CN1717539A - The Fuelinjection nozzle that is used for internal-combustion engine - Google Patents
The Fuelinjection nozzle that is used for internal-combustion engine Download PDFInfo
- Publication number
- CN1717539A CN1717539A CN 03825689 CN03825689A CN1717539A CN 1717539 A CN1717539 A CN 1717539A CN 03825689 CN03825689 CN 03825689 CN 03825689 A CN03825689 A CN 03825689A CN 1717539 A CN1717539 A CN 1717539A
- Authority
- CN
- China
- Prior art keywords
- needle
- valve seat
- fuelinjection nozzle
- pressure
- valve
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 238000002485 combustion reaction Methods 0.000 title claims description 14
- 238000002347 injection Methods 0.000 claims abstract description 31
- 239000007924 injection Substances 0.000 claims abstract description 31
- 238000007789 sealing Methods 0.000 claims abstract description 26
- 239000000446 fuel Substances 0.000 claims abstract description 23
- 238000006243 chemical reaction Methods 0.000 claims abstract description 6
- 230000013011 mating Effects 0.000 claims abstract description 6
- 238000010304 firing Methods 0.000 claims description 7
- 230000015572 biosynthetic process Effects 0.000 claims description 4
- 230000008878 coupling Effects 0.000 claims description 3
- 238000010168 coupling process Methods 0.000 claims description 3
- 238000005859 coupling reaction Methods 0.000 claims description 3
- 230000000284 resting effect Effects 0.000 claims description 2
- 230000002349 favourable effect Effects 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 230000007704 transition Effects 0.000 description 3
- 230000002238 attenuated effect Effects 0.000 description 2
- 230000008901 benefit Effects 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 238000005507 spraying Methods 0.000 description 2
- 241000167854 Bourreria succulenta Species 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 235000012489 doughnuts Nutrition 0.000 description 1
- 231100001261 hazardous Toxicity 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000006386 neutralization reaction Methods 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 238000012856 packing Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 239000007921 spray Substances 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
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
- 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
-
- 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
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/28—Details of throttles in fuel-injection apparatus
-
- 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
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/46—Valves, e.g. injectors, with concentric valve bodies
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
Fuelinjection nozzle has a valve body (1), constitutes a hole (2) in this valve body, and at least one injection channel (14) at one end by a valve seat (11) limited boundary, is drawn from this valve seat in this hole.In hole (2), settled a needle (7) with longitudinal movement, this needle at it in the face of having a valve sealing surface (12) on the end of valve seat (11), needle with this valve sealing surface and valve seat (11) mating reaction to open and close described at least one injection channel (14).Constitute a pressure chamber (5) between the wall of needle (7) and hole (2), this pressure chamber can fill with fuel under high pressure.Go up to constitute a pressure side (30) in the face of valve seat (11) at needle (7), when needle (7) rests on valve seat (11) when going up, this pressure side can be communicated with pressure chamber (5) by a throttling position (26).
Description
Prior art
The present invention relates to a kind of Fuelinjection nozzle that is used for internal-combustion engine, as for example known from open source literature DE (standard valve) A1.This Fuelinjection nozzle comprises a valve body, and in this valve body, the needle of a piston-like is placed in the hole with longitudinal movement.Constitute a pressure chamber between needle and hole wall, this pressure chamber can be filled fuel under high pressure.By a valve seat restricted boundary, draw a plurality of spray-holes on the end of this Kong Zaiqi combustion chamber side from this valve seat.Rest on the valve seat these spray-holes sealings by needle, and when needle when valve seat lifts, fuel enters spray-hole from flowing through between valve sealing surface and the valve seat, is ejected into therefrom in the firing chamber of internal-combustion engine.
At this, the move through both direction opposite power of needle between open position and closed position realizes: on the one hand by one to the closing force of valve seat directive effect on needle, the breaking force that produces by a hydraulic pressure on the other hand.For this reason, needle has at least one pressure side, and it preferably constitutes by a shoulder around needle (Absatz) and is loaded fuel in the pressure chamber.Occupy an leading position according to which power and to decide, needle or to clinging to the direction motion on the valve seat or lifting from valve seat.
Relevant in Modern Internal-Combustion Engine is that the actual ejection time point is just in time with consistent by the predetermined time point of control gear.But if pressure surge took place in the pressure chamber by opening and closing of course of injection and needle, then could not accurately determine the pressure on the pressure side, thereby can not accurately determine breaking force.Like this, that time point of opening motion beginning that equals closing force and needle at breaking force is offset.This changes discharge time point and emitted dose, makes burning not carry out best and may improve hazardous emission.
Advantage of the present invention
In contrast to this, the advantage according to Fuelinjection nozzle of the present invention with claim 1 characteristic feature is to have weakened because the discharge time point fluctuation that the pressure in pressure chamber fluctuation causes.Constitute a pressure side on needle, it can be connected with the pressure chamber by a throttling position when needle rests on the valve seat for this reason.The pressure surge that is occurred is attenuated, and makes that the pressure in the fuel pressure specific pressure chamber of useful effect on pressure side has obviously less pressure surge.Like this, can accurately determine that time point that needle lifts from valve seat owing to the hydraulic pressure on the pressure side, make that being injected in optimum time point begins.
In the of the present invention first favourable scheme, the throttling position is opened when valve seat lifts at needle.Pressure side is loaded by whole fuel pressures of pressure chamber now thus, makes it possible to achieve opening fast of needle.
In another favourable scheme, the throttling position constitutes by the annulus between a valve seat and the needle.This throttling position is opened when valve seat lifts fast at needle, and the intensity of throttling can be by the width simple adjustment of annulus.
Throttling action not only depends on the structure at throttling position, but also depends on by the throttling position and be communicated with the pressure chamber and by the volume of that chamber of the pressure side limited boundary of needle.For further optimization, advantageously, a circular groove is set on needle, in this circular groove, constitute pressure side, wherein, circular groove surrounds needle on the needle circumference.The degree of depth by circular groove and configuration can influence the attenuation on the throttling position.Circular groove also can be constructed deeply like this, make on its outward edge constitute one around lip, between this lip and valve seat, constitute the throttling position.
Can stipulate that also pressure side constitutes as the part of valve sealing surface.In valve seat, constitute a circular groove in this case, between the radially outward edge of this circular groove and the pressure side on the valve sealing surface, form throttle chink.At this, needle can remain unchanged with respect to the needle that uses under other situation.In another favourable scheme, needle is placed in the hollow needle, and this hollow needle interrupts being communicated with of needle and pressure chamber also with the valve seat mating reaction and on resting on valve seat the time.Such hollow needle is used to control the other injection channel that at least one is drawn from valve seat.Lift from valve seat by hollow needle, fuel flows to this at least one spray-hole and impacts on needle and the pressure side thereof at this from the pressure chamber.Because unexpected pressure raises strong pressure surge can take place in this pressure side zone, this is by effectively being weakened according to the decay of the present invention on the throttling position.
In another favourable scheme, on the needle that is surrounded by hollow needle, be provided with second an additional pressure side, it constructs towards pressure side with lifting off a seat.This second pressure side is communicated with the pressure chamber by an annulus of constructing between needle and hollow needle, and this annulus forms one second throttling position.By hydraulic open power is distributed on the pressure side and second pressure side, this has opened up bigger configuration leeway for structural design.
Accompanying drawing
Shown in the drawings according to the present invention an embodiment of Fuelinjection nozzle.Accompanying drawing is represented:
Longitudinal section of Fig. 1 according to Fuelinjection nozzle of the present invention,
An enlarged view of the part of representing with II among Fig. 2 Fig. 1,
Another embodiment's of Fig. 3 the part figure identical with Fig. 2,
Another longitudinal section of Fig. 4 according to Fuelinjection nozzle of the present invention,
An enlarged view of the part of representing with V among Fig. 5 Fig. 4,
An enlarged view of the part of representing with VI among Fig. 6 Fig. 5.
Embodiment's explanation
In Fig. 1, express a longitudinal section according to Fuelinjection nozzle of the present invention.A valve body 1 has a hole 2, on the end of this Kong Zaiqi combustion chamber side by valve seat 11 limited boundaries of a taper, draw at least one but in most cases a plurality of injection channel 14 from valve seat 11, these injection channels feed when Fuelinjection nozzle is in the position in the internal-combustion engine of packing in the firing chamber to internal-combustion engine.Settled the needle 7 of a piston-like in hole 2 with longitudinal movement, this needle is sealed guiding in a guide section 102 in hole 2.Needle 7 attenuates towards valve seat 11, forms a pressure shoulder 9 towards the section that attenuates, and, carrying out the transition in the valve sealing surface 12 in the face of on the end of valve seat 11 at it, this valve sealing surface constitutes substantially taperedly.Between the wall in needle 7 and hole 2, between guide section 102 and valve seat 11, constitute a pressure chamber 5, it can be filled fuel under high pressure by a transfer passage of not representing in the accompanying drawings and extending in valve body 1.
Fig. 2 illustrates an enlarged view using the part of II mark among Fig. 1.Constitute a circular groove 20 between the section attenuating of valve sealing surface 12 and needle 7, this circular groove surrounds the whole circumference of needle 7.Circular groove 20 one side are by the first ring seamed edge 22, on the other hand by the second ring seamed edge, 24 limited boundaries.When needle 7 rests on the valve seat 11, the radially outward edge of circular groove 20, promptly first the ring seamed edge 22 with and valve seat 11 between formation a throttling position 26, by it, the doughnut that is limited by circular groove 20 and valve seat 11 is communicated with pressure chamber 5.Constitute a pressure side 30 by circular groove 20, except that pressure shoulder 9, this pressure side acts on a breaking force on needle 7 when relevant pressure loads.This pressure side 30 can have a bigger or little hydraulic pressure area by specific pressure shoulder 9.But under any circumstance closing force is definite like this: make that all be necessary against the closing force motion to the pressure-loaded of pressure shoulder 9 and pressure side 30 in order to make needle 7.If needle 7 lifts from valve seat 11, then throttling position 26 is opened, and fuel can unhinderedly flow to injection channel 14 by 5 process pressure sides 30 from the pressure chamber.
At this, the functional mode at throttling position 26 is as follows: flow through between valve sealing surface 12 and valve seat 11 to the injection channel direction by pressure chamber 5 at fuel between injection period, finally be ejected in the firing chamber by injection channel 14., promptly be seated on the valve seat 11 by needle 7 spraying closing under the end situation by Fuelinjection nozzle, the fuel that is in the pressure chamber 5 in the motion is braked suddenly.The kinetic energy of fuel is converted into compression work, constitutes the pressure surge in the pressure chamber 5.Do not disappear yet until the described pressure surge of injection beginning next time in some cases, make that the pressure on the pressure side 30 vibrates, on needle 7, can not obtain determined breaking force.Therefore because can not accurately know breaking force, the time point of opening of needle 7 also fluctuates, thus beginning of spraying fluctuate because just be the beginning that when breaking force overcomes closing force, reaches injection.On the contrary, by throttling position 26, the pressure surge in the pressure chamber 5 only continues to be delivered in the circular groove 20 with being attenuated, makes to act on a metastable pressure that has the pressure surge that is weakened on pressure side 30.This makes can have one by the breaking force of explication on needle 7, needle is just opened at the time point that calculates thus, and this is necessary in the Modern Internal-Combustion Engine of operation fast particularly, so that can reach the burning of noiseless and no harmful substance.At this, the degree of decay can be regulated by the size at throttling position 26 or the degree of depth of circular groove 20.
Fig. 3 illustrates another embodiment according to Fuelinjection nozzle of the present invention.Here, pressure side 30 constitutes as the part of valve sealing surface 12, wherein, extends between the line that pressure side 30 dots in the first ring seamed edge 22 and figure, and this first ring seamed edge constitutes at the transition position of valve sealing surface 12 to the section that attenuates of needle 7.This dotted line is represented the combustion chamber side seamed edge of a valve seat circular groove 28 of structure in valve seat 11.Constituting throttling position 26 between the seamed edge that deviates from the firing chamber 31 of valve seat circular groove 28 and the first ring seamed edge 22, works in the same manner in it and throttling position 26 embodiment illustrated in fig. 2.In case needle 7 lifts from valve seat 11, then throttling position 26 is opened, and fuel can unhinderedly flow through between valve sealing surface 12 and valve seat 11 and flow to injection channel 14.
Fig. 4 illustrates a longitudinal section of another Fuelinjection nozzle of the present invention.The structure and the Fuelinjection nozzle shown in Fig. 1 in valve body 1 and hole 2 are basic identical.Here, also constitute the needle that another becomes hollow needle 8 forms in hole 2 except that needle 7, in hollow needle 8, needle 7 is directed in first guiding area, 35 one of the neutralization of a combustion chamber side deviate from second guiding area 36 of firing chamber.Between these guiding areas 35,36, on needle 7, be provided with a heavy segment (Freistich), make the guiding of needle 7 in hollow needle 8 here do not take place.Not only needle 7 but also hollow needle 8 all are loaded a closing force to valve seat 11 directions at least part-time, and wherein, these shuttings are on the end that deviates from valve seat 11 of hollow needle 8 and needle 7, for example by spring force or hydraulic coupling.Constitute two row injection channels in valve seat 11, they are formed and are distributed by a plurality of injection channels 14 respectively and are arranged on the circumference of valve body 1.They form one first injection channel row 114 and one second injection channel row 214, and wherein, the first injection channel row 114 are arranged on the upstream of the second injection channel row 214.
In Fig. 5, amplify the part that Fig. 4 is shown once more with the V mark.The outer valves sealing surface 16 of hollow needle 8 has two conical surfaces, at their seal land 18 of transition position structure, make and a high surface pressure when hollow needle rests on the valve seat 11, in this zone, occurs, thereby guarantee reliable sealing on this position, in pressure chamber 5 even a very high pressure is arranged.The part of the outer valves sealing surface 16 of hollow needle 8 is loaded by the fuel pressure of pressure chamber 5, makes to obtain a breaking force opposite with closing force thus on hollow needle 8.
By 12 of valve sealing surfaces, needle 7 deviates from valve seat 11 ground and has a circular groove 20, as having in the injection valve shown in Figure 2.Constitute pressure side 30 in circular groove 20, the pressure-loaded by this pressure side acts on a breaking force on needle 7.Except that pressure side 30, on needle 7, constitute the face of one second pressure side 32 as other hydraulic pressure, it is made of a shoulder on the needle 7, and this shoulder directly is connected on first guide section 35 of needle 7.Second pressure side 32 can be communicated with pressure chamber 5 in the annulus that constitutes between needle 7 and the hollow needle 8 by one, wherein, and this one second throttling position 34 of formation, annulus.Like this, the pressure side 30 and second pressure side 32 can be communicated with pressure chamber 5 by throttling position 26,34., after lifting, opens towards the fuel of the second injection channel row 214 stream valve seat 11 at needle 7 in the top mode that had illustrated.Detailed view that should the zone shown in Figure 6, this figure are with an enlarged view of the part of VI mark among Fig. 5.
When burner oil, at Fig. 4,5, Fuelinjection nozzle work shown in 6 is as follows: the reduction of fuel pressure and/or the closing force on the hollow needle 8 by a rising in the pressure chamber 5 is producing a hydraulic open power on the pressure shoulder 9 and on the part that is loaded by the fuel of pressure chamber 5 at outer valves sealing surface 16.Hollow needle 8 lifts from valve seat 11 afterwards, and fuel laterally injection channel row 114 from pressure chamber 5 flow out, and fuel is ejected in the firing chamber of internal-combustion engine by these injection channel row.Because hollow needle 8 lifts from valve seat 11, this moment, needle 7 was loaded by the fuel pressure of pressure chamber 5, at this particularly pressure side 30 and second pressure side 32.On pressure side 30,32, occur because hollow needle is opened the pressure surge that produces fast and is weakened by throttling position 26,34, make on needle 7, to act on a definite breaking force.If the hydraulic open on the needle 7 is made every effort to overcome the clothes closing force, then needle 7 also lifts and the second injection channel row 214 are released from valve seat 11.When Fuelinjection nozzle was closed with end injection, pressure reduction in the pressure chamber 5 or the closing force on needle 7 and the hollow needle 8 raise.Thus, they slip back in the closed position and spray and finish.
Claims (11)
1. the Fuelinjection nozzle that is used for internal-combustion engine has a valve body (1), a structure hole (2) in this valve body, and at least one injection channel (14 at one end by a valve seat (11) limited boundary, is drawn from this valve seat in this hole; 114; 214), also has a needle (7), this needle is placed in longitudinal movement in the hole (2) and has a valve sealing surface (12) at it in the face of on the end of valve seat (11), this needle with this valve sealing surface and valve seat (11) mating reaction to open and close described at least one injection channel (14; 114; 214), and have a pressure chamber (5) that constitutes between the wall of needle (7) and hole (2), this pressure chamber can fill with fuel under high pressure, it is characterized in that, goes up at least one pressure side (30 in the face of valve seat (11) of structure at needle (7); 32), when needle (7) rested on the valve seat (11), this pressure side can pass through a throttling position (26; 34) be communicated with pressure chamber (5).
2. Fuelinjection nozzle according to claim 1 is characterized in that, when needle (7) from valve seat (11) when lifting, this throttling position (26; 34) be opened.
3. Fuelinjection nozzle according to claim 1 is characterized in that, this throttling position (26; 34) constitute by a slit between valve seat (11) and the needle (7).
4. Fuelinjection nozzle according to claim 1 is characterized in that, described pressure side (30) is gone up in a circular groove (20) at needle (7) and constituted, and this circular groove surrounds needle (7) on the needle circumference.
5. Fuelinjection nozzle according to claim 1 is characterized in that, described pressure side (30) is gone up at valve sealing surface (12) and constituted.
6. Fuelinjection nozzle according to claim 5 is characterized in that, this throttling position (26) is formation between the outward edge of a valve seat circular groove (28) that extends in valve seat (11) and described pressure side (30).
7. Fuelinjection nozzle according to claim 4 is characterized in that, this throttling position (26) constitutes between the radially outward edge of circular groove (20) and described valve seat (11).
8. Fuelinjection nozzle according to claim 1 is characterized in that, needle (7) is surrounded by a hollow needle (8), and this hollow needle separates needle (7) also with valve seat (11) mating reaction and on resting on valve seat (11) time with pressure chamber (5) hydraulic pressure.
9. Fuelinjection nozzle according to claim 8, it is characterized in that, go up formation one second pressure side (32) at needle (7), it is lifted off a seat to constitute and can pass through an annulus that constitutes between hollow needle (8) and needle (7) towards pressure side (30) (11) and be communicated with pressure chamber (5), wherein, this annulus forms throttling position (34).
10. according to the described Fuelinjection nozzle of one of aforementioned claim, it is characterized in that not only all basic taper of valve seat (11) but also valve sealing surface (12) ground constitutes, wherein, the point that constitutes the circular cone of conical surface points to the firing chamber direction respectively.
11. according to the described Fuelinjection nozzle of one of aforementioned claim, it is characterized in that, needle (7) and hollow needle (8) part-time ground are at least loaded to valve seat (11) direction by a closing force, and to connect (26) reverse with hydraulic coupling and closing force on the part that pressure chamber (5) are communicated with in the throttling of passing through of valve sealing surface (12).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE2002159169 DE10259169A1 (en) | 2002-12-18 | 2002-12-18 | Fuel injection valve for internal combustion engines |
| DE10259169.5 | 2002-12-18 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1717539A true CN1717539A (en) | 2006-01-04 |
| CN100593082C CN100593082C (en) | 2010-03-03 |
Family
ID=32403902
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN03825689A Expired - Fee Related CN100593082C (en) | 2002-12-18 | 2003-05-28 | Fuel injection valve for internal combustion engines |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP1576283A1 (en) |
| CN (1) | CN100593082C (en) |
| DE (1) | DE10259169A1 (en) |
| WO (1) | WO2004057180A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114763844A (en) * | 2021-01-15 | 2022-07-19 | 玛珂系统分析和开发有限公司 | Metering valve |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| TR200402050A2 (en) * | 2004-08-18 | 2006-03-21 | Robert Bosch Gmbh | Dual seating diameter injector with coaxial areal contact |
| DE102007013247A1 (en) * | 2007-03-20 | 2008-09-25 | Robert Bosch Gmbh | Sealing edge for conical seat valve |
| EP2239452A1 (en) * | 2009-03-30 | 2010-10-13 | Delphi Technologies Holding S.à.r.l. | Injection Nozzle |
| DE102009028089A1 (en) | 2009-07-29 | 2011-02-10 | Robert Bosch Gmbh | Fuel injection valve with increased small quantity capability |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1952816A (en) * | 1931-04-04 | 1934-03-27 | Bendix Res Corp | Fuel injector |
| DE4115457A1 (en) * | 1990-05-17 | 1991-11-21 | Avl Verbrennungskraft Messtech | Injection nozzle for IC engine - incorporates hollow needle controlling first group of injection holes and loaded towards closure position by spring |
| DE19634933B4 (en) * | 1996-08-29 | 2007-06-06 | Robert Bosch Gmbh | Fuel injection valve for internal combustion engines |
| AT2164U3 (en) * | 1997-08-07 | 1999-02-25 | Avl List Gmbh | INJECTION NOZZLE FOR A DIRECTLY INJECTING INTERNAL COMBUSTION ENGINE |
| DE19931891A1 (en) * | 1999-07-08 | 2001-01-18 | Siemens Ag | Fuel-injection valve for combustion engine |
| DE10031265A1 (en) * | 2000-06-27 | 2002-01-10 | Bosch Gmbh Robert | Fuel injection valve for internal combustion engines |
| DE10105681A1 (en) * | 2001-02-08 | 2002-08-29 | Siemens Ag | Fuel injection valve for an internal combustion engine |
| DE10115216A1 (en) * | 2001-03-28 | 2002-10-10 | Bosch Gmbh Robert | Fuel injection valve for internal combustion engines |
-
2002
- 2002-12-18 DE DE2002159169 patent/DE10259169A1/en not_active Withdrawn
-
2003
- 2003-05-28 EP EP03813515A patent/EP1576283A1/en not_active Withdrawn
- 2003-05-28 CN CN03825689A patent/CN100593082C/en not_active Expired - Fee Related
- 2003-05-28 WO PCT/DE2003/001734 patent/WO2004057180A1/en not_active Application Discontinuation
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114763844A (en) * | 2021-01-15 | 2022-07-19 | 玛珂系统分析和开发有限公司 | Metering valve |
Also Published As
| Publication number | Publication date |
|---|---|
| DE10259169A1 (en) | 2004-07-01 |
| EP1576283A1 (en) | 2005-09-21 |
| CN100593082C (en) | 2010-03-03 |
| WO2004057180A1 (en) | 2004-07-08 |
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