EP1066466A1 - High-pressure piston cylinder unit - Google Patents
High-pressure piston cylinder unitInfo
- Publication number
- EP1066466A1 EP1066466A1 EP99915701A EP99915701A EP1066466A1 EP 1066466 A1 EP1066466 A1 EP 1066466A1 EP 99915701 A EP99915701 A EP 99915701A EP 99915701 A EP99915701 A EP 99915701A EP 1066466 A1 EP1066466 A1 EP 1066466A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- grooves
- unit according
- piston
- guide surface
- pressure unit
- 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
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
- 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
- F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
-
- 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
- F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
- F02M59/442—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston means preventing fuel leakage around pump plunger, e.g. fluid barriers
-
- 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
- F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
- F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for 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
- 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
Definitions
- the invention relates to a high-pressure piston-cylinder unit, in particular an injection pump or an injection valve for an internal combustion engine, in particular for high numbers of strokes, as presupposed in the preamble of claim 1.
- the piston guided in the cylinder bore either serves to deliver the fuel to be injected into the combustion chamber of the internal combustion engine, as in the case of an injection pump, or in the case of an injection valve to open the injection valve under the action of the fuel to be injected under high pressure, typically by the Piston lifts a nozzle needle coupled to it or made in one piece with it from the valve seat of a needle valve and thus releases an injection cross section for injecting the fuel into the combustion chamber of the internal combustion engine.
- the piston serving to actuate the injection valve of a common rail fuel injector which is typically coupled to the valve needle of the injection valve or embodied in one piece with the material, is permanently exposed to the high fuel pressure
- the nozzle needle guide to the nozzle needle seat or of the piston in the cylinder bore has a permanent leakage flow that is asymmetrical over the piston circumference.
- there are high radial forces which increase the deaxing and which are present during the entire lifting phase, in particular even at the beginning of the lifting phase. These radial forces can lead to starting or rubbing and excessive wear of the nozzle needle in the nozzle needle guide or the piston in the cylinder bore.
- valve needle is formed in two parts by a hollow needle and a valve needle guided in an inner bore of the hollow needle.
- the hollow needle has in the area of its tip a number of grooves running in the circumferential direction, which in the longitudinal direction of the valve needle by a distance of approximately the order of magnitude Diameter of the valve needle are spaced and have a width and depth that correspond to about a tenth of the valve needle diameter.
- Fuel injection pumps for large diesel engines are known to prevent “seizing" of the piston.
- EP 0 565 742 A1 discloses methods for the fine machining of workpiece surfaces, in particular walls of the bores in the cylinder of an internal combustion engine, in which grooves are produced in the surface by beam treatment, in particular by means of a laser, according to a predetermined pattern, which serve as a lubricant reservoir should.
- EP 0419 999 B1 discloses a method for machining surfaces which are highly stressed by friction in internal combustion engines, in particular the cylinder running surfaces of piston engines, in which the surface is honed and additionally subjected to laser beam treatment, the laser treatment for evaporation of outstanding roughness peaks or scaling serves to achieve a smoother surface.
- the object of the invention is to provide a high-pressure piston-cylinder unit, in particular for an injection pump or an injection valve for an internal combustion engine, in which there is less risk of wear of a piston guided in a cylinder bore due to deaxing.
- the invention is also intended to provide a method for producing such a high-pressure unit. This object is achieved by the high-pressure piston-cylinder unit specified in the claims or by the method for producing such specified in the claims, the respective advantageous embodiments being specified in the subclaims.
- the invention provides a high-pressure piston-cylinder unit, in particular an injection pump or an injection valve for an internal combustion engine, in particular for a high number of strokes, in which a piston guided in a cylinder bore is exposed to a high pressure and thus a high pressure difference on one side, according to the invention At least in a part of the guide surface of the piston, fine grooves running at a short distance from one another are formed.
- An advantage of the guide surface of the piston designed according to the invention is that the grooves provide a hydraulic pressure equalization on the circumference of the guide and thus prevent the piston from resting on one side in the cylinder bore or at least reduce the contact forces.
- a further advantage is that the leakage flow is reduced after the piston is centered in the longitudinal direction of the guide surface of the piston, and the hydraulic efficiency of the unit is thus improved.
- a reduction in the leakage flow is also achieved solely because the grooves running transversely to the direction of the leakage flow act like a labyrinth seal.
- a further advantage can be seen that the fluid present in the grooves wets the contact surfaces, whereby a lubrication effect is achieved.
- the grooves formed in the guide surface advantageously have a width b of between 5 and 100 ⁇ m, preferably between 10 and 40 ⁇ m.
- the depth t of the grooves is advantageously between 3 to 50 ⁇ m, preferably between 10 to 30 ⁇ m.
- the distance a of the grooves is advantageously between 0.05 to 1 mm, preferably between 0.1 to 0.5 mm, preferably between 0.1 to 0.3 mm.
- the width b of a groove essentially corresponds to its depth t.
- the ratio of the depth t of the groove to the nominal diameter D of the guide surface is between 1/200 and 1/1000.
- the grooves are designed to run in the circumferential direction of the guide surface.
- the grooves can be formed with a distance a varying in the longitudinal direction of the guide surface.
- the grooves are designed to run in the longitudinal direction of the guide surface.
- the grooves are formed at an angle to the longitudinal direction of the guide surface.
- the grooves can have a gradient which varies in the longitudinal direction of the guide surface.
- the grooves are formed by a helical line.
- the helix is multi-start.
- the helix can have a gradient that varies in the longitudinal direction of the guide surface.
- the grooves are designed to run crosswise at different angles to the longitudinal direction of the guide surface.
- grooves are designed with a gradient varying in the longitudinal direction of the guide surface.
- the grooves are formed in a region of the guide surface which adjoins the high pressure of the piston.
- the grooves can be formed over the entire area of the guide surface.
- the grooves are formed in the lateral surface of the piston which serves as a guide surface.
- the grooves can be provided in the cylinder bore serving as a guide surface.
- the invention is of particular value in the case of a high-pressure piston-cylinder unit which is part of a fuel injector of a common rail injection system in which the piston serves to actuate the injection valve of the fuel injector, and the pressure difference is permanently applied to the piston.
- constant deaxing can occur, that is to say from the beginning of the movement of the piston in the cylinder bore, which is why the invention can be used to achieve a significant reduction in wear with particular advantage.
- the piston is advantageously made of one piece of material on the nozzle needle of the injection valve, the piston having a shoulder which is permanently acted upon by the fuel pressure of the common rail injection system.
- the grooves are advantageously formed on the lateral surface of the piston which adjoins the shoulder acted upon by the fuel pressure and serves as a guide surface.
- the method according to the invention for producing a high-pressure unit of the invention provides that the grooves are produced by machining, for example fine turning.
- An alternative method which is of particular advantage, provides for the grooves to be produced by beam machining.
- Such beam processing is advantageously carried out in particular by laser engraving.
- An advantageous development of the method according to the invention provides that, after the grooves have been produced, lapping or fine grinding of the 8th
- the grooves can also be preceded by a fine machining of the guide surface.
- Figure 1 is a partially sectioned side view of the injector
- Fuel injector of a common rail injection system which is designed according to an exemplary embodiment of the invention, the section A enlarged showing the fine grooves provided in the guide surface of a piston of the injection valve;
- FIG. 2 shows an enlarged view of the nozzle needle of the injection valve of the fuel injector shown in FIG. 1;
- FIG. 3 shows a greatly enlarged cross section through the fine grooves formed on the guide surface of the piston of the nozzle needle shown in FIG. 2;
- Figure 4 is a view corresponding to Figure 2 of the nozzle needle of the injection valve with four embodiments a) to d) the arrangement of the grooves on the as
- Figure 5 is a greatly enlarged view of the guide surface of the piston with grooves designed as a screw thread.
- FIG. 1 shows a view, partly in cross section, of the injection nozzle of a fuel injector for a common rail fuel injection system.
- the injection nozzle designated by reference number 1 has a needle housing 2, in which a cylinder bore 3 is provided.
- a piston 5 is located in this cylinder bore 3 performed, which is integrally formed with a nozzle needle 4.
- the nozzle needle 4 has a needle tip 8 which interacts with a valve seat 9.
- an injection cross section 11 is formed in the form of injection openings.
- a shoulder 6 is formed, which lies in the area of an annular space 12 formed in the needle housing, into which a fuel channel 7 opens.
- the fuel channel 7 leads to a high-pressure accumulator of the common rail system, in which fuel to be injected is held under high pressure.
- the fuel injector has an electromechanical or hydraulic actuating element, not shown in FIG. 1, as is well known per se, by means of which the piston 5 is released in the sense of an upward movement, so that the piston in the annular space 12 fuel pressure acting on the shoulder 6 of the piston 5 causes the nozzle needle 4 and thus the needle tip 8 to be lifted out of the valve seat 9 and thus releases the injection cross section 11.
- fine grooves 10 are formed in the lateral surface of the piston 5 at a short distance from one another. These grooves 10 on the one hand bring about a hydraulic pressure compensation over the circumference of the piston 5 in the guide formed by the cylinder bore 3 and thus prevent the piston 5 from one-sided contact due to the annular space 12 in the gap between the outer surface of the piston 5 and the cylinder bore 3 entering fuel under high pressure when the nozzle needle guide is deaxed. At the same time, an asymmetrical and thus increased leakage flow in the longitudinal direction of the guide between the outer surface of the piston 5 and the cylinder bore 3 is reduced, and thus the hydraulic efficiency of the fuel injector is improved.
- the nozzle needle 4 provided in one piece with the piston 5 is shown enlarged.
- the piston 5 has a nominal diameter D, which at the 10 illustrated embodiment is 6.8 millimeters.
- D nominal diameter
- the grooves 10 are formed over a length 1 in the circumferential direction on the lateral surface of the piston 5. In the illustrated embodiment, this length 1, over which the grooves 10 are provided, is approximately 22 mm.
- FIG. 3 shows a greatly enlarged cross section through the surface of the jacket of the piston 5, which shows two grooves 10.
- the cross section of the grooves 10 has a substantially triangular shape in the illustrated embodiment.
- the width b of a groove is, for example, 5 to 100 ⁇ m, preferably between 10 to 40 ⁇ m. In the illustrated embodiment, the groove width b is 30 ⁇ m.
- the groove depth t can be 3 to 50 ⁇ m, preferably between 10 to 30 ⁇ m. In the exemplary embodiment shown, the depth is 15 ⁇ m.
- the distance a between two grooves can be between 0.05 to 1 mm, preferably between 0.1 to 0.5 mm, preferably between 0.1 to 0.3 mm. In the illustrated embodiment, the distance a is 0.2 mm.
- the ratio of the depth t of the groove 10 to the nominal diameter D of the guide surface or of the piston 5 is advantageously between 1/200 and 1/1000. In the illustrated embodiment, the ratio mentioned is around 1/450, which has proven to be particularly advantageous.
- the cross section of the grooves 10 can take other forms instead of a triangular shape, for example a semicircular shape.
- FIG. 4 again shows a representation corresponding to FIG. 2 and examples a) to d) of the structuring of the outer surface of the piston 5.
- the grooves 10 are formed in the circumferential direction of the piston 5, as shown in the side view above and also in FIG.
- the grooves are formed with the same distance a in the longitudinal direction, alternatively the grooves 10 can also be formed with a distance a varying in the longitudinal direction of the guide surface.
- the grooves 10 are designed to run in the longitudinal direction of the guide surface.
- the grooves 10 are designed to run at an angle to the longitudinal direction of the guide surface.
- the grooves 10 all have the same slope.
- the grooves 10 can also be provided with an incline that varies in the longitudinal direction of the guide surface.
- the grooves 10 can be formed by a helical line.
- a section of the guide surface with grooves formed as a screw thread 22 is shown in FIG. 5.
- the guide surface is a cylindrical piston surface which is divided by the threads of the screw thread 22.
- the pitch of the screw thread 22 is indicated by s.
- the screw thread or the screw line can be single-start or multi-start.
- the helix may have a constant gradient in the longitudinal direction of the guide surface or, alternatively, a gradient varying in the longitudinal direction of the guide surface. The formation of the grooves as a helix is particularly advantageous in terms of production technology.
- the grooves 10 can be designed to run crosswise at different angles to the longitudinal direction of the guide surface, the angles 12 opposite, but may be the same in amount or different in amount. While in the illustrated embodiment the slope of the grooves 10 in the longitudinal direction of the guide surface is the same, the grooves 10 can alternatively also be formed with a gradient varying in the longitudinal direction of the guide surface.
- the structuring patterns according to FIGS. 4a) to 4d) are basic patterns, but different patterns are also possible. Furthermore, several patterns can be combined in accordance with the type described with reference to FIGS. 4a) to 4d).
- the distance a of the grooves 10 in the longitudinal direction of the guide surface is selected so that it essentially corresponds to the operating stroke of the piston 5 in the cylinder bore 3. This has the advantageous effect that the remaining guide surface on the jacket of the piston 5 between the grooves 10 is constantly moving on wetted surfaces of the guide, thus largely preventing the guide from running dry. In the case of a single-start thread, the distance a between the grooves 10 then corresponds to the thread pitch.
- the grooves 10 are formed in the outer surface of the piston 5 in their function as a guide surface.
- the grooves 10 can also be formed in the cylinder bore 3 as a guide surface.
- the piston is exposed to a high pressure difference on one side, as is the case in particular with other injection valves and injection pumps for internal combustion engines, the invention leads to a corresponding advantage.
- the grooves 10 in the guide surface of the piston can be produced by machining, for example by turning, precision turning, grinding or milling.
- the grooves, in particular on the lateral surface of the piston 5, can be produced by beam machining, the method of laser engraving being particularly advantageous.
- the grooves 10 are produced after the finishing (grinding) of the guide surface. After the grooves 10 have been produced, the guide surface is lapped or ground to produce the final surface of the guide surface. A fine machining of the guide surface before creating the grooves can also be omitted if adequate dimensional accuracy can be ensured by suitable manufacturing measures.
Abstract
Description
Claims
Applications Claiming Priority (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE1998113454 DE19813454B4 (en) | 1998-03-26 | 1998-03-26 | High-pressure piston-cylinder unit for high stroke cycles |
DE19813454 | 1998-03-26 | ||
DE19820264 | 1998-05-07 | ||
DE1998120264 DE19820264A1 (en) | 1998-05-07 | 1998-05-07 | High-pressure piston cylinder unit for internal combustion engine |
PCT/EP1999/002010 WO1999049209A1 (en) | 1998-03-26 | 1999-03-24 | High-pressure piston cylinder unit |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1066466A1 true EP1066466A1 (en) | 2001-01-10 |
EP1066466B1 EP1066466B1 (en) | 2002-10-16 |
Family
ID=26044996
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP99915701A Expired - Lifetime EP1066466B1 (en) | 1998-03-26 | 1999-03-24 | High-pressure piston cylinder unit |
Country Status (5)
Country | Link |
---|---|
US (1) | US6477940B1 (en) |
EP (1) | EP1066466B1 (en) |
AT (1) | ATE226279T1 (en) |
DE (1) | DE59903092D1 (en) |
WO (1) | WO1999049209A1 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1469187A1 (en) * | 2003-04-16 | 2004-10-20 | Siemens Aktiengesellschaft | Valve needle assembly and method for producing the same |
WO2017203092A1 (en) | 2016-05-25 | 2017-11-30 | Wärtsilä Finland Oy | Fuel injection valve unit for an internal combustion piston engine and a method of operating the fuel injection valve unit |
Families Citing this family (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19843344A1 (en) * | 1998-09-22 | 2000-03-23 | Bosch Gmbh Robert | Fuel injection valve for internal combustion engine has valve member axially movably positioned in bore of valve body, which has valve sealing surface at combustion chamber-side end |
DE10024854C2 (en) * | 2000-05-19 | 2002-11-28 | Siemens Ag | Valve needle and valve control piston of injectors |
DE10046323B4 (en) * | 2000-09-19 | 2004-02-12 | Siemens Ag | Hydraulic backlash compensation system |
DE10232050A1 (en) * | 2002-07-16 | 2004-02-05 | Robert Bosch Gmbh | Fuel injection valve, for an IC motor, has micro-recesses in the valve needle sealing surface and/or the valve seat to improve the drift behavior of the injected fuel volume and increase the working life |
KR101307563B1 (en) * | 2003-07-16 | 2013-09-12 | 베르트질레 슈바이츠 악티엔게젤샤프트 | Piston for a high pressure piston in cylinder unit |
JP4066959B2 (en) * | 2004-01-27 | 2008-03-26 | 株式会社デンソー | Fuel injection device |
DE102005011574A1 (en) * | 2005-03-14 | 2006-09-21 | Robert Bosch Gmbh | Intermediate element for a fuel injection valve |
WO2007056172A1 (en) * | 2005-11-04 | 2007-05-18 | Robert Bosch Gmbh | Method and apparatus for an articulating drill |
JP2008057458A (en) * | 2006-08-31 | 2008-03-13 | Mitsubishi Heavy Ind Ltd | Fuel injection valve |
DE102009000181A1 (en) * | 2009-01-13 | 2010-07-15 | Robert Bosch Gmbh | Fuel injector |
DE102011051904A1 (en) | 2011-07-18 | 2012-06-21 | L'orange Gmbh | Device i.e. nozzle element, for use in fuel injection system, has structures formed at surfaces of guiding path and/or lifting rod and comprising and/or formed by trimming edges that traverse each other based on stroke position |
DE102011090148B4 (en) | 2011-12-30 | 2017-06-01 | Continental Automotive Gmbh | Method for producing a nozzle needle for an injector for injecting fuel into cylinder combustion chambers of an internal combustion engine and injector with such a nozzle needle |
JP6660548B2 (en) * | 2015-07-23 | 2020-03-11 | 住友ゴム工業株式会社 | Medical syringe, gasket applied to syringe and method of manufacturing the same |
DE102016207171A1 (en) | 2016-04-27 | 2017-11-02 | Robert Bosch Gmbh | High pressure pump with reduced wear |
IT201700054112A1 (en) * | 2017-05-18 | 2018-11-18 | Bosch Gmbh Robert | PUMP UNIT FOR FUEL SUPPLY TO AN INTERNAL COMBUSTION ENGINE |
KR102268258B1 (en) * | 2019-11-08 | 2021-06-23 | 엘지전자 주식회사 | Compressor and Manufacturing Method thereof |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
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US3398936A (en) * | 1966-08-02 | 1968-08-27 | Curtiss Wright Corp | Fuel injection pintle |
US3425635A (en) * | 1967-02-15 | 1969-02-04 | Int Harvester Co | Fuel injection nozzle |
US3722801A (en) * | 1970-09-11 | 1973-03-27 | Stanadyne Inc | Fuel injector |
WO1989010479A1 (en) * | 1988-04-22 | 1989-11-02 | Hei-Tech B.V. | High-pressure piston cylinder unit |
DE3824467A1 (en) | 1988-07-19 | 1990-01-25 | Man B & W Diesel Ag | Injection valve |
DE3932328A1 (en) | 1989-09-28 | 1991-04-11 | Opel Adam Ag | METHOD FOR MACHINING SURFACES HIGHLY STRESSED BY FRICTION IN INTERNAL COMBUSTION ENGINES, AND DEVICE FOR CARRYING OUT THE METHOD |
DE4139907A1 (en) * | 1991-12-04 | 1993-06-09 | Robert Bosch Gmbh, 7000 Stuttgart, De | High pressure fuel injection device - has labyrinth seal between pump piston and cylinder liner, or between nozzle pin and housing |
EP0565742B1 (en) | 1992-04-11 | 1995-03-01 | Maschinenfabrik Gehring GmbH & Co. | Procedure of fine machining workpiece surfaces |
JP3159593B2 (en) * | 1994-02-28 | 2001-04-23 | 三菱電機株式会社 | Laser processing method and apparatus |
IT1276503B1 (en) * | 1995-07-14 | 1997-10-31 | Elasis Sistema Ricerca Fiat | IMPROVEMENTS TO AN ELECTROMAGNETICALLY OPERATED DOSING VALVE, FOR A FUEL INJECTOR. |
-
1999
- 1999-03-24 AT AT99915701T patent/ATE226279T1/en active
- 1999-03-24 WO PCT/EP1999/002010 patent/WO1999049209A1/en active IP Right Grant
- 1999-03-24 DE DE59903092T patent/DE59903092D1/en not_active Expired - Lifetime
- 1999-03-24 EP EP99915701A patent/EP1066466B1/en not_active Expired - Lifetime
- 1999-03-24 US US09/647,058 patent/US6477940B1/en not_active Expired - Lifetime
Non-Patent Citations (1)
Title |
---|
See references of WO9949209A1 * |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1469187A1 (en) * | 2003-04-16 | 2004-10-20 | Siemens Aktiengesellschaft | Valve needle assembly and method for producing the same |
WO2017203092A1 (en) | 2016-05-25 | 2017-11-30 | Wärtsilä Finland Oy | Fuel injection valve unit for an internal combustion piston engine and a method of operating the fuel injection valve unit |
Also Published As
Publication number | Publication date |
---|---|
ATE226279T1 (en) | 2002-11-15 |
EP1066466B1 (en) | 2002-10-16 |
WO1999049209A1 (en) | 1999-09-30 |
US6477940B1 (en) | 2002-11-12 |
DE59903092D1 (en) | 2002-11-21 |
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Legal Events
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