WO2004085832A1 - Kraftstoffeinspritzventil für brennkraftmaschinen - Google Patents
Kraftstoffeinspritzventil für brennkraftmaschinen Download PDFInfo
- Publication number
- WO2004085832A1 WO2004085832A1 PCT/DE2003/002817 DE0302817W WO2004085832A1 WO 2004085832 A1 WO2004085832 A1 WO 2004085832A1 DE 0302817 W DE0302817 W DE 0302817W WO 2004085832 A1 WO2004085832 A1 WO 2004085832A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- valve
- annular groove
- injection
- edge
- valve needle
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
- F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
- F02M61/1873—Valve seats or member ends having circumferential grooves or ridges, e.g. toroidal
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
- F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
- F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
- F02M45/08—Injectors peculiar thereto
- F02M45/086—Having more than one injection-valve controlling discharge orifices
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- 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
-
- 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
Definitions
- the invention is based on a fuel injection valve for internal combustion engines, as it corresponds to the preamble of claim 1.
- a fuel injection valve for internal combustion engines, as it corresponds to the preamble of claim 1.
- Such a fuel injection valve is known, for example, from published patent application DE 198 44 638 AI.
- the known fuel injection valve here has a valve body in which a piston-shaped valve needle is guided so as to be longitudinally displaceable in a bore.
- the bore is delimited by a conical valve seat, from which several injection channels extend, which open into the combustion chamber of the internal combustion engine when the fuel injection valve is in the installed position.
- the inlet openings of the injection channels are at the same height with respect to the longitudinal axis of the bore.
- the valve needle At its end on the combustion chamber side facing the valve seat, the valve needle has an essentially conical valve sealing surface, which comprises a first conical surface and a second conical surface arranged downstream thereof. Between the two conical surfaces, a sealing edge is formed, with which the valve needle interacts with the valve seat in its closed position, so that when the valve needle rests on the valve seat, the fuel flow from the pressure chamber to the injection channels is interrupted, the pressure chamber between the valve needle and the wall of the Bore is formed.
- the known fuel injection valve has an annular groove on the valve sealing surface, which is at least in the closed position.
- the valve needle covers the inlet openings of the injection channels. This favors the inflow of the fuel into the injection channels on the one hand by the fact that the fuel is distributed evenly over the individual injection channels, even if the valve needle is slightly offset with respect to the valve seat. On the other hand, fluctuations that occur due to a different degree of rounding at the transition of the valve seat into the injection channels have less of an impact through the annular groove, since the fuel inlet is throttled.
- the known fuel injection valve has the disadvantage, however, that the annular groove has a relatively large volume and fuel can thus enter the combustion chamber of the internal combustion engine from the injection channels even when the valve needle is closed, which leads to increased hydrocarbon emissions from the internal combustion engine.
- the fuel injection valve according to the invention with the characterizing features of patent claim 1 has the advantage that the inflow of fuel into the injection channels is unthrottled without negative effects on the hydrocarbon emissions of the internal combustion engine.
- a circumferential, first annular groove is formed on the second conical surface of the valve needle and runs in a radial plane with respect to the longitudinal axis of the valve needle.
- the circumferential first annular groove has an upstream edge and a downstream edge, the downstream edge running in the closed position of the valve needle to the height of the inlet openings of the injection channels.
- the groove can also compensate for fluctuations that result from the fact that the transition from the valve seat to the injection channels is usually rounded, but this cannot be reproduced exactly the same on all injection channels. For this reason, the different injection channels at the inlet openings generally have slightly different rounding radii, which are compensated for by the first annular groove, which brings about the same inlet conditions for all injection channels.
- the width of the first annular groove is smaller than the diameter of the inlet openings of the injection channels.
- the upstream and / or the downstream edge of the first annular groove is rounded. This configuration of the annular grooves further facilitates and dethrottles the flow of fuel into the injection channels.
- the upstream edge of the first annular groove is designed as a sealing edge with which the valve needle seals when it rests on the valve seat.
- This sealing function is additionally carried out by the first Ring groove reinforced, because in this case a higher surface pressure occurs in this area.
- a second annular groove is formed in the second conical surface of the valve needle, which is arranged downstream of the first annular groove and is parallel to the latter, and the downstream edge of the inlet openings lies within the second annular groove.
- the inflow of fuel is also throttled at the downstream edge of the inlet opening of the injection channel, so that the flow through the second annular groove is further favored. It is particularly advantageous here if a conical area remains between the first annular groove and the second annular groove, the height of which is smaller than the diameter of the inlet openings of the injection channels.
- Another fuel injector which is a variant of the same solution idea, has the same advantages as the injector according to claim 1.
- a circumferential body ring groove is formed in the valve seat, which runs in a radial plane with respect to the longitudinal axis of the bore and which has an upstream edge and a downstream edge, the downstream edge running through the inlet openings of the injection channels.
- the dethrottling effect of this body ring groove is the same as the dethrottling effect of the first ring groove in the second conical surface of the valve needle, but here the valve needle can be left in its original shape.
- the width of the annular groove is smaller than the diameter of the inlet openings of the injection channels. As a result, only a small volume is created. det, but reliably dethrottled the inlet of the fuel into the injection channels. It is particularly advantageous here if the upstream edge and / or the downstream edge of the annular groove is rounded. It can also be provided here that a second annular groove is formed in the second conical surface of the valve needle, which is arranged downstream of the annular groove in the valve seat and is parallel to the latter, the downstream edge of the inlet openings being located within the second annular groove.
- FIG. 1 shows a longitudinal section through a fuel injection valve
- FIG. 2 shows an enlargement of FIG. 1 in the area of the valve seat
- FIG. 3 shows the same view as FIG. 2 of a further exemplary embodiment
- FIG. 4 shows another exemplary embodiment, which is shown here in an enlarged detail of the valve seat area
- FIG another embodiment in the same
- FIG. 1 shows a longitudinal section through a fuel injection valve according to the invention.
- the fuel injection valve comprises a valve body 1 which, in the installed position of the fuel injection valve in an internal combustion engine, projects into a combustion chamber 8 with its end on the combustion chamber side.
- the Ven TililITY 1 is pressed by means of a clamping nut 2 with the interposition of a throttle body 4 against a holding body 6, wherein the clamping nut 2 engages with an internal thread, not shown in the drawing, in a corresponding external thread of the holding body 6.
- a bore 3 is formed in the valve body 1, which widens away from the combustion chamber to form a spring chamber 22.
- the bore 3 is delimited by a conical valve seat 13, a plurality of injection channels 11 being formed at the end of the valve body 1 on the combustion chamber side, which open into the combustion chamber 8 of the internal combustion engine.
- a piston-shaped valve needle 5 is arranged to be longitudinally displaceable, which has a longitudinal axis 7 and which is guided in a central section of the bore 3.
- the valve needle 5 has at its end on the combustion chamber side an essentially conical valve sealing surface 9 with which the valve needle 5 interacts with the valve seat 13.
- a pressure chamber 20 is formed between the wall of the bore 3 and the valve needle 5, which opens into the spring chamber 22, facing away from the combustion chamber, and via which fuel flows from the spring chamber 22 to the injection openings 11.
- the interaction of the valve sealing surface 9 with the valve seat 13 takes place in such a way that when the valve needle 5 is in contact with the valve seat 13, the fuel flow from the pressure chamber 20 to the injection openings 11 is interrupted, while when the valve needle 13 is lifted from the valve seat 13, fuel is between the valve sealing surface 9 and flows through the valve seat 13 to the injection openings 11.
- the fuel flow from the spring chamber 22 to the injection openings 11 is conducted in the region in which the valve needle 5 is guided in the bore 3 through a plurality of cuts 17 which form a sufficient flow cross section.
- a sleeve 24 is arranged in the spring chamber 22, which surrounds the end of the valve needle 5 facing away from the combustion chamber and abuts the throttle body 4.
- a control chamber 26 is delimited by the end face 32 of the valve needle 5 facing away from the combustion chamber, the sleeve 24 and the throttle body 4, said control chamber being connected to the spring chamber 22 via an inlet throttle 34 formed in the sleeve 24.
- the control chamber 26 can be connected via a discharge throttle 36, which is formed in the throttle body 4, to a leakage oil chamber (not shown in the drawing), the connection being closable by means of a control valve 14.
- a closing spring 28 is arranged, which is supported at one end on the sleeve 24 and at the other end on a spring plate 30 surrounding the valve needle 5, the closing spring 28 having a prestress.
- the prestressing of the closing spring 28 results in a force on the spring plate 30 and thus, since the spring plate 30 is supported on the valve needle 5, also on the valve needle 5, so that the valve needle 5 with the valve sealing surface 9 is pressed against the valve seat 13.
- the fuel injection is controlled in such a way that at the beginning of an injection cycle the control valve 14 closes the outlet throttle 36, so that the same pressure prevails in the control chamber 26 via the inlet throttle 34 as in the spring chamber 22, which results in a hydraulic force on the end face 32 of the valve needle 5 causes this presses against the valve seat 13 so that the injection channels 11 are closed.
- the control valve 14 opens the discharge throttle 36, which causes a pressure drop in the control chamber 26.
- the hydraulic forces on the pressure shoulder 15 and on parts of the valve sealing surface 9 now predominate, so that the valve needle 5 lifts off the valve seat 13 and fuel from the pressure chamber 20 to the Injection channels 11 flows.
- the control valve 14 By actuating the control valve 14 again, the high fuel pressure in the control chamber 26 builds up again, and the valve needle 5 slides back into its closed position.
- FIG 2 shows an enlargement of Figure 1 in the section designated II.
- the valve sealing surface 9 of the valve needle 5 comprises a first conical surface 40 and a second conical surface 42 located downstream of it. At the transition from the first conical surface 40 to the second conical surface 42, a sealing edge 45 is formed, which seals the valve needle 5 on the valve seat 13 leads.
- a first annular groove 50 is formed, which runs in a radial plane with respect to the longitudinal axis 7 of the valve needle 5 and which has an upstream edge 51 and a downstream edge 52.
- the downstream edge 52 runs at the level of the inlet openings 16 of the injection channels 11, so that the inflow of the fuel into the injection channels 11 is throttled.
- the inlet opening 16 of the injection channels 11 has a diameter a that is larger than the diameter D of the injection channels 11, which is due to the fact that the upstream end 18 and the downstream end 19 of the inlet opening 16 also coexist at the transition from the injection channel 11 to the valve seat 13 are rounded to a radius R.
- the fuel If the fuel flows from the pressure chamber 20 past the sealing edge 45 between the second conical surface 42 and the valve seat 13 to the injection channels 11, the fuel must undergo a major change in direction when it flows into the injection channel 11. This normally leads to a strong loss of energy and thus to a correspondingly reduced injection pressure in the injection channel 11.
- the rounding radius R at the inlet opening 16 can somewhat alleviate this effect, but it does still present and leads to a reduced injection pressure.
- the inflow of the fuel into the injection channel 11 is throttled by the first annular groove 50, so that the speed of the fuel in the injection channel 11 is higher and thus a correspondingly higher effective injection pressure is present.
- a second annular groove 53 is formed on the second conical surface 42 parallel to the first annular groove 50, which also has an upstream edge 54 and a downstream edge 55.
- the downstream end 19 of the inlet opening 16 is in the closed position of the valve needle 5 with respect to the longitudinal axis 7 between the upstream edge 54 and the downstream edge 55 of the second annular groove 53. This also favors the second annular groove 53 to allow the fuel to flow into the injection channel 11 at the critical point of the downstream end 19 of the inlet opening 16.
- the reduction in the throttling when the fuel flows into the injection channel 11 is particularly important in the partial stroke range, that is to say when the valve needle 5 has lifted off the valve seat 13 but has not yet reached its maximum stroke.
- the height x of the first annular groove 50 which is approximately equal to the height y of the second annular groove 53, is preferably smaller than the diameter D of the injection channel 11.
- FIG. 3 shows a further exemplary embodiment of the fuel injection valve according to the invention, the section only showing the left half.
- the formation of the ring grooves 50, 53 on the second cone surface 42 is somewhat different from the arrangement as shown in FIG. 2: the first ring groove 50 adjoins the sealing edge 45 directly, so that the first cone surface 40 does not directly adjoin the second conical surface 42 borders.
- the inlet openings 16 are arranged such that the same arrangement of the inlet opening 16 or of the injection channel 11 is given to the first annular groove 50 and to the second annular groove 53.
- FIG. 4 shows the same detail as FIG.
- the valve needle 5 here has only the second annular groove 53 on the second cone surface 42, while the first annular groove 50 is omitted.
- a body ring groove 57 is formed in the valve seat 13, which runs in the closed position of the valve needle 5 at approximately the same height with respect to the longitudinal axis 7 as the first ring groove 50 in the exemplary embodiment shown in FIG. 2 when the valve needle 5 rests on the valve seat 13
- the inflow of fuel into the injection channel 11 is throttled by the body ring groove 57 as well as by the first ring groove 50 in the exemplary embodiment shown in FIG the inlet openings 16 are not changed by the stroke of the valve needle 5.
- a longitudinal groove 56 can also be provided on the second conical surface 42, which connects the second annular groove 53 to the volume between the end surface on the combustion chamber side 47 of the valve needle 5 and the valve body 1 is formed. This pressure relief of the second annular groove 53 additionally favors the dethrottling of the inflow into the injection channel 11.
- the upstream edge 58 and the downstream edge 59 of the body ring groove 57 can be rounded in order to optimize the dethrottling, since sharp edges can easily lead to a flow separation and thus to an increased flow resistance with a fast fuel flow.
- the distance of the upstream edge 58 of the body ring groove 57 from the sealing edge 45 in the closed position of the valve needle 5 is approximately 0.02 to 0.2 mm.
- FIG. 5 shows a further exemplary embodiment, in which not only a single valve needle is provided, but two valve needles which are guided coaxially one inside the other.
- a valve needle 60 has a first cone surface 63 and a second cone surface 64 at its combustion chamber end, an annular groove 70 being formed in the second cone surface 63.
- the valve needle 60 has a longitudinal bore 61 in which a valve inner needle 62 is arranged to be longitudinally displaceable.
- a conical valve sealing surface 66 in which an annular groove 72 is formed, is formed on the end of the valve inner needle 62 on the combustion chamber side.
- the outer row of injection channels 11a through the valve needle 60 and the inner row Injection channel row 11b is controlled by the valve inner needle 62.
- the annular groove 70 serves here in the same way.
- the inflow of fuel into the downstream injection channel row 11b is throttled by the annular groove 72, which has an upstream edge 73 and a downstream edge 74, the downstream edge 74 at the level of the inlet openings of the inner injection opening row 11b when the valve inner needle 62 is in its closed position.
- the diameter D of the injection channels 11 in all exemplary embodiments is preferably in the range from 80 to 150 ⁇ m, which necessitates a diameter of the ring grooves 50, 53, 57 that is smaller than this diameter of the injection channels 11.
- Such fine ring grooves can preferably be made using a Introduce the laser into the valve needle 5 or into the valve seat 13, since mechanical processing methods generally do not have the necessary precision here.
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
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP03747819A EP1627148A1 (de) | 2003-03-25 | 2003-08-22 | Kraftstoffeinspritzventil für brennkraftmaschinen |
JP2004569830A JP2006514210A (ja) | 2003-03-25 | 2003-08-22 | 内燃機関用の燃料噴射弁 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE2003113225 DE10313225A1 (de) | 2003-03-25 | 2003-03-25 | Kraftstoffeinspritzventil für Brennkraftmaschine |
DE10313225.2 | 2003-03-25 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2004085832A1 true WO2004085832A1 (de) | 2004-10-07 |
Family
ID=32946137
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2003/002817 WO2004085832A1 (de) | 2003-03-25 | 2003-08-22 | Kraftstoffeinspritzventil für brennkraftmaschinen |
Country Status (5)
Country | Link |
---|---|
EP (1) | EP1627148A1 (de) |
JP (1) | JP2006514210A (de) |
CN (1) | CN1759240A (de) |
DE (1) | DE10313225A1 (de) |
WO (1) | WO2004085832A1 (de) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2007100471A1 (en) * | 2006-02-28 | 2007-09-07 | Caterpillar Inc. | Fuel injector having nozzle member with annular groove |
US7578450B2 (en) | 2005-08-25 | 2009-08-25 | Caterpillar Inc. | Fuel injector with grooved check member |
RU2724287C1 (ru) * | 2020-01-10 | 2020-06-22 | Александр Александрович Стуров | Распылитель форсунки для дизельного двигателя внутреннего сгорания |
Families Citing this family (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
TR200402050A2 (tr) * | 2004-08-18 | 2006-03-21 | Robert Bosch Gmbh | Eşeksenli alansal temaslı çift oturma çaplı enjektör |
DE102005020365A1 (de) * | 2005-05-02 | 2006-11-09 | Robert Bosch Gmbh | Ventil, insbesondere Kraftstoffeinspritzventil |
DE102005029024A1 (de) * | 2005-06-22 | 2007-01-04 | Siemens Ag | Düsenbaugruppe |
JP2008057458A (ja) * | 2006-08-31 | 2008-03-13 | Mitsubishi Heavy Ind Ltd | 燃料噴射弁 |
EP2369166B1 (de) * | 2010-03-22 | 2017-12-13 | Delphi International Operations Luxembourg S.à r.l. | Einspritzdüse |
DE102010063355A1 (de) * | 2010-12-17 | 2012-06-21 | Robert Bosch Gmbh | Kraftstoffeinspritzventil für Brennkraftmaschinen |
JP5716788B2 (ja) * | 2013-04-25 | 2015-05-13 | 株式会社デンソー | 燃料噴射弁 |
EP2905457B1 (de) | 2014-01-15 | 2018-08-29 | Continental Automotive GmbH | Ventilanordnung und Flüssigkeitseinspritzdüse für eine Brennkraftmaschine |
DE102014205454A1 (de) * | 2014-03-24 | 2015-09-24 | Robert Bosch Gmbh | Gasinjektor mit Doppelventilnadel |
EP3156640B1 (de) * | 2015-10-14 | 2020-12-30 | Vitesco Technologies GmbH | Düsenkörper für flüssigkeitseinspritzventil und flüssigkeitsinjektor |
FR3057623B1 (fr) * | 2016-10-14 | 2020-12-25 | Delphi Int Operations Luxembourg Sarl | Membre de vanne d'un injecteur de carburant |
Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH04128552A (ja) * | 1990-09-18 | 1992-04-30 | Nissan Motor Co Ltd | 燃料噴射ノズル |
JPH04318277A (ja) * | 1991-04-17 | 1992-11-09 | Nissan Motor Co Ltd | 燃料噴射ノズル |
JPH07259704A (ja) * | 1994-03-24 | 1995-10-09 | Nissan Diesel Motor Co Ltd | 内燃機関の燃料噴射ノズル |
JP2000291515A (ja) * | 1999-02-02 | 2000-10-17 | Toyota Motor Corp | 燃料噴射弁の噴射孔構造 |
DE10020148A1 (de) * | 1999-04-26 | 2000-11-16 | Toyota Motor Co Ltd | Kraftstoffeinspritzdüse |
EP1091117A2 (de) * | 1999-10-06 | 2001-04-11 | Delphi Technologies, Inc. | Kraftstoffeinspritzventil |
DE10109345A1 (de) * | 2000-02-29 | 2001-08-30 | Denso Corp | Kraftstoffeinspritzeinrichtung für einen Verbrennungsmotor |
EP1136693A2 (de) * | 2000-03-21 | 2001-09-26 | C.R.F. Società Consortile per Azioni | Ventilnadel für ein Brennstoffeinspritzventil einer Verbrennungsmaschine |
JP2003120474A (ja) * | 2001-10-15 | 2003-04-23 | Hino Motors Ltd | 燃料噴射ノズル |
-
2003
- 2003-03-25 DE DE2003113225 patent/DE10313225A1/de not_active Withdrawn
- 2003-08-22 CN CN 03826217 patent/CN1759240A/zh active Pending
- 2003-08-22 EP EP03747819A patent/EP1627148A1/de not_active Withdrawn
- 2003-08-22 WO PCT/DE2003/002817 patent/WO2004085832A1/de not_active Application Discontinuation
- 2003-08-22 JP JP2004569830A patent/JP2006514210A/ja not_active Withdrawn
Patent Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH04128552A (ja) * | 1990-09-18 | 1992-04-30 | Nissan Motor Co Ltd | 燃料噴射ノズル |
JPH04318277A (ja) * | 1991-04-17 | 1992-11-09 | Nissan Motor Co Ltd | 燃料噴射ノズル |
JPH07259704A (ja) * | 1994-03-24 | 1995-10-09 | Nissan Diesel Motor Co Ltd | 内燃機関の燃料噴射ノズル |
JP2000291515A (ja) * | 1999-02-02 | 2000-10-17 | Toyota Motor Corp | 燃料噴射弁の噴射孔構造 |
DE10020148A1 (de) * | 1999-04-26 | 2000-11-16 | Toyota Motor Co Ltd | Kraftstoffeinspritzdüse |
EP1091117A2 (de) * | 1999-10-06 | 2001-04-11 | Delphi Technologies, Inc. | Kraftstoffeinspritzventil |
DE10109345A1 (de) * | 2000-02-29 | 2001-08-30 | Denso Corp | Kraftstoffeinspritzeinrichtung für einen Verbrennungsmotor |
EP1136693A2 (de) * | 2000-03-21 | 2001-09-26 | C.R.F. Società Consortile per Azioni | Ventilnadel für ein Brennstoffeinspritzventil einer Verbrennungsmaschine |
JP2003120474A (ja) * | 2001-10-15 | 2003-04-23 | Hino Motors Ltd | 燃料噴射ノズル |
Non-Patent Citations (5)
Title |
---|
PATENT ABSTRACTS OF JAPAN vol. 016, no. 391 (M - 1298) 19 August 1992 (1992-08-19) * |
PATENT ABSTRACTS OF JAPAN vol. 017, no. 144 (M - 1386) 23 March 1993 (1993-03-23) * |
PATENT ABSTRACTS OF JAPAN vol. 1996, no. 02 29 February 1996 (1996-02-29) * |
PATENT ABSTRACTS OF JAPAN vol. 2000, no. 13 5 February 2001 (2001-02-05) * |
PATENT ABSTRACTS OF JAPAN vol. 2003, no. 08 6 August 2003 (2003-08-06) * |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7578450B2 (en) | 2005-08-25 | 2009-08-25 | Caterpillar Inc. | Fuel injector with grooved check member |
WO2007100471A1 (en) * | 2006-02-28 | 2007-09-07 | Caterpillar Inc. | Fuel injector having nozzle member with annular groove |
RU2724287C1 (ru) * | 2020-01-10 | 2020-06-22 | Александр Александрович Стуров | Распылитель форсунки для дизельного двигателя внутреннего сгорания |
Also Published As
Publication number | Publication date |
---|---|
CN1759240A (zh) | 2006-04-12 |
JP2006514210A (ja) | 2006-04-27 |
EP1627148A1 (de) | 2006-02-22 |
DE10313225A1 (de) | 2004-10-07 |
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