EP1062423B1 - Soupape d'injection de carburant - Google Patents
Soupape d'injection de carburant Download PDFInfo
- Publication number
- EP1062423B1 EP1062423B1 EP99964369A EP99964369A EP1062423B1 EP 1062423 B1 EP1062423 B1 EP 1062423B1 EP 99964369 A EP99964369 A EP 99964369A EP 99964369 A EP99964369 A EP 99964369A EP 1062423 B1 EP1062423 B1 EP 1062423B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- transition region
- fuel injection
- upstream
- sealing
- 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
- 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
- F02M59/46—Valves
-
- 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
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
- F02M2200/304—Fuel-injection apparatus having mechanical parts, the movement of which is damped using hydraulic means
Definitions
- the invention relates to a fuel injection valve for internal combustion engines according to the preamble of the patent claim 1.
- fuel injectors are for example from DE 195 47 423 A1 and DE 196 34 133 A1 known.
- valves In such fuel injection valves is a piston-shaped one Valve member axially displaceable in one Drilled bore of a valve body.
- the valve member has a conical end on the combustion chamber side Valve sealing surface with which it is conical Valve seat surface cooperates on the valve body, at the inwardly projecting end of the closed valve bore is formed.
- the valve sealing surface on the valve member is in several, preferably two areas divided different cone angles, one Transition area between the two valve sealing surface areas is provided by a downstream side and an upstream valve sealing edge is limited.
- the valve member is elastically equal under the valve closing force to the nozzle body.
- the resulting one hydraulically effective seat diameter is in in this case arranged undefined in the transition area, as shown schematically in Fig. 1. Due to the inverse seat angle difference Pressure distribution at the offset from the axial direction A valve member, which the valve member back into the centric, axial position pushes back. In contrast to would look at a fuel injector without an inverse Seat angle difference set a pressure distribution, through which the valve member further from the centric, axial position would be moved.
- the invention has for its object a fuel injection itzventil of the generic type such further that it by axial alignment of the Valve member a symmetrical spray pattern and above a defined hydraulically effective seat diameter, a high damping of the valve member and enables the lowest possible risk of cavitation.
- the distance between the upstream valve sealing edge and the downstream valve sealing edge the transition area is chosen so that the upstream valve sealing edge of the transition area forms the hydraulically effective seat diameter.
- the distance can be determined by test measurements and / or Bills can be determined.
- a fuel injector shown in FIGS. 1 to 3 for internal combustion engines has a cylindrical valve body 1 on with its free lower End in a combustion chamber, not shown protrudes with fuel to be supplied to the internal combustion engine.
- An axial blind bore 3 is provided in the valve body 1, in which a piston-shaped valve member 5 axially is slidably guided.
- the valve member 5 instructs a conical valve sealing surface at its lower end near the combustion chamber 7 with which it is used to control a Injection cross section with a conical valve seat 9 at the combustion chamber end of the valve body 1 interacts with the closed cantilever End of the bore 3 is formed and from the injection openings 6 in the combustion chamber of the internal combustion engine out.
- the valve sealing surface 7 is like 3, in particular, in an upper region 71 and divided into a lower area. Between the upper area 71 and the lower area 72 a transition region 73 is formed. The angle that from the difference between transition area 73 and Valve seat surface 9 results must be smaller than that Angle resulting from the difference between valve seat area 9 and the lower area 72 results (inverse Seat angle difference). Adjacent to the downstream side Area 72 are injection openings in the valve body 1 20 provided.
- the upstream side Area 71 of the valve sealing surface has a radial, undercut-shaped recess 74. This forms a space formed by one on the valve body 1 Edge 75 is limited upstream.
- the transition region 73 is marked by an upstream Valve sealing edge 73a and a downstream side Valve sealing edge 73b limited, which is adjacent are arranged to each other that the hydraulic effective seat diameter during a closing process the upstream valve sealing edge 73a coincides. Because of this defined hydraulically effective Seat diameter becomes a resulting radial Prevents force on the valve member, which in the Fig. 1 shown undefined hydraulic effective seat diameter 90 occurs.
- the design of the distance between the two valve sealing edges 73a and 73b will be experimental and based determined by bills. With a maximum closing force of 1250 N, which are determined experimentally can result, for example, in a difference in diameter of approximately 0.15 mm with a geometric seat diameter of 2 mm. With this minimal transition area, i.e. with this minimal seating area is in any case guaranteed that the hydraulic effective seat diameter exactly with the valve sealing edge 73a coincides.
- the angle that the Damping room includes, chosen so that it is larger is than the body seat angle. In this way it is created in the closed state a damping room that one Effect similar to that of a sail Pressure cushion generated when the valve member 5 is closed, that increases the damping of the valve member 5.
- the fuel injector will close the fuel arranged in the damping space displaces and flows over between the valve member 5 and the edge 75 formed upstream gap from the damping room. The damping effect is due to the flow resistance generated by the gap generated during the closing process.
- the upstream side Edge 75 is designed so that it in Extreme case with complete deformation of the valve member has no distance from the valve body 5. Out this damping results in a lower tip load.
- Such a fuel injection valve also has the advantage that the bladder collapse of the cavitation bubbles preferably in the area upstream of the edge 75 takes place because the originating from the injection pump Pressure waves through edge 75 from the transition area be kept away. This does not cause damage the seating area.
- valve holding body (not shown) tends to an opening pressure drop, whereas the valve member 5 due to the inverse seat angle difference to an increase in opening pressure tends. Opposing effects occur that partially cancel each other out. hereby the service life of the fuel injector increases.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
Claims (2)
- Injecteur de carburant pour moteurs à combustion interne comprenant un élément de soupape (5) pouvant coulisser axialement dans un perçage (3) d'un corps de soupape (1) et qui présente à son extrémité dirigée vers la chambre de combustion du moteur à combustion interne une surface d'étanchéité de soupape conique (7) au moyen de laquelle il coopère avec une surface de siège de soupape conique (9) prévue à l'extrémité fermée, côté chambre de combustion, du perçage (3) du corps de soupape (1), la surface d'étanchéité de soupape conique (7) sur l'élément de soupape (5) étant divisée en deux régions (71, 72) qui présentent des angles de cône différents et à la transition desquelles est formée une région de transition (73), limitée par des arêtes d'étanchéité de soupape côté amont et côté aval (73a et 73b), la différence entre l'angle de cône de la région de transition (73) et celui de la surface de siège de soupape (9) étant plus petite que la différence entre l'angle de cône de la région côté aval (72) et celui de la surface de siège de soupape (9),
caractérisé en ce qu'
à la région de transition (73) fait suite, vers l'amont, un évidement radial (74) formé dans l'élément de soupape (5), limité par l'arête d'étanchéité côté amont (73a) de la région de transition (73) et par une arête (75) formée sur le corps de soupape (1). - Injecteur de carburant selon la revendication 1,
caractérisé en ce que
les arêtes d'étanchéité de soupape (73a, 73b) qui limitent la région de transition (73) sont rapprochées si étroitement l'une de l'autre que l'arête d'étanchéité de soupape côté amont (73a) forme un diamètre de portée à effet hydraulique.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19901057 | 1999-01-14 | ||
DE19901057A DE19901057A1 (de) | 1999-01-14 | 1999-01-14 | Kraftstoffeinspritzventil für Brennkraftmaschinen |
PCT/DE1999/003723 WO2000042316A1 (fr) | 1999-01-14 | 1999-11-24 | Soupape d'injection de carburant |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1062423A1 EP1062423A1 (fr) | 2000-12-27 |
EP1062423B1 true EP1062423B1 (fr) | 2004-08-11 |
Family
ID=7894152
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP99964369A Expired - Lifetime EP1062423B1 (fr) | 1999-01-14 | 1999-11-24 | Soupape d'injection de carburant |
Country Status (6)
Country | Link |
---|---|
US (1) | US6502554B1 (fr) |
EP (1) | EP1062423B1 (fr) |
JP (1) | JP4587248B2 (fr) |
KR (1) | KR100631298B1 (fr) |
DE (2) | DE19901057A1 (fr) |
WO (1) | WO2000042316A1 (fr) |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10050600A1 (de) * | 2000-10-12 | 2002-04-25 | Siemens Ag | Injektor für eine Kraftstoffeinspritzanlage |
DE10105681A1 (de) * | 2001-02-08 | 2002-08-29 | Siemens Ag | Kraftstoffeinspritzventil für eine Brennkraftmaschine |
ATE325271T1 (de) | 2003-10-06 | 2006-06-15 | Delphi Tech Inc | Einspritzdüse |
DE10359302A1 (de) * | 2003-12-17 | 2005-07-21 | Robert Bosch Gmbh | Ventilkörper mit Mehrfachkegelgeometrie am Ventilstitz |
JP2006307678A (ja) * | 2005-04-26 | 2006-11-09 | Denso Corp | 燃料噴射ノズル |
US20070200011A1 (en) * | 2006-02-28 | 2007-08-30 | Caterpillar Inc. | Fuel injector having nozzle member with annular groove |
EP2969318B1 (fr) * | 2013-03-15 | 2018-07-25 | Schott Corporation | Composite verre-métal |
Family Cites Families (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1952816A (en) * | 1931-04-04 | 1934-03-27 | Bendix Res Corp | Fuel injector |
JPS6058868U (ja) * | 1983-09-30 | 1985-04-24 | いすゞ自動車株式会社 | バルブシ−ト型燃料噴射ノズル |
JPS60169664A (ja) * | 1984-02-14 | 1985-09-03 | Mitsui Eng & Shipbuild Co Ltd | 超高圧燃料噴射弁 |
SE448828B (sv) * | 1985-06-07 | 1987-03-23 | Ingemanssons Ingenjorsbyra Ab | Munstycke |
JPH0158770U (fr) * | 1987-10-07 | 1989-04-12 | ||
JP2819702B2 (ja) * | 1989-12-12 | 1998-11-05 | 株式会社デンソー | 燃料噴射弁 |
US5020500A (en) * | 1990-03-28 | 1991-06-04 | Stanadyne Automotive Corp. | Hole type fuel injector and injection method |
US5159911A (en) * | 1991-06-21 | 1992-11-03 | Cummins Engine Company, Inc. | Hot start open nozzle fuel injection systems |
FI88333C (fi) * | 1991-06-25 | 1993-04-26 | Waertsilae Diesel Int | Foerbaettrat insprutningsventilarrangemang foer braensle |
US5288025A (en) * | 1992-12-18 | 1994-02-22 | Chrysler Corporation | Fuel injector with a hydraulically cushioned valve |
US5449121A (en) * | 1993-02-26 | 1995-09-12 | Caterpillar Inc. | Thin-walled valve-closed-orifice spray tip for fuel injection nozzle |
US5647536A (en) * | 1995-01-23 | 1997-07-15 | Cummins Engine Company, Inc. | Injection rate shaping nozzle assembly for a fuel injector |
DE69626097T2 (de) * | 1995-08-29 | 2003-10-30 | Isuzu Motors Ltd | Kraftstoffeinspritzvorrichtung der speichergattung |
DE19547423B4 (de) * | 1995-12-19 | 2008-09-18 | Robert Bosch Gmbh | Kraftstoffeinspritzventil für Brennkraftmaschinen |
DE19634133C2 (de) | 1996-08-23 | 1999-03-11 | Siemens Ag | Mikroprozessor, insbesondere zur Verwendung in einer Chipkarte, sowie Chipkarte mit einem ebensolchen Mikroprozessor |
DE19822503C1 (de) * | 1998-05-19 | 1999-11-25 | Siemens Ag | Steuerventil für Kraftstoffeinspritzventil |
GB9823028D0 (en) * | 1998-10-22 | 1998-12-16 | Lucas Ind Plc | Fuel injector |
-
1999
- 1999-01-14 DE DE19901057A patent/DE19901057A1/de not_active Withdrawn
- 1999-11-24 JP JP2000593859A patent/JP4587248B2/ja not_active Expired - Fee Related
- 1999-11-24 US US09/646,189 patent/US6502554B1/en not_active Expired - Fee Related
- 1999-11-24 EP EP99964369A patent/EP1062423B1/fr not_active Expired - Lifetime
- 1999-11-24 WO PCT/DE1999/003723 patent/WO2000042316A1/fr active IP Right Grant
- 1999-11-24 KR KR1020007009967A patent/KR100631298B1/ko not_active IP Right Cessation
- 1999-11-24 DE DE59910205T patent/DE59910205D1/de not_active Expired - Lifetime
Also Published As
Publication number | Publication date |
---|---|
JP4587248B2 (ja) | 2010-11-24 |
DE19901057A1 (de) | 2000-07-27 |
JP2002535537A (ja) | 2002-10-22 |
KR20010041733A (ko) | 2001-05-25 |
DE59910205D1 (de) | 2004-09-16 |
WO2000042316A1 (fr) | 2000-07-20 |
EP1062423A1 (fr) | 2000-12-27 |
KR100631298B1 (ko) | 2006-10-09 |
US6502554B1 (en) | 2003-01-07 |
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