002-05-07 US US10/363,961 patent/US6883725B2/en not_active Expired - Fee Related
- 2002-05-07 KR KR1020037003392A patent/KR100853645B1/ko not_active IP Right Cessation
Also Published As
Publication number | Publication date |
---|---|
US6883725B2 (en) | 2005-04-26 |
KR20030036762A (ko) | 2003-05-09 |
JP4116542B2 (ja) | 2008-07-09 |
DE50212447D1 (de) | 2008-08-14 |
US20040011892A1 (en) | 2004-01-22 |
JP2004521271A (ja) | 2004-07-15 |
KR100853645B1 (ko) | 2008-08-25 |
WO2003006820A1 (fr) | 2003-01-23 |
DE10133265A1 (de) | 2003-01-23 |
EP1407136A1 (fr) | 2004-04-14 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP1407136B1 (fr) | Soupape d'injection de carburant | |
EP1434937B1 (fr) | Soupape d'injection de carburant | |
DE69708396T2 (de) | Piezoelektrisch gesteuertes Einspritzventil mit hydraulischer Vergrösserung des Hubs | |
EP1423600B1 (fr) | Soupape d'injection de carburant | |
EP2052148B1 (fr) | Injecteur de carburant avec commande directe du pointeau et servosoupape d'assistance | |
EP1454053B1 (fr) | Soupape d'injection de carburant | |
DE19936668A1 (de) | Common-Rail-Injektor | |
EP1421271B1 (fr) | Soupape d'injection de carburant | |
EP1144844B1 (fr) | Soupape d'injection de carburant | |
EP1378657B1 (fr) | Injecteur de carburant | |
EP1472453B1 (fr) | Soupape d'injection de carburant | |
EP2462335A1 (fr) | Dispositif pour l'injection à haute pression de carburant | |
EP1601868B1 (fr) | Soupape d'injection de carburant | |
EP1538331B1 (fr) | Soupape d'injection de carburant | |
DE10213858A1 (de) | Brennstoffeinspritzventil | |
EP1457662B1 (fr) | Injector de carburant | |
EP1714026B1 (fr) | Soupape d'injection de carburant | |
EP1488096B1 (fr) | Soupape d'injection de carburant | |
EP1519034B1 (fr) | Soupape d'injection de carburant | |
EP1406006B1 (fr) | Soupape d'injection de carburant | |
DE10123526A1 (de) | Common-Rail-Injektor | |
EP1825137A1 (fr) | Injecteur de carburant | |
WO2006056522A1 (fr) | Injecteur de carburant | |
EP1450034B1 (fr) | Injecteur de carburant | |
EP1891322A1 (fr) | Injecteur common rail |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
17P | Request for examination filed |
Effective date: 20040209 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): DE FR GB IT |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D Free format text: NOT ENGLISH |
|
REF | Corresponds to: |
Ref document number: 50212447 Country of ref document: DE Date of ref document: 20080814 Kind code of ref document: P |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
26N | No opposition filed |
Effective date: 20090403 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: GB Payment date: 20100324 Year of fee payment: 9 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20100608 Year of fee payment: 9 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: IT Payment date: 20100527 Year of fee payment: 9 |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20110507 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST Effective date: 20120131 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20110507 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20110531 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20110507 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20140724 Year of fee payment: 13 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R119 Ref document number: 50212447 Country of ref document: DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20151201 |