CN101529078B - Injector for injecting fuel - Google Patents
Injector for injecting fuel Download PDFInfo
- Publication number
- CN101529078B CN101529078B CN2007800388424A CN200780038842A CN101529078B CN 101529078 B CN101529078 B CN 101529078B CN 2007800388424 A CN2007800388424 A CN 2007800388424A CN 200780038842 A CN200780038842 A CN 200780038842A CN 101529078 B CN101529078 B CN 101529078B
- Authority
- CN
- China
- Prior art keywords
- valve
- valve piston
- seat surface
- shoulder
- seat
- 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 - Fee Related
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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
- 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
- F02M63/0014—Valves characterised by the valve actuating means
- F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
-
- 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
- F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
- F02M63/0073—Pressure balanced 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
- 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
- F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member
- F02M63/008—Hollow valve members, e.g. members internally guided
-
- 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
-
- 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
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
The invention relates to an injector for injecting fuel into a combustion chamber (3) of an internal combustion engine, having an injector housing (9) in which is held a control valve (5) for activating an injection valve element (7) which opens or closes off at least one injection opening (11), wherein the control valve (5) comprises a valve piston (39), by means of which a connection from a control space (25) into a fuel return line (27) can be opened or closed off. The valve piston (39) comprises an annular seat face (41) which can be placed into a seat (43). A shoulder (55; 93) is formed on the valve piston (39), which shoulder (55; 93) is arranged on the high-pressure side of the valve piston (39) in such a way that the pressure force exerted by the fuel on the shoulder (55; 93) assists the closing movement of the valve piston (39).
Description
Technical field
The present invention relates to a kind of like claim 1 sparger that is used to inject fuel into the combustion chambers of internal combustion engines the inside as described in the preamble.
Background technique
In the firing chamber for the DENG of the internal-combustion engine, the especially direct injection that inject fuel into self ignition, use the high pressure accumulator system (common rail system) of stroke control more and more.In the high pressure accumulator ejecting system of stroke control, can make jet pressure adapt to load and rotating speed.
In the fuel injector of stroke control, control injection valve member through the servocontrol chamber.Through the pressure in the electromagnetic valve servocontrol chamber with spherical closing element.But this is not pressure balanced and needs high spring force, high magnetic switch power and many structure spaces.Control by the ball solenoid valve has strong restriction for multi-injection.Very short interval between can not realizing spraying.
, can realize the valve piston of control valve that littler spring force, littler electromagnetic force, littler Valve travel also realize conversion time faster thus when being in pressure balance.Can improve the multi-injection ability thus.Pressure balanced control valve is as the guide rail and the rectilinear sealing seat that are had high pressure sealing by the known that kind of existing technology, and the sealing seat is corresponding to the guide rail diameter.Making valve thus is pressure balanced in state of rest.
But the defective of pressure balanced valve is possibly produce for the pin type closure body and close rebound.Load when this external valve piston is closed on lineal shape valve seamed edge is very large.Therefore produce wearing and tearing, it impairs function.
Summary of the invention
The sparger that is used for injecting fuel into combustion chambers of internal combustion engines according to the present invention structure comprises a case of sprayer; In this case of sprayer, hold one be used to control an injection valve member control valve, this injection valve member discharges or seals at least one and spray opening.This control valve comprises a valve piston, can discharge or close the connection from a control room to an area of low pressure through this valve piston.Said valve piston comprise one basically the annular seat surface, this seat surface can be placed in the flat seat.This control valve of structure makes that it is pressure balanced like this.
In pressure balanced control valve, beyond seat surface, there is not or has only very little pressure side in the high pressure side.For this reason, valve piston is directed in a valve guide rail in the high pressure side.Seat surface-high pressure is on this seat surface-the seat diameter also roughly corresponding to the guide rail diameter.
" seat surface of basic annular " means that on meaning of the present invention seat surface can constitute circlewise.It is not accurately annular can making seat surface in addition.Therefore seat surface can have for example little sword.
In a form of implementation, on valve piston, constructed shoulder, this shoulder is arranged on the high pressure side of valve piston like this, the feasible closing movement that is applied to the pressure support valve piston on the shoulder by fuel.
The advantage of annular sealing surface is to reduce the load of sealing surface when pin is closed thus and improved impact damping.Improved the rebound characteristic thus, that is, taken place small or do not knock-on, improved the multi-injection ability thus and reduce the valve wearing and tearing.Can produce the additional of pressure through sealing surface and open, but this is opened through pressure balanced valve piston and controllably is retained through present operational electromagnetic actuator.
In a preferred form of implementation, the seat surface on the valve piston is surrounded by a damping area, and wherein damping area and seat surface are configured to a step, damping area is not touched when control valve is closed lean against on the valve seat.Optimized the damping of shocks of valve piston through damping area.Damping area can be implemented with simple mode on processing technique, because there is the reference level that is used for spacing dimension through annular seat surface.Because, on the working life of sparger, can stably realize damping area thus because seat surface makes the valve seat minimum of must wearing and tearing.
Usually, the control valve according to the sparger of the present invention structure is solenoid-operated.Also can conversion control valve for example be handled through piezo actuator.
For the pressure on the high pressure side of control valve piston, the high-pressure area on the control valve is connected with fuel high pressure pipeline through at least one throttling unit, makes the fuel that is under the system pressure flow to sparger from high pressure accumulator through this fuel high pressure pipeline.
In a preferred form of implementation, said seat is a flat seat, and annular seat surface can place this seat.Can realize the two-part construction mode of valve piston through valve seat being configured to flat seat.The guide rail of valve piston and annular seat surface can be manufactured in the various parts thus.This allows the good processability of annular seat surface and allows the favourable manufacturing of cost thus.If replace flat seat for example to use conical seat, the guide rail of annular seat surface and valve piston is realized on a structure member, because have only when annular seat surface abuts on the conical seat, could realize the closing liquid seal of control valve on whole circumference.The accurate guiding that for this reason needs valve piston.Different therewith is that annular seat surface is in the blow-by that can not cause when control valve is closed that moves axially on the flat seat.
In order to realize the short interval between each time injection, valve piston preferably constitutes with solenoid valve ground armature integratedly.Can realize the small movements quality of armature and valve piston thus.Armature is contained in the armature chamber, and the return flow path of this armature chamber and the fuel quantity that is used to control sparger takes off couplet.Make the conversion dynamic and the counterflow condition of electromagnetic actuator irrelevant thus.
The shoulder of on valve piston, constructing-this shoulder is arranged on the high pressure side of valve piston like this; Make by fuel be applied to pressure on this shoulder support the closing movement of valve piston-advantage be; The valve that produces hydraulic pressure through this shoulder cuts out power, and this valve cuts out the open hydraulic coupling of force compensating from annular seat surface.Can realize it also almost being pressure balanced control valve thus.Through this shoulder control valve is configured with bigger sealing surface in addition, has improved the damping characteristic of seal valve seat thus and further reduced wearing and tearing.On shoulder, form a hydraulic pressure when this external valve seat has been closed and close power, this is closed mechanical resistance and ends valve and open.Can realize the best valve harmony and the multi-injection ability of improvement thus.
In a form of implementation, in valve piston, constructed the break-through structure, a pin is contained in this break-through structure, this pin with its deviate from said surface bearing on the case of sprayer and this pin in valve piston to high pressure sealing be directed to.Through this pin valve piston pressure balance ground is constituted.
Although in order there to be also pressure balance ground structure valve piston almost of shoulder, make the cross-section area of this shoulder be about annular seat surface cross-section area 50%.
The cross-section area that preferably makes said break-through structure is less than the cross-section area that excircle surrounded by the annular seat surface of valve piston.The diameter that preferably makes said guide rail is more than or equal to the internal diameter of said seat surface and be less than or equal to the external diameter of said seat surface.
In the form of implementation of a conversion, valve piston is directed in a guide rail, wherein, in order on valve piston, to construct shoulder, the cross-section area that the cross-section area in the zone of said guide rail that makes valve piston surrounds less than the excircle by said seat surface.Valve piston almost pressure balance ground constitutes thus, the cross-section area of said shoulder be about said seat surface cross-section area 50%.
Description of drawings
Form of implementation of the present invention shown in the drawings and illustrated in detail in the following description.In the accompanying drawing:
Fig. 1 illustrates the fuel injector that constitutes according to the present invention with first form of implementation,
Fig. 2 illustrates the fuel injector that constitutes according to the present invention with second form of implementation.
Embodiment
In Fig. 1, the fuel injector that constitutes according to the present invention is shown with first form of implementation.
Inject fuel in the sparger 1 of combustion chambers of internal combustion engines 3 being used for, the control valve 5 that is used for controlling injection valve member 7 is contained in case of sprayer 9.In order to inject fuel in the combustion chambers of internal combustion engines 3, injection valve member 7 discharges or seals at least one and spray opening 11.Injection valve member 7 is surrounded by nozzle box 13, and this nozzle box is connected with fuel inlet pipe road 17 through pressure duct 15.Fuel inlet pipe road road 17 makes the high pressure accumulator 19 of high pressure accumulator ejecting system (common rail system) be connected with sparger 1.
In deviating from least one side of spraying opening 11 of injection valve member 7, on injection valve member 7, connected control piston 21.Control piston 21 defines control room 25 with the end face 23 that deviates from injection valve member 7.Control piston 21 is directed in piston guide rail 27, and this piston rail configurations is in director element 29.Director element 29 is surrounded by pressure chamber 31, and this pressure chamber is connected with high pressure accumulator 19 through fuel inlet pipe road 17.Through throttling unit 33 pressure chamber 31 is connected with control room 25.
Through the second throttling unit 34 fuel, control valve 5 is flow to the fuel backflow portion 37 when opening from control room 25.Fuel backflow portion 37 is connected with the area of low pressure of this ejecting system.
Construct break-through structure 49 in valve piston 39 the insides, in this break-through structure, held pin 51.Pin 51 is bearing on the case of sprayer 9 with end face 53.
In the break-through structure 49 of valve piston 39, constructed shoulder 55.When break-through structure 49 had circular cross section, the diameter of break-through structure 49 was greater than the internal diameter of annular seat surface 41.The cross-section area of this break-through structure is greater than the free cross-section area of this annular seat surface thus.Although in order to make valve piston 39 have shoulder 55 also almost is pressure balanced, make the cross-section area of shoulder 55 be about annular seat surface 41 cross-section area 50%.Preferably make the diameter of break-through structure 49 be less than or equal to the external diameter of annular seat surface 41, make the cross-section area of break-through structure 49 be less than or equal to the cross-section area that excircle surrounded by the annular seat surface 41 of valve piston 39.
In form of implementation shown in Figure 1, on valve piston 39, constructed the armature 57 of said electromagnetic actuator integratedly.Deviating from the side of annular seat surface 41, the coil 59 of said electromagnetic actuator is positioned at the opposite of armature 57.Coil 59 is contained in the magnetic core 61 in order to strengthen magnetic force.Magnetic core 61 surrounds spring housing 63, in this spring housing, has held spring element 65.Spring element 65 is bearing on the case of sprayer 9 on the end face 67 of valve piston 39 and with the other end with an end bearing.Surround pin 51 at this spring element 65.Spring element 65 preferably is configured to helical spring stage clip.
In order to begin course of injection, make coil 59 energisings of electromagnetic actuator.Thus, the armature 57 that is connected with valve piston 39 is attracted by coil 59.The annular seat surface 41 from valve seat 43 lift and discharge from control room 25 to fuel backflow portion 37 connection.Pressure in the control room 25 descends.Be in fuel under the system pressure act on the injection valve member 7, put on the pressure step 77 in the nozzle box 13.Because the pressure on the pressure step 77 makes injection valve member 7 and control piston 21 25 motions towards the control room.Thus injection valve member from its seat lift 79 and discharge thus said at least one spray opening.
For the end injection process finishes, finish the energising of the coil 59 of electromagnetic actuator.Actuator 57 is no longer attracted by coil 59.By means of spring element 65 valve piston 39 is placed in its seat 43 with annular seat surface 41.On annular seat surface 41, form pressure pad at this, the motion of this pressure pad trimmer valve piston 39.The motion of valve piston 39 also is cushioned through damping area 45, the same pressure pad that forms on this damping area.The motion of valve piston 39, control valve 5 is delayed before closing soon.Avoid the impact on the annular seat surface 41 present 43 thus, this impact can cause the resilience of valve piston 39.Through throttling unit 33, fuel flows in the control room 25.Pressure in the control room 25 improves.Control piston 21 is towards injection valve member 7 motions thus.Injection valve member 7 is placed in its seat 79 and closes at least one and spray opening 11 thus.
In Fig. 2, the fuel injector according to the present invention's structure is shown with second form of implementation.
For at the sparger shown in Fig. 21, control piston 21 is surrounded by pressure chamber 81.Through the free surface on the injection valve member 7 83 pressure chamber 81 is connected with nozzle box 13.In the form of implementation here, control piston 21 constitutes with injection valve member 7 integratedly.Control piston 21 is surrounded by seal sleeve 85.Seal sleeve 85 is separated control room 81 and control room 25.Seal sleeve 85 places on the valve piece 89 through clamping seamed edge 87 for this reason, and wherein valve piece 89 constitutes the border in control room 25 on the face relative with control piston 21.Control room 25 is connected with pressure chamber 81 through throttling unit 33.Be configured in the seal sleeve 85 in this throttling unit 33.
Shown in form of implementation in, armature 57 is contained in the armature chamber 99, so that the conversion dynamic that makes control valve 5 is irrelevant with the counterflow condition from valve chamber 91.Make armature chamber 99 for this reason and take off couplet from the backflow portion of valve chamber 91.This point realizes that so promptly, armature chamber 99 is not connected with valve chamber 91, but directly is connected with fuel backflow portion 37 through path 10 1.
In the working method of the fuel injector shown in Fig. 2 corresponding to working method at the fuel injector shown in Fig. 1.
Claims (7)
1. be used for injecting fuel into the sparger of a firing chamber (3) of internal-combustion engine, have a case of sprayer (9), in this case of sprayer, held one be used to control an injection valve member (7) control valve (5); This injection valve member discharges or closes at least one and spray opening (11); Wherein, this control valve (5) comprises a valve piston (39), can discharge or close the connection from a control room (25) to a fuel backflow portion (37) through this valve piston; Wherein, Said valve piston (39) comprises the seat surface (41) of a basic annular, and this seat surface can be placed in one (43), and the structure of this control valve (5) makes that this control valve is pressure balanced; In said valve piston (39), constructed a break-through structure (49); In this break-through structure, held a pin (51), this pin be supported on the said case of sprayer (9) with its face that deviates from said seat (43) and this pin in said valve piston (39) to high pressure sealing be directed to, in said break-through structure (49), constructed a shoulder (55; 93), this shoulder is set on the high pressure side of said valve piston (39), makes to be applied to this shoulder (55 by fuel; 93) pressure on is supported the closing movement of said valve piston (39); The cross-section area that the cross-section area of said break-through structure (49) surrounds less than the excircle by the seat surface (41) of said valve piston (39); It is characterized in that the seat surface (41) on the said valve piston (39) is surrounded by a damping area (45), wherein; This damping area (45) and this seat surface (41) constitute a step (47), make this damping area (45) not touch when closing at said control valve (5) and lean against on the said seat (43).
2. sparger as claimed in claim 1 is characterized in that, said control valve (5) is an eletromagnetic-operating.
3. according to claim 1 or claim 2 sparger; It is characterized in that; High-pressure area on the said control valve (5) is connected with a fuel inlet pipe road (17) through at least one throttling unit (33); Through this fuel inlet pipe road, the fuel that is under the system pressure flows to this sparger (1) from a high pressure accumulator (19).
4. according to claim 1 or claim 2 sparger is characterized in that, said seat (43) is a flat seat, and the seat surface of said annular (41) can be placed in this seat.
5. according to claim 1 or claim 2 sparger is characterized in that, the cross-section area of said shoulder (55) be said annular seat surface (41) cross-section area about 50%.
6. according to claim 1 or claim 2 sparger; It is characterized in that; Said valve piston (39) is directed in a guide rail (97); Wherein in order to go up structure said shoulder (93), the cross-section area that the cross-section area of said valve piston (39) in the zone of this guide rail (97) surrounds less than the excircle by said seat surface (41) at said valve piston (39).
7. sparger as claimed in claim 6 is characterized in that, the cross-section area of said shoulder (93) be about said seat surface (41) cross-section area 50%.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102006049050.9 | 2006-10-18 | ||
| DE102006049050A DE102006049050A1 (en) | 2006-10-18 | 2006-10-18 | Injector for injecting fuel |
| PCT/EP2007/058470 WO2008046679A1 (en) | 2006-10-18 | 2007-08-15 | Injector for injecting fuel |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101529078A CN101529078A (en) | 2009-09-09 |
| CN101529078B true CN101529078B (en) | 2012-07-18 |
Family
ID=38717215
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2007800388424A Expired - Fee Related CN101529078B (en) | 2006-10-18 | 2007-08-15 | Injector for injecting fuel |
Country Status (5)
| Country | Link |
|---|---|
| EP (1) | EP2079922B1 (en) |
| CN (1) | CN101529078B (en) |
| AT (1) | ATE491091T1 (en) |
| DE (2) | DE102006049050A1 (en) |
| WO (1) | WO2008046679A1 (en) |
Families Citing this family (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102007011685A1 (en) * | 2007-03-09 | 2008-09-11 | Robert Bosch Gmbh | Fuel injector with improved control valve |
| DE102008001425A1 (en) * | 2008-04-28 | 2009-10-29 | Robert Bosch Gmbh | Fuel injector |
| DE102009029355A1 (en) * | 2009-09-10 | 2011-03-24 | Robert Bosch Gmbh | injector |
| DE102009045335A1 (en) | 2009-10-05 | 2011-04-07 | Robert Bosch Gmbh | injector |
| DE102009045995A1 (en) * | 2009-10-26 | 2011-06-09 | Robert Bosch Gmbh | Fuel injector |
| EP2333296B1 (en) * | 2009-12-10 | 2013-04-17 | Delphi Technologies Holding S.à.r.l. | A Valve Member for a Fluid Valve Arrangement |
| DE102012104531A1 (en) * | 2012-05-25 | 2013-10-24 | L'orange Gmbh | Valve assembly for fuel injection nozzle, has rod-shaped valve actuator that is provided in sealing boarders at outlet side, and flow throttling device is integrated in rod-shaped valve actuator |
| DE102012209841A1 (en) | 2012-06-12 | 2013-12-12 | Robert Bosch Gmbh | Fuel injector for common-rail fuel injection system, has control piston guided in valve unit, which divides control chamber into multiple pressure chambers, where former pressure chamber is arranged between shaft end and control piston |
| DE102012223166A1 (en) | 2012-12-14 | 2014-06-18 | Robert Bosch Gmbh | fuel injector |
| DE102013212140A1 (en) | 2013-06-25 | 2015-01-08 | Robert Bosch Gmbh | control valve |
| GB201400650D0 (en) * | 2014-01-15 | 2014-03-05 | Delphi Tech Holding Sarl | Bobbin with venting conduit |
| DE102015223168A1 (en) | 2015-11-24 | 2017-05-24 | Robert Bosch Gmbh | fuel injector |
| CN110529316B (en) * | 2019-08-22 | 2020-11-03 | 一汽解放汽车有限公司 | Fuel injection valve and engine |
| CN114060193A (en) * | 2020-08-04 | 2022-02-18 | 温特图尔汽柴油公司 | Fuel injection valve for large diesel engine and large diesel engine |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2330873A (en) * | 1997-11-04 | 1999-05-05 | Caterpillar Inc | A fuel injector with a spill valve and a check control valve controlled by a single actuator |
| US5947380A (en) * | 1997-11-03 | 1999-09-07 | Caterpillar Inc. | Fuel injector utilizing flat-seat poppet valves |
| GB2336628A (en) * | 1998-04-24 | 1999-10-27 | Lucas Ind Plc | A fuel injector, for an I.C. engine, having a three way two position needle control valve |
| GB2350662A (en) * | 1999-06-03 | 2000-12-06 | Lucas Ind Plc | Valve for a fuel injector |
| CN1829858A (en) * | 2003-07-24 | 2006-09-06 | 罗伯特·博世有限公司 | Fuel injection device |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19915686A1 (en) * | 1999-04-07 | 2000-10-12 | Delphi Tech Inc | Switching valve |
| DE10118053A1 (en) * | 2001-04-11 | 2002-10-24 | Bosch Gmbh Robert | Valve for controlling liquids e.g. for vehicle fuel injection system, has hydraulic chamber that transfers control piston movement to actuating piston, which is in hydraulic force equilibrium with valve element closed |
| ITTO20010969A1 (en) * | 2001-10-12 | 2003-04-12 | C R F Societa Con Sortile Per | IMPROVEMENTS TO A FUEL INJECTOR FOR ENDOTHERMAL ENGINES, WITH AN ELECTROMAGNETIC DOSING VALVE. |
| DE102006021741A1 (en) * | 2006-05-10 | 2007-11-15 | Robert Bosch Gmbh | Fuel injector with pressure compensated control valve |
-
2006
- 2006-10-18 DE DE102006049050A patent/DE102006049050A1/en not_active Withdrawn
-
2007
- 2007-08-15 DE DE502007005914T patent/DE502007005914D1/en active Active
- 2007-08-15 AT AT07788444T patent/ATE491091T1/en active
- 2007-08-15 WO PCT/EP2007/058470 patent/WO2008046679A1/en active Application Filing
- 2007-08-15 CN CN2007800388424A patent/CN101529078B/en not_active Expired - Fee Related
- 2007-08-15 EP EP07788444A patent/EP2079922B1/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5947380A (en) * | 1997-11-03 | 1999-09-07 | Caterpillar Inc. | Fuel injector utilizing flat-seat poppet valves |
| GB2330873A (en) * | 1997-11-04 | 1999-05-05 | Caterpillar Inc | A fuel injector with a spill valve and a check control valve controlled by a single actuator |
| GB2336628A (en) * | 1998-04-24 | 1999-10-27 | Lucas Ind Plc | A fuel injector, for an I.C. engine, having a three way two position needle control valve |
| GB2350662A (en) * | 1999-06-03 | 2000-12-06 | Lucas Ind Plc | Valve for a fuel injector |
| CN1829858A (en) * | 2003-07-24 | 2006-09-06 | 罗伯特·博世有限公司 | Fuel injection device |
Also Published As
| Publication number | Publication date |
|---|---|
| EP2079922A1 (en) | 2009-07-22 |
| DE102006049050A1 (en) | 2008-04-30 |
| ATE491091T1 (en) | 2010-12-15 |
| EP2079922B1 (en) | 2010-12-08 |
| CN101529078A (en) | 2009-09-09 |
| WO2008046679A1 (en) | 2008-04-24 |
| DE502007005914D1 (en) | 2011-01-20 |
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