WO2001050014A2 - Injektor für ein common-rail-kraftstoffeinspritzsystem mit schiebergesteuertem zulaufkanal und direkter kopplung von steuerkolben und düsennadel - Google Patents
Injektor für ein common-rail-kraftstoffeinspritzsystem mit schiebergesteuertem zulaufkanal und direkter kopplung von steuerkolben und düsennadel Download PDFInfo
- Publication number
- WO2001050014A2 WO2001050014A2 PCT/DE2000/004101 DE0004101W WO0150014A2 WO 2001050014 A2 WO2001050014 A2 WO 2001050014A2 DE 0004101 W DE0004101 W DE 0004101W WO 0150014 A2 WO0150014 A2 WO 0150014A2
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- control piston
- injector
- nozzle needle
- control
- slide
- 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
- 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
-
- 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 is based on an injector for a common rail fuel injection system for internal combustion engines with an injection nozzle having a nozzle needle and with a control chamber divided into three sections by a control piston, the first section and the second section being hydraulically connected via an inlet throttle arranged in the control piston Are connected and the second section is hydraulically connected to a high pressure connection and the third section to an inlet channel.
- the object of the invention is to further improve this known injector, in particular to increase the design options for the course of the pre-injection and main injection.
- the security against leaks in the combustion chamber of the internal combustion engine should be increased.
- an injector for a common rail fuel injection system for internal combustion engines with an injection nozzle having a nozzle needle, with one by a control piston in three Sections divided control chamber, the first section and the second section being hydraulically connected via an inlet throttle arranged in the control piston, the second section being hydraulically connected to a high-pressure connection and the third section being connected to an inlet channel, and wherein the stroke of the nozzle needle and the stroke of the suer piston are coupled together.
- the coupling of the control piston and nozzle needle enables pre-injections with a reduced injection pressure and extremely small pre-injection quantities.
- By suitably controlling the solenoid valve of the injector small strokes of the control piston can be achieved. Since the stroke of the nozzle needle cannot be greater than the stroke of the control piston due to the coupling of the control piston and nozzle needle, it is thus also possible to restrict the stroke of the nozzle needle.
- control piston is arranged in an axially displaceable manner in a guide bore, and that the nozzle needle is arranged in a for
- Guide bore coaxial bore is axially displaceable and that the coupling of the control piston and nozzle needle takes place via a valve piston. Due to the coaxial arrangement of the control piston and nozzle needle, the coupling forces can be transmitted directly and easily. If necessary, the distance between the control piston and the nozzle needle can be bridged using a valve piston.
- valve pistons and control pistons or nozzle needles and Control piston made in one piece, so that the number of components is reduced and misalignments avoided.
- control piston has two grooves, that the control piston between the grooves is designed as a slide, and that the slide, when the injection nozzle is closed, has extensive hydraulic separation with a control edge of the guide bore
- the high-pressure connection and inlet channel have the effect that, with a small stroke of the control piston, the fuel is throttled between the control edge and the spool, thus reducing the injection pressure.
- This and the resulting low injection quantity result in further design options with regard to the injection process.
- Pre-injection take place. This is possible in particular if the pressure in the inlet channel and in the pressure chamber of the injection nozzle drops so much during the pre-injection that the hydraulic force acting on the first end face of the valve piston is greater than that on the
- Cross-sectional change of the nozzle needle is acting force.
- the hydraulic separation of the high-pressure connection and the inlet channel is structurally determined by the overlap of the slide and the control edge and the fit between the slide and the guide bore, so that a further degree of freedom can be used when coordinating the injector.
- Another variant provides for one against the housing of the injector and the nozzle needle supporting closing spring is present, so that even if there is no fuel jerk the injector is always closed securely.
- the closing spring can contribute to the nozzle needle automatically closing again after the solenoid valve has been actuated once, by increasing the hydraulic closing force.
- an auxiliary spring acting on the control piston is present and / or that the inlet channel, in conjunction with the fuel contained in it, serves as a pressure accumulator, so that it is ensured, in particular in the case of the main injection, that the control piston is one executes such a large stroke that there is no longer any overlap between the spool and the control edge and the injector's injection nozzle is thus subjected to the full pressure of the fuel. This enables the injector to be opened quickly and a large amount of fuel can be injected in a short time.
- FIG. 1 shows a cross section through an injector according to the invention with the solenoid valve closed
- Fig. 2 shows the control room of an injector according to the invention with the solenoid valve open. Description of the embodiments
- a high-pressure connection 1 supplies a control chamber 3 with fuel, not shown in FIGS. 1 and 2.
- An injection nozzle 7 is also supplied with fuel via the control chamber 3 and an inlet duct 5.
- the control chamber 3 is radially delimited by a guide bore 9.
- An axially displaceable control piston 11 is present in the guide bore 9.
- the control piston divides the control chamber 3 into three sections 13, 15 and 17.
- the first section 13 of the control chamber 3 is axially defined by a first end face 18 of the control piston 11
- first section 13 of the control chamber 3 is hydraulically connected to the second section 15 of the control chamber 3 via an inlet throttle 19.
- the inlet throttle 19 can be designed as a groove or as a bore.
- the first section 13 is connected to a fuel return, also not shown, via an outlet throttle 21, which can be opened by a ball 22 controlled by a solenoid valve (not shown).
- the control piston 11 has two grooves 23, 25, which radially limit the second section 15 and the third section 17 of the control chamber 3.
- a slide 27 is arranged between the grooves 23, 25.
- a valve piston 33 which acts on a nozzle needle 31 of the injection nozzle 7, adjoins the second end face 29 of the control piston 11.
- the nozzle needle 31 prevents the fuel under pressure from flowing between the injections into the combustion chamber, not shown. This is done in that the nozzle needle 31 is in a nozzle needle seat 34 is pressed and seals the inlet channel 5 against the combustion chamber.
- the nozzle needle 31 has a cross-sectional change 35 from a larger diameter 37 to a smaller diameter 39. With its larger diameter 37, the nozzle needle 31 is guided in a housing 41 of the injector. The change in cross section 35 delimits a pressure space 43 of the injection nozzle 7.
- the slide 27 separates the third section 17 of the control chamber 3 and thus also the inlet duct 5 coming from the third section 17 of the control chamber 3 from the high-pressure connection 1.
- the overlap 45 of the slide 27 and a control edge 47 of the guide bore 9 is selected so that, even in this position of the slide 27, a certain leakage occurs between the injections and thus the same pressure prevails in the pressure chamber 43 as in the high pressure connection 1.
- the flow restrictor 21 When the flow restrictor 21 is opened by the Solenoid valve controlled and the ball 22 is lifted from a ball seat 51, the pressure in the first section 13 of the control chamber 3 drops, since the inlet throttle 19 prevents complete pressure equalization between the inlet channel 5 and the first section 13 of the valve control chamber 3. As a result, the hydraulic force acting on the first end face 18 also drops. As soon as this hydraulic force is less than the hydraulic force acting on the cross-sectional change 35, the nozzle needle 31 lifts off the nozzle needle seat 34 and thus opens the injection nozzle 7, so that fuel is injected into the combustion chamber.
- the opening speed of the nozzle needle 31 is determined, among other things, by the flow difference between the inlet throttle 19 and the outlet throttle 21.
- a pre-injection with a low injection pressure and a small injection quantity can also be brought about.
- the force of the closing spring 49 and the hydraulic force acting on the first end face 18 must be greater than the hydraulic force acting on the cross-sectional change 35.
- the pressure in pressure chamber 43 can drop so far that the above-mentioned condition occurs. This results in additional options for the design of the course of the main injection and the pre-injection.
- a pre-injection with a single activation of the Solenoid valve can be reached.
- the main injection takes place in the position of the control piston 9 shown in FIG. 2.
- the elasticity of the inlet channel 5 is to be selected appropriately.
- auxiliary spring 53 can also be provided.
- the auxiliary spring 53 acts on the second end face 29 of the control piston 9 and supports the opening of the injection nozzle 7.
- Another advantage of this injector is that the overlap 45 between the slide 27 and the control edge 47 when the injector 7 is closed leaks between the nozzle needle 31 and the nozzle needle seat 34, for example by small chips or the like. greatly reduced. This means increased security against a faulty, permanent one.
- the outlet throttle 21 is closed by the ball 22 in a manner not explained in detail.
- the valve control chamber 3 builds up in the first section 13 About the inlet throttle 19 again approximately the pressure prevailing in the high-pressure connection 1.
- This pressure exerts a hydraulic force on the nozzle needle 31 via the first end face 18 of the control piston 9 via the valve piston 33.
- the nozzle needle 31 closes. Because of the first end face 18 of the control piston 9, which is significantly larger compared to the annular surface of the cross-sectional change 35, the closing movement takes place very quickly and with great force.
- control quantity required in addition to the fuel quantity injected into the combustion chamber reaches the inlet throttle 19, the control chamber 3 and the outlet throttle 21 in the
- Fuel return In addition to the control quantity, there is also a leak at the nozzle needle guide.
- the control and leakage quantities can be up to 50 mm / stroke. They are also discharged back into the fuel return, not shown, via the outlet throttle 21.
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 (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
KR1020017011046A KR20010102443A (ko) | 1999-12-31 | 2000-11-21 | 슬라이딩식으로 제어되는 입구를 구비하며 제어 피스톤 및인젝터 핀이 직접 연결된 커먼 레일 연료 분사 시스템용인젝터 |
EP00993733A EP1187986A2 (de) | 1999-12-31 | 2000-11-21 | Injektor für ein common-rail-kraftstoffeinspritzsystem mit schiebergesteuertem zulaufkanal und direkter kopplung von steuerkolben und düsennadel |
JP2001549925A JP2003519336A (ja) | 1999-12-31 | 2000-11-21 | スプール制御される流入通路と、制御ピストンとノズルニードルとの直接的な連結部とを備えた、コモンレール燃料噴射系のためのインジェクタ |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19963920.5 | 1999-12-31 | ||
DE19963920A DE19963920B4 (de) | 1999-12-31 | 1999-12-31 | Injektor für ein Common-Rail-Kraftstoffeinspritzsystem mit schiebergesteuertem Zulaufkanal und direkter Kopplung von Steuerkolben und Düsenkanal |
Publications (2)
Publication Number | Publication Date |
---|---|
WO2001050014A2 true WO2001050014A2 (de) | 2001-07-12 |
WO2001050014A3 WO2001050014A3 (de) | 2001-12-13 |
Family
ID=7935087
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2000/004101 WO2001050014A2 (de) | 1999-12-31 | 2000-11-21 | Injektor für ein common-rail-kraftstoffeinspritzsystem mit schiebergesteuertem zulaufkanal und direkter kopplung von steuerkolben und düsennadel |
Country Status (6)
Country | Link |
---|---|
EP (1) | EP1187986A2 (de) |
JP (1) | JP2003519336A (de) |
KR (1) | KR20010102443A (de) |
CZ (1) | CZ20013144A3 (de) |
DE (1) | DE19963920B4 (de) |
WO (1) | WO2001050014A2 (de) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10158028A1 (de) * | 2001-11-27 | 2003-06-12 | Bosch Gmbh Robert | Injektor für ein Common-Rail-Kraftstoffeinspritzsystem mit Einspritzverlaufsformung |
JP5039524B2 (ja) * | 2007-12-05 | 2012-10-03 | 三菱重工業株式会社 | 蓄圧式燃料噴射装置の燃料噴射弁 |
Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5551634A (en) * | 1993-11-26 | 1996-09-03 | Mercedes-Benz A.G. | Fuel injection nozzle for an internal combustion engine |
EP0789142A1 (de) * | 1995-08-29 | 1997-08-13 | Isuzu Motors Limited | Kraftstoffeinspritzvorrichtung der speichergattung |
EP0829641A2 (de) * | 1996-08-31 | 1998-03-18 | Isuzu Motors Limited | Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen |
DE19742320A1 (de) * | 1997-09-25 | 1999-04-01 | Bosch Gmbh Robert | Kraftstoffeinspritzventil |
DE19826339A1 (de) * | 1998-06-12 | 1999-12-16 | Bosch Gmbh Robert | Ventil zum Steuern von Flüssigkeiten |
DE19826791A1 (de) * | 1998-06-16 | 1999-12-23 | Bosch Gmbh Robert | Ventilsteuereinheit für ein Kraftstoffeinspritzventil |
DE19826719A1 (de) * | 1998-06-16 | 1999-12-23 | Bosch Gmbh Robert | Ventilsteuereinheit für ein Kraftstoffeinspritzventil |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3151065C2 (de) * | 1981-12-23 | 1986-03-20 | Daimler-Benz Ag, 7000 Stuttgart | Kraftstoffeinspritzdüse für Brennkraftmaschinen |
AT1626U1 (de) * | 1995-04-05 | 1997-08-25 | Avl Verbrennungskraft Messtech | Speichereinspritzsystem für brennkraftmaschinen |
DE19701879A1 (de) * | 1997-01-21 | 1998-07-23 | Bosch Gmbh Robert | Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen |
-
1999
- 1999-12-31 DE DE19963920A patent/DE19963920B4/de not_active Expired - Fee Related
-
2000
- 2000-11-21 WO PCT/DE2000/004101 patent/WO2001050014A2/de not_active Application Discontinuation
- 2000-11-21 EP EP00993733A patent/EP1187986A2/de not_active Withdrawn
- 2000-11-21 JP JP2001549925A patent/JP2003519336A/ja active Pending
- 2000-11-21 CZ CZ20013144A patent/CZ20013144A3/cs unknown
- 2000-11-21 KR KR1020017011046A patent/KR20010102443A/ko not_active Application Discontinuation
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5551634A (en) * | 1993-11-26 | 1996-09-03 | Mercedes-Benz A.G. | Fuel injection nozzle for an internal combustion engine |
EP0789142A1 (de) * | 1995-08-29 | 1997-08-13 | Isuzu Motors Limited | Kraftstoffeinspritzvorrichtung der speichergattung |
EP0829641A2 (de) * | 1996-08-31 | 1998-03-18 | Isuzu Motors Limited | Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen |
DE19742320A1 (de) * | 1997-09-25 | 1999-04-01 | Bosch Gmbh Robert | Kraftstoffeinspritzventil |
DE19826339A1 (de) * | 1998-06-12 | 1999-12-16 | Bosch Gmbh Robert | Ventil zum Steuern von Flüssigkeiten |
DE19826791A1 (de) * | 1998-06-16 | 1999-12-23 | Bosch Gmbh Robert | Ventilsteuereinheit für ein Kraftstoffeinspritzventil |
DE19826719A1 (de) * | 1998-06-16 | 1999-12-23 | Bosch Gmbh Robert | Ventilsteuereinheit für ein Kraftstoffeinspritzventil |
Also Published As
Publication number | Publication date |
---|---|
JP2003519336A (ja) | 2003-06-17 |
EP1187986A2 (de) | 2002-03-20 |
KR20010102443A (ko) | 2001-11-15 |
WO2001050014A3 (de) | 2001-12-13 |
CZ20013144A3 (cs) | 2003-02-12 |
DE19963920A1 (de) | 2001-07-12 |
DE19963920B4 (de) | 2005-01-13 |
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