EP1066465B1 - Kraftstoff-einspritzventil für eine hochdruckeinspritzung - Google Patents
Kraftstoff-einspritzventil für eine hochdruckeinspritzung Download PDFInfo
- Publication number
- EP1066465B1 EP1066465B1 EP99966842A EP99966842A EP1066465B1 EP 1066465 B1 EP1066465 B1 EP 1066465B1 EP 99966842 A EP99966842 A EP 99966842A EP 99966842 A EP99966842 A EP 99966842A EP 1066465 B1 EP1066465 B1 EP 1066465B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- diffuser
- fuel injection
- ball
- valve ball
- 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
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
- 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
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/0012—Valves
- F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
- F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
- F02M63/0036—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat with spherical or partly spherical shaped valve member ends
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/0012—Valves
- F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
- F02M63/0071—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059 characterised by guiding or centering means in valves including the absence of any guiding means, e.g. "flying arrangements"
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/0012—Valves
- F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
- F02M63/0077—Valve seat details
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
- F02M2547/003—Valve inserts containing control chamber and valve piston
Definitions
- the invention relates to a fuel injection valve for a high-pressure injection according to the preamble of claim 1.
- Document EP 0 851 115 A1 shows a fuel injection valve according to the preamble of claim 1.
- Such an injection valve is from European patent application 0 661 442 A1 known.
- Fuel injection valves of this type have a control chamber on, constantly via an inlet throttle bore with a high pressure fuel source is connected via a high pressure line. A valve closing member the fuel injector is held in the closed position until how high the control pressure in the control room is.
- the control chamber can be relieved via an outlet throttle bore, which by an injection control valve is applied. Once the injection control valve the drain throttle bore releases, the control chamber is relieved and that Valve closing element of the fuel injection valve goes into its open position over, so that the injection into a combustion chamber of an internal combustion engine can be done. If the injection control valve the drain throttle bore closes again because of the pressure increase in the control room Valve closing element brought back into the closed position.
- the opening and closing movements of the injection control valve are for the quality of the Fuel injection is vital.
- the reproducibility the opening and closing movements are crucial to the structure of the injection control valve, which essentially consists of a valve seat for opening and closing the outlet throttle bore with a valve ball interacts by a guide member to close and open the Injection control valve pressed onto the valve seat or to open one Spring preload a spring is exposed.
- a typical embodiment of the essential structural parts of a Injection control valve shows a section of FIG. 3.
- the fuel injection valve is about the compression 11 with the central High-pressure line 6 connected, which in turn is connected to a high-pressure fuel source communicates.
- An inlet throttle bore 10 is a Control chamber 7 is placed under high pressure, which on a valve closing member 12 acts that keeps the fuel injector closed as long as the High pressure is present in the high pressure control room.
- Via a relief hole, which passes into an outlet throttle bore 8, the control room 7 are relieved, so that the valve closing member, the fuel injector opens and fuel from the central high pressure line 6 into the combustion chambers injects an internal combustion engine.
- the opening and closing of the drain throttle bore 8 is through an injection control valve with a valve seat 2 a valve ball 3 and a guide member guiding the valve ball 3 4 guaranteed.
- the flat-conical valve seat is also evident here to recognize an obtuse opening angle ⁇ , which is also evident from the publication EP 0 661 442 A1 with FIG. 2 is known.
- the object of the invention is therefore to address the disadvantages of fuel injection valves state of the art to overcome a safe, even closing of the valve ball in the injection control valve ensure and distortion caused by transients or others Valve ball obstruction when closing the injection control valve Reduce.
- the funnel shape By forming an approximately steep-walled funnel shape Drain throttle bore, diffuser and valve seat, the funnel shape one has right to acute cone angle ⁇ is advantageously achieved, that in contrast to the conventional valve seat with a flat cone drain throttle bore arranged centrally on the cone tip Funnel wall of the valve seat when the injection control valve closes Centering the valve ball supports and radial displacement of the Valve ball opposite the diffuser and the outlet throttle bore prevented.
- the design of the injection control valve according to the invention increased accuracy and in the fuel injector Reproducibility of the opening and closing movements achieved.
- a diffuser is usually a continuous expansion of a minimum diameter to a maximum diameter.
- the diffuser is designed as a "cross-sectional jump", i.e. minimum and The maximum diameter of the diffuser is the same. This represents an erratic Extension of the outlet throttle bore to the diameter of the diffuser represents what is commonly referred to as the Carnot opening.
- Such one Carnot opening has the advantage that the drag coefficient ⁇ by simply changing the ratio between the diameter of the diffuser and the diameter of the outlet throttle bore can be optimized.
- the ratio is between the mean diameter of the diffuser and the diameter the outlet throttle bore between 1.2 and 2, so that approximately the Resistance coefficient ⁇ can be set between 0.16 and 9.
- the Cone angle ⁇ 60 ° to 90 ° In contrast to that from the state of the Technically known flat cone allows this steep wall cone improved centering of the valve ball. With cone angles less than 60 ° the centering of the valve ball is supported more, but can the ball does not protrude deep enough into the diffuser to The smallest possible distance to the outlet throttle bore when the valve is closed Injection control valve to hover. On the other hand, at cone angles ⁇ greater than 90 ° the centering effect of the funnel shape becomes increasingly smaller, so that the disadvantages described for the prior art increase.
- the valve ball is preferably immersed between 1/5 and 1/10 of its radius r into the diffuser. This can be achieved in an advantageous manner that on the one hand a sufficiently large ball cap of the valve ball from the high pressure jet hit and lifted centered from the valve seat and on the other hand Excessive immersion of the valve ball in the diffuser is avoided.
- the maximum diameter D of the diffuser and the length l of the diffuser on each other matched that the valve ball in a closed injection valve Distance of ⁇ 0.1 mm, preferably between 30 and 80 microns above Drain throttle bore is positioned. With this distance is preferred ensures that the high pressure jet from the outlet throttle bore at Initially, opening the injection control valve does not just open the valve ball surface acted in the area of the throttle bore, but that the Pressure on the larger surface of a ball cap of the valve ball in the Range of the maximum diameter of the diffuser or valve seat effect.
- the length-to-diameter ratio is the proportion of the throttling Drain throttle bore crucial. The smaller the diameter and each the greater the length of a throttle bore, the greater the throttling. With increasing throttling, lower consumption also increases reached fuel running out of the control room. At the same time however, the time for the relief of the high pressure in the control room increases. Therefore, the range from 1 to 20 represents the length-to-diameter ratio the drain throttle bore an optimal compromise between these two extremes.
- the diffuser preferably has a length-to-maximum diameter ratio between 0.1 and 0.5. With this length-to-maximum diameter ratio the diffuser is achieved that the flow at the jacket-shaped wall of the diffuser does not come into contact, so that the Friction losses in the diffuser become negligibly small, while the Flow losses due to vortex formation at the step-like transition increase.
- Fig. 1 shows a cross section through a fuel injection valve in the area of a valve seat 2 of an injection control valve in a first embodiment the invention.
- a pressure chamber 7 is above one shown in FIG Inlet throttle bore 10 connected to a central high-pressure line 6 and is therefore under a fuel pressure between 150 and 300 MPa.
- valve ball 3 is replaced by a valve ball 3 shown in FIG. 3 leading guide member 4 held when opening and closing.
- the Centering the ball 3 on the valve seat 2 is essential by a steep-walled funnel shape, which has a right to acute cone angle ⁇ , which is 90 ° in this preferred embodiment, guaranteed.
- This can advantageously be the high pressure jet from the outlet throttle bore 8 hit the valve ball 3 centrally and this as soon as a solenoid valve Valve ball 3 relieved of a contact pressure on the valve seat 2 in Raise arrow direction A.
- a diffuser 9 Between valve seat 2 and outlet throttle bore 8 is arranged a diffuser 9, in which in this embodiment the The minimum diameter d and the maximum diameter D are the same.
- the length-to-diameter ratio of the diffuser 9 is in this embodiment 0.2, and the length-to-diameter ratio of the drain throttle bore 8 is ⁇ 2.
- the valve ball 3 dips with an eighth of hers Radius r into the diffuser 9 and is when the injection control valve is closed positioned at a distance of 80 ⁇ m above the throttle bore.
- the Cross-sectional expansion between discharge throttle bore 8 and diffuser 9 forms a Carnot opening where the flow of the high pressure jet, from the outlet throttle bore 8 towards the center of the valve ball 3 is no longer laminar to the walls of the diffuser 9, rather, there are lossy flow vortices at the cross-sectional expansion forms.
- the diffuser 9 has in connection with the steep-walled valve seat 2 a much higher centering effect on the Valve ball 3 as the conventional flat conical valve seats in connection with an immediate transition from the drain throttle bore 8 to the Valve seat 2 using conventional technology.
- valve ball 3 plunges much deeper in this embodiment the diffuser 9 and floats when the injection control valve 30 is closed ⁇ m over the drain edge 14 of the drain throttle bore 8.
- the valve ball 3 is hydraulic centered. This means that the closing can be done smoothly and No distortions in the return flow when closing the valve ball 3 occur.
- the relatively large diffuser hole also has the advantage that the steep-walled valve seat 2 can be machined and polished better.
- FIG. 3 shows a cross-section in sections in the area of the essential structural parts of a conventional injection control valve, as already described in detail in the prior art chapter.
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
Description
- Fig. 1
- einen Querschnitt durch ein Kraftstoff-Einspritzventil im Bereich eines Ventilsitzes eines Einspritzsteuerventils in einer ersten Ausführungsform der Erfindung;
- Fig. 2
- einen Querschnitt durch ein Kraftstoff-Einspritzventil im Bereich eines Ventilsitzes eines Einspritzsteuerventils in einer zweiten Ausführungsform der Erfindung; und
- Fig. 3
- einen ausschnittsweisen Querschnitt im Bereich der wesentlichen konstruktiven Teile eines herkömmlichen Einspritzsteuerventils.
Claims (8)
- Kraftstoff-Einspritzventil für eine Hochdruckeinspritzung von Kraftstoff aus einer zentralen Hochdruckleitung (6) in Brennräume einer Brennkraftmaschine, das ein Einspritzsteuerventil (1) mit einem Ventilsitz (2), einer Ventilkugel (3) und einem die Ventilkugel (3) führenden Führungsglied (4) aufweist, welches zu dessen Schließen die Ventilkugel (3) auf dem Ventilsitz (2) preßt und zu dessen Öffnen die Ventilkugel (3) einer Federvorspannung einer Feder (5) aussetzt, wobei die Ventilkugel (3) in geöffnetem Zustand mittels eines Hochdruckstrahls, der von einem mit der zentralen Hochdruckleitung (6) in Verbindung stehenden Steuerraum (7) über eine Ablauf-Drosselbohrung (8) gespeist ist, vom Ventilsitz (2) abgehoben ist, wobei
zwischen Ventilsitz (2) und Ablauf-Drosselbohrung (8) ein Diffusor (9) angeordnet ist, dadurch gekennzeichnet, daß die Ablauf-Drosselbohrung (8), der Diffusor (9) und der Ventilsitz (2) näherungsweise eine steilwandige Trichterform mit einem recht- bis spitzwinkligen Konuswinkel (α) aufweisen. - Kraftstoff-Einspritzventil nach Anspruch 1, dadurch gekennzeichnet, daß Minimal- (d) und Maximaldurchmesser (D) des Diffusors (9) gleich sind.
- Kraftstoff-Einspritzventil nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß das Verhältnis zwischen einem mittleren Durchmesser dm des Diffusors (9) und einem Durchmesser (m) der Ablauf-Drosselbohrung (8) zwischen 1,2 und 2 ist.
- Kraftstoff-Einspritzventil nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß der Konuswinkel (α) 60 bis 90° ist.
- Kraftstoff-Einspritzventil nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß die Ventilkugel (3) zwischen 1/5 und einem 1/10 ihres Radius (r) in den Diffusor (9) eintaucht.
- Kraftstoff-Einspritzventil nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß der Maximaldurchmesser (D) des Diffusors (9) und die Länge des Diffusors (9) derart aufeinander abgestimmt sind, daß die Ventilkugel (3) bei geschlossenem Einspritzventil (1) in einem Abstand ≤ 0,1 mm, vorzugsweise zwischen 30 und 80 µm über der Ablauf-Drosselbohrung (8) positioniert ist.
- Kraftstoff-Einspritzventil nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, daß die Ablauf-Drosselbohrung ein Länge-zu-Durchmesser-Verhältnis zwischen 1 und 20 aufweist.
- Kraftstoff-Einspritzventil nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, daß der Diffusor (9) ein Länge-zu-Maximaldurchmesser-Verhältnis zwischen 0,1 und 0,5 aufweist.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19859484A DE19859484A1 (de) | 1998-12-22 | 1998-12-22 | Kraftstoff-Einspritzventil für eine Hochdruckeinspritzung |
DE19859484 | 1998-12-22 | ||
PCT/DE1999/003913 WO2000037793A1 (de) | 1998-12-22 | 1999-12-08 | Kraftstoff-einspritzventil für eine hochdruckeinspritzung |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1066465A1 EP1066465A1 (de) | 2001-01-10 |
EP1066465B1 true EP1066465B1 (de) | 2004-03-17 |
Family
ID=7892274
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP99966842A Expired - Lifetime EP1066465B1 (de) | 1998-12-22 | 1999-12-08 | Kraftstoff-einspritzventil für eine hochdruckeinspritzung |
Country Status (6)
Country | Link |
---|---|
US (1) | US6378502B1 (de) |
EP (1) | EP1066465B1 (de) |
JP (1) | JP2002533607A (de) |
KR (1) | KR100692113B1 (de) |
DE (2) | DE19859484A1 (de) |
WO (1) | WO2000037793A1 (de) |
Families Citing this family (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10036868B4 (de) * | 2000-07-28 | 2004-07-29 | Robert Bosch Gmbh | Injektor für ein einen Hochdrucksammelraum umfassendes Einspritzsystem |
JP2003113761A (ja) * | 2001-08-01 | 2003-04-18 | Denso Corp | 燃料噴射弁 |
EP1442209A1 (de) * | 2001-11-09 | 2004-08-04 | Siemens Aktiengesellschaft | Steuermodul für einen injektor eines speichereinspritzsystems |
US8133554B2 (en) | 2004-05-06 | 2012-03-13 | Micron Technology, Inc. | Methods for depositing material onto microfeature workpieces in reaction chambers and systems for depositing materials onto microfeature workpieces |
DE102004061800A1 (de) * | 2004-12-22 | 2006-07-06 | Robert Bosch Gmbh | Injektor eines Kraftstoffeinspritzsystems einer Brennkraftmaschine |
DE102006052817A1 (de) | 2006-11-09 | 2008-05-15 | Robert Bosch Gmbh | Brennstoffeinspritzventil |
DE102007004553A1 (de) * | 2007-01-30 | 2008-07-31 | Robert Bosch Gmbh | Kugelsitzventil mit verringertem Erosionsverhalten |
DE102010043092A1 (de) * | 2010-10-29 | 2012-05-03 | Robert Bosch Gmbh | Druckregelventil |
DE102011004993A1 (de) * | 2011-03-02 | 2012-09-06 | Robert Bosch Gmbh | Ventileinrichtung zum Schalten oder Zumessen eines Fluids |
DE102012221540A1 (de) * | 2012-11-26 | 2014-05-28 | Robert Bosch Gmbh | Ventileinrichtung |
CN108025270B (zh) * | 2015-07-16 | 2021-08-27 | 大川原化工机株式会社 | 湿式分散器 |
CN107387281A (zh) * | 2017-07-31 | 2017-11-24 | 成都威特电喷有限责任公司 | 柴油共轨油泵进出油单向阀 |
Family Cites Families (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2296805A1 (fr) * | 1975-01-06 | 1976-07-30 | Dba | Electrovanne miniature |
DE3230844A1 (de) * | 1982-08-19 | 1984-02-23 | Robert Bosch Gmbh, 7000 Stuttgart | Elektromagnetisch betaetigbares ventil |
DE3510222A1 (de) * | 1985-03-21 | 1986-09-25 | Robert Bosch Gmbh, 7000 Stuttgart | Magnetventil, insbesondere kraftstoffmengensteuerventil |
US4655396A (en) * | 1985-09-25 | 1987-04-07 | United Technologies Diesel Systems, Inc. | Electromagnetic fuel injector |
IT220662Z2 (it) * | 1990-10-31 | 1993-10-08 | Elasis Sistema Ricerca Fita Nel Mezzogiorno Soc.Consortile P.A. | Perfezionamenti alla valvola pilota e alla relativa ancora di comando odi un iniettore elettromagnetico per sistemi di iniezione del combustibile di motori a combustione interna |
BR7100246U (pt) * | 1991-02-05 | 1991-07-23 | Daniel Sofer | Disposicao em valvula para injetor de combustivel |
US5197675A (en) * | 1991-02-11 | 1993-03-30 | Siemens Automotive L.P. | Fuel rail having rolling ball fuel injectors |
JP3294382B2 (ja) * | 1992-10-30 | 2002-06-24 | 株式会社デンソー | 流量制御弁 |
IT1261149B (it) * | 1993-12-30 | 1996-05-09 | Elasis Sistema Ricerca Fiat | Valvola di dosaggio per il comando dell'otturatore di un iniettore di combustibile |
US5626325A (en) * | 1995-09-14 | 1997-05-06 | Cummins Engine Company, Inc. | High pressure control valve for a fuel injection system |
DE19618468C1 (de) * | 1996-05-08 | 1997-04-30 | Siemens Ag | Einspritzventil |
DE19634105A1 (de) * | 1996-08-23 | 1998-01-15 | Daimler Benz Ag | Einspritzventil für Verbrennungskraftmaschinen |
IT1289795B1 (it) * | 1996-12-23 | 1998-10-16 | Elasis Sistema Ricerca Fiat | Perfezionamenti ad una valvola di dosaggio a comando elettromagnetico, con otturatore a sfera, per un iniettore di combustibile. |
DE19742320A1 (de) * | 1997-09-25 | 1999-04-01 | Bosch Gmbh Robert | Kraftstoffeinspritzventil |
DE19746143A1 (de) * | 1997-10-18 | 1999-04-22 | Bosch Gmbh Robert | Ventil zum Steuern von Flüssigkeiten |
IT1296143B1 (it) * | 1997-11-18 | 1999-06-09 | Elasis Sistema Ricerca Fiat | Dispositivo di comando di un iniettore di combustibile per motori a combustione interna. |
US6129072A (en) * | 1999-04-02 | 2000-10-10 | Caterpillar Inc. | Hydraulically actuated device having a ball valve member |
-
1998
- 1998-12-22 DE DE19859484A patent/DE19859484A1/de not_active Ceased
-
1999
- 1999-12-08 US US09/622,718 patent/US6378502B1/en not_active Expired - Lifetime
- 1999-12-08 JP JP2000589826A patent/JP2002533607A/ja active Pending
- 1999-12-08 DE DE59908890T patent/DE59908890D1/de not_active Expired - Lifetime
- 1999-12-08 KR KR1020007009193A patent/KR100692113B1/ko not_active IP Right Cessation
- 1999-12-08 EP EP99966842A patent/EP1066465B1/de not_active Expired - Lifetime
- 1999-12-08 WO PCT/DE1999/003913 patent/WO2000037793A1/de active IP Right Grant
Also Published As
Publication number | Publication date |
---|---|
EP1066465A1 (de) | 2001-01-10 |
DE19859484A1 (de) | 2000-07-06 |
DE59908890D1 (de) | 2004-04-22 |
JP2002533607A (ja) | 2002-10-08 |
KR20010041144A (ko) | 2001-05-15 |
KR100692113B1 (ko) | 2007-03-12 |
WO2000037793A1 (de) | 2000-06-29 |
US6378502B1 (en) | 2002-04-30 |
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