EP0943054B1 - Kraftstoffeinspritzventil für brennkraftmaschinen - Google Patents
Kraftstoffeinspritzventil für brennkraftmaschinen Download PDFInfo
- Publication number
- EP0943054B1 EP0943054B1 EP98936173A EP98936173A EP0943054B1 EP 0943054 B1 EP0943054 B1 EP 0943054B1 EP 98936173 A EP98936173 A EP 98936173A EP 98936173 A EP98936173 A EP 98936173A EP 0943054 B1 EP0943054 B1 EP 0943054B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- valve member
- fuel injection
- pressure
- injection valve
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- 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
Definitions
- the invention relates to a fuel injection valve for Internal combustion engines according to the preamble of claim 1 out.
- Fuel injector is a piston-shaped one Valve member axially displaceable in a bore in a valve body guided.
- the valve member points to his end of the combustion chamber on a conical valve sealing surface, with which it has a conical valve seat on the valve body which cooperates at the cantilevered end of the closed valve bore is formed.
- a Contact edge between the valve sealing surface on the valve member and the valve seat surface a circumferential sealing edge.
- This sealing edge formed when the injection valve is closed seals an upstream adjacent to the sealing edge Pressure chamber with the injector closed. Downstream of this sealing edge is at least one in the Combustion chamber of the internal combustion engine to be supplied Injection opening provided in the wall of the valve body, which leads away from the valve seat surface.
- this known fuel injection valve has the disadvantage that the operating times of the valve member due of the large hydraulic forces on the valve member for very fast switching injection valves are too long. Furthermore builds the well-known fuel injector due to the large number of axially consecutive components very large in terms of the usability of the known Fuel injectors are available on engines with low limited space.
- the fuel injection valve according to the invention for internal combustion engines with the characterizing features of the claim 1 has the advantage that very small Actuating forces and therefore very fast valve stroke movements of the Valve element of the injection valve are possible.
- the valve member has a guide bore has with which it slidably on a pin a fixed insert body is guided. It is Slidable valve member hydraulically in the injection breaks pressure equalized so that no leakage losses occur. This means that there is no seal for leaking leakage oil to the outside necessary, in addition to the leakage also heat development and a possible dirt entry due to the good Reduce separation of sealing and guide components leaves.
- Another advantage is the very short construction Construction of the fuel injection valve according to the invention reached, whereby the required installation space on the to be supplied Internal combustion engine can also be greatly reduced can.
- the valve member of the injection valve in the closing direction return spring must act on the injector only close when the system is depressurized so that it can be dimensioned accordingly small.
- the closing movement and by holding the valve member on the valve seat surface the interpretation of the hydraulic effective on the valve member Opening and closing surfaces, with the hydraulic contact surface of the closing surfaces on the valve member when closed Injector larger than that in the opening direction acting hydraulic attack surfaces.
- the opening stroke movement the valve member becomes more advantageous Way by mechanical stroke stop surfaces on the pin of fixed insert body limited, but they are alternative hydraulic stroke stops also possible.
- Control room in a relief valve opening control valve can as shown in the embodiment as a 2/2-way solenoid valve be trained, but alternatively 2/3, 3/2 or 3/3 control valves can also be used.
- the valve member is via its inner guide bore axially guided on the pin of the stationary insert body, however, it is also possible to add another tour on the outer circumference of the valve member within the valve body provided.
- fuel passage openings on the valve member provided that a passage of fuel from a pressure chamber to the valve seat surfaces and which as Surface grinding on the outer surface of the valve member or can be formed as through holes.
- valve member itself can advantageously be in two parts be formed, wherein a having the valve sealing surface Head piece inserted into a sleeve, preferably pressed is.
- a two-part valve member is included easy to manufacture and with high accuracy.
- Another advantage of the fuel injector according to the invention is the possibility of a hydraulically floating Storage of the insert body carrying the pin in the valve body, so that this and the valve member guided on this are securely centerable with respect to the valve body.
- FIG. 1 shows a first embodiment of the Fuel injection valve in a longitudinal section, in which the fuel supply and relief of the control or work area between the pin and the valve member a central through hole is made in the pin
- the figure 2 shows an enlarged detail of the on the pin guided valve member, which is formed in two parts
- 3 shows a second exemplary embodiment of the fuel injection valve, in which the valve member an additional 4 has an external guide in the valve body third embodiment with a by a paragraph on Pin circumference formed stroke stop for the valve member
- the FIG. 5 shows a fourth exemplary embodiment of the fuel injection valve, at which the stroke stop of the valve member is formed by a stepped end face of the pin
- FIG. 6 shows a fifth exemplary embodiment of the fuel injection valve, in which the work or control room is arranged outside the pin of the insert body.
- the first embodiment shown in Figure 1 of the fuel injection valve according to the invention for internal combustion engines has a cylindrical valve body 1, the one with its free lower end into a not shown Combustion chamber of the internal combustion engine to be supplied protrudes.
- the valve body 1 designed as a hollow body is by means of a clamping nut 3 axially against a valve holding body 5 braced, being between the facing each other End faces of the valve body 1 and the valve holding body 5 an insert body 7 is clamped.
- This step-like cylindrical insert body 7 has on its the valve holding body 5 opposite end of a pin 9 with which he protrudes into the interior of the valve body 1.
- On the free end of the pin 9 is a cylindrical valve member 11 with a central guide bore 13 axially slidably guided.
- valve member 11 has on its a closed conical end facing away from the pin 9 Valve sealing surface 15, which in two areas different cone angles is divided, being at the transition between the two cone angles of the valve sealing surface 15 a circumferential sealing edge 17 is formed on the valve member 11 is.
- the valve member 11 acts with its valve sealing surface 15 with an inwardly projecting closed end of the Interior of valve seat surface 19 formed in valve body 1 together, the sealing edge 17 on the valve member 11 at the valve seat surface 19 adjacent valve member 11 a upstream, formed inside the valve body 1
- Pressure chamber 21 from a downstream of the sealing edge 17 lying blind hole 23 separates from which the sealing edge 17 downstream valve seat surface 19 injection openings 25 lead into the combustion chamber of the internal combustion engine.
- a return spring 27 is between an annular end face 29 facing away from the valve seat 19 on Valve member 11 and a shoulder 31 clamped on the pin 9, which acts on the valve member 11 in the direction of the valve seat surface 19. Furthermore, between the end face 33 closed end of the guide bore 13 in the valve member 11 and the end face 35 of the pin 9 a hydraulic working or control room 37 formed. This control room 37 is via an axial through hole 39 in the insert body 7 filled with high pressure fuel and relieved.
- the ring end face act to adjust the valve member 11 29 and the end face 33 of the guide bore 13 as hydraulic pressure application surfaces acting in the closing direction on the valve member 11.
- Valve member 11 first upstream of the Sealing edge 17 adjoining area acts.
- the diameter d3 for a safe function of the fuel injection valve larger than the diameter d1, which is the seat diameter at the valve sealing seat Are defined.
- the fuel injection valve according to the invention works in following way. At the beginning of the function of the injection system is the high-pressure storage space, not shown from the high pressure fuel pump with fuel filled with high pressure. This pressure is on the individual High-pressure lines 43 to the respective in the combustion chamber Internal combustion engine projecting injection valves. There the high fuel pressure reaches in the first embodiment via the high-pressure line 43 into the pressure chamber 21 as well as via the branching from the high pressure line 43 Throttle bore 41 and the through bore 39 in the insert body 7 in the control room 37. The control valve 47 stops the relief line 45 closed.
- the throttle bore 41 ensures that the the high-pressure line 43 inflowing high-pressure fuel does not immediately flow into the relief line 45 in a short circuit.
- the injection at the injection valve is ended, by the control valve 47 the relief line 45 again closes so that it is in the control chamber 37 via the bore 41 and 39 can build up a high fuel pressure again now over the attack surface 33 and the ring end face 29 the valve member 11 again in contact with the valve seat surface 19 moves. Because with the injector closed the hydraulic pressure inside and outside the displaceable Valve member 11 is of equal size, can a leakage flow at the valve member 11 in the low pressure chamber be avoided.
- the valve member 11 is during its lifting movement by means of its internal guide on the Pin 9 of the insert body 7 safely axially slidably guided.
- FIG 11 A possible embodiment of the valve member is shown in FIG 11 as a two-part component in an enlarged Item drawing shown.
- the valve member has 11 a sleeve 49, which is slidable with its inner diameter guided on the pin 9 of the insert body 7 and in its lower end on the combustion chamber side as stepped cylinder formed head piece 51 is pressed is that on its end facing away from the sleeve 49 has the valve sealing surface 15 and the sealing edge 17.
- the head 51 is preferably with a cone-shaped projection in the inner diameter of the sleeve 49 inserted and on the ring heel with the ring face the sleeve 11 welded.
- FIG. 3 shows a second exemplary embodiment of the invention Fuel injector shown at which the valve member 11 in addition to the internal guide on the Bore 13 via an outer guide on the inner wall of the valve body 1 is performed.
- the outer peripheral wall forms 53 of the valve member 11 this second additional guide surface on the inner wall surface 55 of the valve body 1 slides.
- the valve seat surface 19 are recesses on the outer circumference of the valve member 11 provided, which preferably as Surface grindings 57 are formed.
- Figures 4 and 5 show two further exemplary embodiments of the fuel injector for those to limit the Opening stroke movement of the valve member 11 different mechanical Stroke stops are provided.
- 4 shows this a third embodiment in which the stroke stop for the valve member 11 as a ring shoulder 59 on the lateral surface of the Pin 9 of the insert body 7 is formed. To this Ring shoulder surface 59 comes after the valve member 11 Pass through its total opening stroke with the ring face 29 in annex.
- control room 37 is filled between the pin 9 and the closed end face 33 the guide bore 13 in the valve member 11 now directly the pressure chamber 21, for which purpose a throttle bore 61 in the valve member 11 is provided, starting from the control room 37 on the Shell surface of the valve member 11 opens into the pressure chamber 21.
- the fourth exemplary embodiment shown in FIG. 5 differs from the third shown in FIG. 4 Embodiment only in the nature of the stroke stop for limiting the opening stroke movement of the valve member 11.
- the opening stroke of the valve member 11 is now by the abutment of the end face 33 of the bore 13 in the valve member 11 on the end face 35 of the pin 9 on the insert body 7 limited.
- the annular end face 35 of the pin 9 for this purpose has an axially inwardly offset shoulder 63, the retention of the end face acting in the closing direction 33 guaranteed on the valve member 11. In this way can when closing the discharge line 45 by the Control valve 47 at the end of the injection phase and the renewed Filling the control room 37 with high pressure fuel the return movement of the valve member via the throttle bore 61 11 guaranteed securely to the valve seat 19 stay.
- the opening stroke of the valve member 11 can be thereby in a simple manner over the axial length of the stationary adjust the arranged insert body 7.
- the control room 37 compared to the previous ones Embodiments arranged outside the valve member 11.
- the valve member 11 is analogous to the second embodiment both inside the guide bore 13 as also guided outside on the peripheral wall 53 of the valve member 11.
- a between the rear ring face 29 am Valve member 11 and between the paragraph 31 on the stationary insert body 7 formed space forms in the fifth embodiment the control room 137, in which the return spring 27 is arranged.
- hydraulic work space 65 The between the End face 35 of the pin 9 and the closed end face 33 of the bore 13 enclosed on the valve member 11 hydraulic work space 65 is again a Through hole 39 and a high pressure line 43 with fuel high pressure from a high-pressure fuel tank filled. This leads from the hydraulic working space 65 a connecting bore 67 from the near a valve seat Space opens within the valve body 1.
- the high pressure fuel supply of control room 137 takes place via a throttle bore 41 which from the through hole 39 in Insert body 7 opens into the control room 137.
- the opening stroke movement of the valve member 11 takes place at fifth embodiment by relieving the pressure external control room 137 via the relief channel 64 and the relief line 45.
- the end face acts 33 within the valve member 11 with its diameter d3 continues in the closing direction of the valve member 11. That is due to the difference in diameter between the outer circumference of the valve member 11 (d2) and the diameter at the seat edge 17 (d1) formed in the opening direction on the valve member 11 attacking hydraulic pressure area must be larger be formed than that now only in the closing direction end face 33 acting on the valve member 11.
- the closing stroke movement of the valve member 11 is carried out analogously to the previous ones Embodiments by reclosing the relief line 45, as a result of which Control chamber 137 again through the throttle bore 41 a high fuel pressure builds up the valve member 11 on the ring end face 29 in addition to the end face 33 in the closing direction acted upon and thus the valve member 11 in contact the valve seat 19 moves back.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
Description
Claims (15)
- Kraftstoffeinspritzventil für Brennkraftmaschinen mit einem in einem Ventilkörper (1) angeordneten, axial verschiebbaren Ventilglied (11), das an seinem dem Brennraum der Brennkraftmaschine zugewandten Ende eine konische Ventildichtfläche (15) aufweist, mit der es mit einer konischen Ventilsitzfläche (19) am Ventilkörper (1) zusammenwirkt, wobei die konische Ventildichtfläche (15) am Ventilglied (11) eine eine Dichtkante (17) bildende Ringkante aufweist, sowie mit wenigstens einer Einspritzöffnung (25) in den Brennraum der Brennkraftmaschine in dem sich bei geschlossenem Einspritzventil stromabwärts an die Dichtkante (17) anschließenden Bereich der Ventilsitzfläche (19), dadurch gekennzeichnet, daß das Ventilglied (11) eine Führungsbohrung (13) aufweist, mit der es gleitverschiebbar auf einem Zapfen (9) eines ortsfesten Einsatzkörpers (7) geführt ist.
- Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, daß im Ventilkörper (1) ein an die Ventilsitzfläche (19) mündender Hochdruckraum (21) gebildet ist, der ständig über eine Hochdruckleitung (43) mit einem mit Kraftstoff hohen Druckes gefüllten Hochdruckspeicherraum verbunden ist.
- Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, daß zwischen einer geschlossenen Stirnfläche (33) der Führungsbohrung (13) im Ventilglied (11) und einer Stirnfläche (35) des Zapfens (9) des Einsatzkörpers (7) ein Arbeitsraum begrenzt ist, der aus dem Hochdruckraum (21) oder der Hochdruckleitung (43) mit Kraftstoff hohen Druckes befüllbar ist.
- Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, daß ein mit Kraftstoffhochdruck befüllbarer Steuerraum (37, 137) im Ventilkörper (1) vorgesehen ist, dessen Innendruck das Ventilglied (11) in Schließrichtung beaufschlagt und der über eine aufsteuerbare Entlastungsleitung (45) in einen Niederdruckraum druckentlastbar ist.
- Kraftstoffeinspritzventil nach Anspruch 4, dadurch gekennzeichnet, daß ein von außen betätigbares Steuerventil (47) in die Entlastungsleitung (45) eingesetzt ist.
- Kraftstoffeinspritzventil nach den Ansprüchen 3 und 4, dadurch gekennzeichnet, daß der Steuerraum (37) durch den Arbeitsraum zwischen den Stirnflächen (33) am Ventilglied (11) und (35) am Zapfen (9) gebildet ist.
- Kraftstoffeinspritzventil nach Anspruch 6, dadurch gekennzeichnet, daß der Steuerraum (37) über einen, eine Drosselstelle (41) enthaltenen Zulaufkanal mit der Hochdruckleitung (43) oder dem Hochdruckraum (21) verbunden ist.
- Kraftstoffeinspritzventil nach Anspruch 4, dadurch gekennzeichnet, daß der Steuerraum (137) radial auswärts des Zapfens (9) des ortsfesten Einsatzkörpers (7) angeordnet ist und von der brennraumabgewandten Ringstirnfläche (29) des Ventilgliedes (11) begrenzt wird.
- Kraftstoffeinspritzventil nach Anspruch 8, dadurch gekennzeichnet, daß der Steuerraum (137) über eine Drosselbohrung (41) ständig mit der Hochdruckleitung (43) und über eine zusteuerbare Entlastungsleitung (45) mit einem Niederdruckraum verbindbar ist.
- Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, daß zwischen dem Ventilglied (11) und dem Einsatzkörper (7) eine, das Ventilglied (11) in Schließrichtung beaufschlagende Rückstellfeder (27) eingespannt ist.
- Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, daß das Ventilglied (11) durch eine Hülse (49) gebildet ist, in deren brennraumzugewandte Öffnung ein Kopfstück (51) eingesetzt ist, an dessen der Hülse (49) abgewandter Stirnseite die Ventildichtfläche (15) angeordnet ist.
- Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, daß der Öffnungshubweg des Ventilgliedes (11) durch einen Hubanschlag begrenzt ist.
- Kraftstoffeinspritzventil nach Anspruch 12, dadurch gekennzeichnet, daß der Hubanschlag durch einen Ringabsatz (59) am zylindrischen Zapfen (9) des Einsatzkörpers (7) gebildet ist.
- Kraftstoffeinspritzventil nach Anspruch 12, dadurch gekennzeichnet, daß der Hubanschlag durch einen an der ventilgliedseitigen Ringstirnfläche (35) des Zapfens (9) des Einsatzkörpers (7) gebildet ist.
- Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, daß das Ventilglied (11) zusätzlich mit seiner radialen Mantelfläche (53) an der Innenwand (55) des Ventilkörpers (1) geführt ist, wobei Durchtrittskanäle (57, 67) für einen Kraftstoffdurchtritt am Ventilglied (11) vorgesehen sind.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19744518A DE19744518A1 (de) | 1997-10-09 | 1997-10-09 | Kraftstoffeinspritzventil für Brennkraftmaschinen |
DE19744518 | 1997-10-09 | ||
PCT/DE1998/001628 WO1999019619A1 (de) | 1997-10-09 | 1998-06-16 | Kraftstoffeinspritzventil für brennkraftmaschinen |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0943054A1 EP0943054A1 (de) | 1999-09-22 |
EP0943054B1 true EP0943054B1 (de) | 2002-09-18 |
Family
ID=7844994
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP98936173A Expired - Lifetime EP0943054B1 (de) | 1997-10-09 | 1998-06-16 | Kraftstoffeinspritzventil für brennkraftmaschinen |
Country Status (5)
Country | Link |
---|---|
US (1) | US6247452B1 (de) |
EP (1) | EP0943054B1 (de) |
JP (1) | JP2001506345A (de) |
DE (2) | DE19744518A1 (de) |
WO (1) | WO1999019619A1 (de) |
Families Citing this family (25)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6626371B1 (en) | 1997-10-09 | 2003-09-30 | Robert Bosch Gmbh | Common rail injector |
DE19936669A1 (de) * | 1999-08-04 | 2001-02-22 | Bosch Gmbh Robert | Common-Rail-Injektor |
US6770564B1 (en) * | 1998-07-29 | 2004-08-03 | Denso Corporation | Method of etching metallic thin film on thin film resistor |
DE19933328A1 (de) * | 1999-07-16 | 2001-01-25 | Bosch Gmbh Robert | Common-Rail-Injektor |
DE19945314A1 (de) * | 1999-09-22 | 2001-04-05 | Bosch Gmbh Robert | Common-Rail-Injektor |
DE19949526A1 (de) * | 1999-10-14 | 2001-04-19 | Bosch Gmbh Robert | Injektor für ein Common-Rail-Kraftstoffeinspritzsystem für Brennkraftmaschinen mit teilweisem Kraftausgleich der Düsennadel |
DE19949527A1 (de) * | 1999-10-14 | 2001-04-19 | Bosch Gmbh Robert | Injektor für ein Kraftstoffeinspritzsystem für Brennkraftmaschinen mit in den Ventilsteuerraum ragender Düsennadel |
JP4048699B2 (ja) * | 1999-11-10 | 2008-02-20 | 株式会社デンソー | 燃料噴射弁 |
IT1319988B1 (it) * | 2000-03-21 | 2003-11-12 | Fiat Ricerche | Spina di chiusura di un ugello in un iniettore di combustibile permotori a combustione interna. |
DE10031571A1 (de) * | 2000-06-29 | 2002-01-17 | Bosch Gmbh Robert | Injektor mit zentralem Hochdruckanschluß |
DE10031573A1 (de) * | 2000-06-29 | 2002-01-17 | Bosch Gmbh Robert | Hochdruckfester Injektor zur Kraftstoffeinspritzung in Kompaktbauweise |
DE10036868B4 (de) * | 2000-07-28 | 2004-07-29 | Robert Bosch Gmbh | Injektor für ein einen Hochdrucksammelraum umfassendes Einspritzsystem |
DE10115215A1 (de) * | 2001-03-28 | 2002-10-10 | Bosch Gmbh Robert | Kraftstoffeinspritzventil für Brennkraftmaschinen |
DE10131618A1 (de) | 2001-06-29 | 2003-01-23 | Bosch Gmbh Robert | Kraftstoffinjektor mit zuschaltbarem Steuerraumzulauf |
DE10131617A1 (de) | 2001-06-29 | 2003-01-23 | Bosch Gmbh Robert | Kraftstoffinjektor-Schaltventil zur Druckentlastung/Belastung eines Steuerraumes |
DE10131642A1 (de) | 2001-06-29 | 2003-01-16 | Bosch Gmbh Robert | Kraftstoffinjektor mit variabler Steuerraumdruckbeaufschlagung |
DE10132248C2 (de) * | 2001-07-04 | 2003-05-28 | Bosch Gmbh Robert | Kraftstoffinjektor mit 2-Wege-Ventilsteuerung |
US7278593B2 (en) * | 2002-09-25 | 2007-10-09 | Caterpillar Inc. | Common rail fuel injector |
DE102004032181A1 (de) | 2004-07-02 | 2006-01-19 | Robert Bosch Gmbh | Kraftstoffeinspritzventil |
US7441546B2 (en) * | 2005-07-28 | 2008-10-28 | Denso Corporation | Valve apparatus |
DE102007004553A1 (de) * | 2007-01-30 | 2008-07-31 | Robert Bosch Gmbh | Kugelsitzventil mit verringertem Erosionsverhalten |
CA2695961C (en) | 2007-08-14 | 2013-05-21 | Graphic Packaging International, Inc. | Cartons, packages, blanks, and containers having dispensing and opening features |
CN102305162A (zh) * | 2011-08-19 | 2012-01-04 | 中国兵器工业集团第七○研究所 | 柴油机的喷油嘴偶件 |
JP5677329B2 (ja) | 2012-01-20 | 2015-02-25 | 日立オートモティブシステムズ株式会社 | 電磁駆動型の吸入弁を備えた高圧燃料供給ポンプ |
US10415527B2 (en) * | 2015-01-30 | 2019-09-17 | Hitachi Automotive Systems, Ltd. | Fuel injection valve |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CH494346A (de) * | 1968-07-31 | 1970-07-31 | Sulzer Ag | Elektromagnetisch gesteuertes Brennstoffeinspritzventil einer Kolbenbrennkraftmaschine |
CH495504A (de) * | 1968-08-28 | 1970-08-31 | Sopromi Soc Proc Modern Inject | Brennstoff-Einspritzventil mit elektromagnetischer Betätigung |
NL133905C (de) * | 1968-11-05 | |||
FR2068857A5 (de) * | 1969-10-24 | 1971-09-03 | Sofredi | |
US4156560A (en) * | 1977-11-09 | 1979-05-29 | The United States Of America As Represented By The Secretary Of The Army | Electrically-controlled fuel injector |
US4342427A (en) * | 1980-07-21 | 1982-08-03 | General Motors Corporation | Electromagnetic fuel injector |
AT378242B (de) * | 1981-07-31 | 1985-07-10 | Berchtold Max Prof | Kraftstoffeinspritzanlage fuer brennkraftmaschinen, insbesondere dieselmotoren |
IT212432Z2 (it) | 1987-08-25 | 1989-07-04 | Weber Srl | Valvola di iniezione del combustibile a comando elettromagnetico per motori a ciclo diesel |
US5409165A (en) * | 1993-03-19 | 1995-04-25 | Cummins Engine Company, Inc. | Wear resistant fuel injector plunger assembly |
DE4340305C2 (de) * | 1993-11-26 | 1998-02-19 | Daimler Benz Ag | Kraftstoffeinspritzdüse für eine Brennkraftmaschine |
ATE184078T1 (de) * | 1994-06-06 | 1999-09-15 | Ganser Hydromag | Brennstoffeinspritzventil für verbrennungskraftmaschinen |
-
1997
- 1997-10-09 DE DE19744518A patent/DE19744518A1/de not_active Withdrawn
-
1998
- 1998-06-16 EP EP98936173A patent/EP0943054B1/de not_active Expired - Lifetime
- 1998-06-16 WO PCT/DE1998/001628 patent/WO1999019619A1/de active IP Right Grant
- 1998-06-16 DE DE59805604T patent/DE59805604D1/de not_active Expired - Lifetime
- 1998-06-16 JP JP52073099A patent/JP2001506345A/ja not_active Ceased
- 1998-06-16 US US09/319,533 patent/US6247452B1/en not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
DE59805604D1 (de) | 2002-10-24 |
WO1999019619A1 (de) | 1999-04-22 |
JP2001506345A (ja) | 2001-05-15 |
EP0943054A1 (de) | 1999-09-22 |
US6247452B1 (en) | 2001-06-19 |
DE19744518A1 (de) | 1999-04-15 |
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