EP1989436A1 - Kraftstoffeinspritzvorrichtung für eine brennkraftmaschine - Google Patents
Kraftstoffeinspritzvorrichtung für eine brennkraftmaschineInfo
- Publication number
- EP1989436A1 EP1989436A1 EP07712013A EP07712013A EP1989436A1 EP 1989436 A1 EP1989436 A1 EP 1989436A1 EP 07712013 A EP07712013 A EP 07712013A EP 07712013 A EP07712013 A EP 07712013A EP 1989436 A1 EP1989436 A1 EP 1989436A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- fuel injection
- injection device
- valve element
- guide
- sleeve
- 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
- 239000000446 fuel Substances 0.000 title claims abstract description 74
- 238000002347 injection Methods 0.000 title claims abstract description 46
- 239000007924 injection Substances 0.000 title claims abstract description 46
- 238000002485 combustion reaction Methods 0.000 title claims abstract description 12
- 230000008878 coupling Effects 0.000 claims abstract description 20
- 238000010168 coupling process Methods 0.000 claims abstract description 20
- 238000005859 coupling reaction Methods 0.000 claims abstract description 20
- 239000012530 fluid Substances 0.000 claims description 8
- 230000000295 complement effect Effects 0.000 claims description 2
- 230000005484 gravity Effects 0.000 claims description 2
- 238000007789 sealing Methods 0.000 description 14
- 238000004519 manufacturing process Methods 0.000 description 9
- 230000033001 locomotion Effects 0.000 description 5
- 230000008901 benefit Effects 0.000 description 3
- 238000011161 development Methods 0.000 description 3
- 230000018109 developmental process Effects 0.000 description 3
- 238000009434 installation Methods 0.000 description 3
- 238000000926 separation method Methods 0.000 description 3
- 238000010276 construction Methods 0.000 description 2
- 238000012432 intermediate storage Methods 0.000 description 2
- ORQBXQOJMQIAOY-UHFFFAOYSA-N nobelium Chemical compound [No] ORQBXQOJMQIAOY-UHFFFAOYSA-N 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 238000003860 storage Methods 0.000 description 2
- 208000033999 Device damage Diseases 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000001427 coherent effect Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000011109 contamination Methods 0.000 description 1
- 238000013016 damping Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000007257 malfunction Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000010355 oscillation Effects 0.000 description 1
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
- 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
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
- F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
- F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for valve bodies
-
- 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
- F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
- F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
-
- 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
- F02M2547/001—Control chambers formed by movable sleeves
Definitions
- the invention relates to a fuel injection device for an internal combustion engine according to the preamble of claim 1.
- a fuel injection device with which the fuel can be injected directly into its associated combustion chamber of an internal combustion engine.
- a valve element is arranged in a housing, which in the region of a fuel outlet opening has a total pressure acting in the opening direction of the valve element.
- a control surface acting in the closing direction is present, which delimits a control chamber.
- the control surface acting in the closing direction is larger than the pressure surface acting in the opening direction when the valve element is open.
- Fuel pressure such as that provided by a fuel rail (rail).
- the pressure applied to the control surface is lowered until the hydraulic force resultant in the opening direction on the pressure surface exceeds the force acting in the closing direction. As a result, opening of the valve element is effected.
- this fuel injection device Prerequisite for the operation of this fuel injection device is a seal between that area in which the comparatively small acting in the opening direction Pressure surface is present, and that portion of the valve element in which the comparatively large acting in the closing direction control surface is present. Leakage fluid is discharged in the known fuel injection device from the region of the seal via a leakage line.
- Object of the present invention is to develop a fuel injection device of the type mentioned so that it is as simple and inexpensive builds and can be used at a very high operating pressure.
- the fuel injection device should work safely even in the presence of manufacturing tolerances.
- the freedom of design of the fuel injection device is significantly increased by the hydraulic coupling of two separate parts of the valve element, because it can be optimally adapted to the respective location within the fuel injection device, the respective parts of the valve element.
- the elastic properties of the valve element can be optimally adapted to the intended area of use by an appropriate choice of the material used and the dimensions.
- the manufacture of the valve element as a whole is considerably simplified since parts with a constant diameter are also used. This allows a structure of the fuel injection device with simple parts, which on the one hand facilitates the production and on the other hand allows a small construction.
- numerous components of previous devices can continue to be used for realizing the present invention.
- Another advantage of the hydraulic coupler is the compensation of tolerances, which simplifies the manufacture and assembly. The coupling of two parts of the valve element by means of a hydraulic coupler also allows the realization of a certain motion damping.
- the hydraulic coupler can be easily realized, and work required on the housing side is simplified.
- the guide element separate from the housing according to the invention, a misalignment of the sleeve relative to a housing-side sealing surface cooperating therewith is furthermore minimized. This comes into play particularly when the first part of the valve element is particularly long, and when the sleeve is guided particularly narrow on the first part of the valve element. Leaks in the coupling space are minimized through or even completely prevented. An elaborate and costly Einmessrata can therefore be omitted. A wear-related change in the functional properties of the fuel injection device according to the invention is reduced. By the leadership by means of the guide element manufacturing tolerances are compensated, which ensures a secure injector function.
- the fuel injection device is particularly simple in construction when the sleeve is supported on the guide element.
- a sealing surface on the guide element, on which the sleeve is supported are formed exactly at right angles to the guide axis of the guide element, so that a slanted position of the sleeve guided on the first part relative to the sealing surface on the guide element is particularly clearly minimized.
- Guide portion of the guide member or a complementary portion of the first part of the valve element is a leading from one side to the other side of the guide member fluid passage is present.
- Such a separation of the functions allows each an optimal design.
- the fluid passage can be formed by a guide play between the guide element and the first part of the valve element. This is manufacturing technology particularly easy to implement.
- the guide element comprises a stroke stop for the second part of the valve element.
- Measured values could be adjusted via a selection group of setting elements the correct stroke value.
- the production of the fuel injection device is further simplified when the guide element comprises a passage opening, preferably with a flow restrictor, which connects a pressure chamber in the region of the valve seat with a high-pressure chamber.
- the guide element between two housing bodies of the fuel injection device may be jammed, with its contact surfaces are designed with the housing bodies so that their centroid lies at least approximately on a central axis of a guide portion of the guide member.
- the sleeve is acted upon by a spring which is supported on a shoulder which is formed on the first part of the valve element.
- a preassemblable unit the at least the first part of the valve element, the Sleeve and the spring and optionally the guide element comprises.
- damage to the high-precision guidance between the sleeve and the first part of the valve element during final assembly are thereby avoided.
- the housing and thus its manufacture is simplified because now a smooth through hole can be provided without grading for receiving the valve element in the housing. This also improves the high-pressure resistance of the fuel injection device, and its greater storage volume
- sleeve is acted upon by a first spring, which is supported on a shoulder which is formed on one side of a ring member which is acted upon on the other side by a second spring, at least indirectly on Housing supported, and which is coupled via a coupling element with the valve element in the closing direction.
- the guide element can have a centering section, preferably a centering collar, which centers the guide element with respect to a housing body. At least indirectly, this also the valve element and other remote from the coupler areas of the housing are centered to each other.
- FIG. 1 shows a schematic representation of an internal combustion engine with a fuel
- Figure 2 is a schematic and partially sectioned view of a first
- FIG. 3 is a more detailed illustration of a portion of the fuel injector of Figure 2;
- Figure 4 is a plan view of a guide element of the fuel injection device of
- FIG. 3
- Figure 5 is a section along the line V-V of Figure 4.
- Figure 6 is a view similar to Figure 2 of a portion of a second embodiment of a fuel injection device
- Figure 7 is a view similar to Figure 2 of a portion of a third embodiment of a fuel injection device
- Figure 8 is a view similar to Figure 2 of a fourth embodiment.
- Figure 9 is a view similar to Figure 2 of a fifth embodiment.
- an internal combustion engine carries the reference numeral 10. Overall, it serves to drive a motor vehicle, not shown.
- a high-pressure conveyor 12 promotes
- Fuel from a fuel reservoir 14 in a fuel pressure accumulator 16 ("Rail").
- Fuel injectors 18 are connected, which inject the fuel directly into them associated combustion chambers 20.
- Each of the fuel injection devices 18 also has a low-pressure connection 21, via which they are connected to a low-pressure region, present with the fuel reservoir 14.
- the fuel injectors 18 may be formed in a first embodiment according to Figures 2 and 3:
- the fuel injector 18 shown therein comprises in the present embodiment, a housing 22 having a nozzle body 24, a main body 26 and an end body 28. It is also possible one-piece design of main body 26 and end body 28.
- a stepped recess 30 is provided in the longitudinal direction, in which a needle-like valve element 32 is received. This is in two parts: it consists of a control piston 34 and a nozzle needle 36th
- the nozzle needle 36 has pressure surfaces 38 which delimit a pressure chamber 40 and their hydraulic force resulting in the opening direction of the nozzle needle 36 shows. At its lower end in FIG. 2, the nozzle needle 36 cooperates with a housing-side valve seat (not numbered) in a manner not shown in FIG. In this way, fuel outlet openings 42 can be separated from the pressure chamber 40 or connected thereto.
- the nozzle needle 36 has a smaller diameter portion 44 and a larger diameter portion 46. With the section 46, the nozzle needle 36 is guided longitudinally displaceable in the nozzle body 24.
- the control piston 34 is received in the main body 26.
- An upper end region 48 of the control piston 34 in FIG. 2 is designed as a guide, which is received and guided in a sleeve-like extension of the end body 28.
- a spring 50 is supported by a through a
- Ring collar 52 formed shoulder on the control piston 34 and acts on the control piston 34 in the closing direction.
- the upper axial end face of the control piston 34 in FIG. 2 forms a hydraulic control surface 54 which acts in the closing direction of the valve element 32. It delimits, together with the end body 28, a control chamber 56.
- the control chamber 56 is connected via an inlet throttle 58, which is present in the sleeve-like extension of the end body 28, with an existing present between the sleeve-like extension of the end body 28 and the main body 26 annular space 60, which in turn is connected to the high pressure port 17.
- the annular space 60 is formed by the recesses 30 incorporated therein.
- the control chamber 56 is also connected to a 2/2-way valve 66 through an outlet throttle 64 provided in the end body 28. Depending on the switching position, this connects or blocks the outlet throttle 64 to the Low pressure port 21 down.
- the annular space 60 is also connected via at least one channel 68 to the pressure chamber 40.
- Guide element 70 has a base plate 72 and a molded-on this cylindrical extension 74 which forms a guide collar, which has a centering function. Concentric with the extension 74, a guide bore 76 forming a guide region is present in the guide element 70, which cooperates with a guide on the lower end region 77 of the control piston 34 in FIGS. 2 and 3.
- the upper and lower sides of the base plate 72 are formed as high-pressure sealing surfaces 78, in the installation position a secure seal of the housing 22, in particular the annular space 60 and lying within the guide member 70 spaces, with respect to the environment of the fuel injector 18 is ensured.
- the position of the center of gravity of the center axis also belongs. This is achieved by a corresponding design of the outer contour of the base plate 72, in such a way that the centroid is at least approximately on a central axis (not shown) of the guide bore 76.
- a bore approach 80 is incorporated, which is concentric with the guide bore 76 and has a larger diameter than this.
- the diameter of the bore extension 80 is also greater than the diameter of the portion 46 of the nozzle needle 36. In this way, the bore extension 80 forms a stroke stop for the nozzle needle 36 in a manner yet to be illustrated.
- the base plate 72 of the guide element 70 is also an eccentric passage opening or bore 82 introduced in the installation position part of
- Channel 68 is.
- the passage opening 82 must comprise a flow restrictor, as indicated in Figure 2.
- a sealing surface representing an end face 85 of the extension 74 is worked very precisely at right angles to the axis of the guide bore 76.
- the sleeve 88 belongs to a hydraulic coupler 92, through which the first part of the valve element 32, namely the control piston 34, with the second part of the valve element 32, namely the nozzle needle 36 is coupled.
- the hydraulic coupler 92 for this purpose comprises a hydraulic coupling chamber 94 with subspaces 94a and 94b, between the sleeve 88, the guide member 70, the lower end portion of the control piston 34 in Figures 2 and 3 and the upper end portion of the nozzle needle in Figures 2 and 3 36 is formed.
- the volume formed by the guide play between the guide bore 76 and the guide 77 on the control piston 34 is dimensioned so that the subspaces 94a and 94b of the coupling space 94 form a coherent control volume without hydraulic influence. Said volume thus forms a fluid passage from one side to the other of the guide element 70.
- the fluid passage could also comprise at least one groove in the guide bore 76 and / or at least one flattening on the control piston 34.
- the fuel injection device 18 shown in Figures 2 and 3 operates as follows: In the initial state, with de-energized switching valve 66, the control chamber 56 is separated from the low pressure port 21 and connected via the inlet throttle 58 to the high pressure port 17 and thus to the rail 16. In the control chamber 56 is thus the same pressure as in the annulus 60. This prevails over the channel 68 in the pressure chamber 40. Due to certain unavoidable leaks by the leadership of the nozzle needle 36 in the nozzle body 24 and the sleeve 88 on the control piston 34 is also in Coupling chamber 94 this pressure on.
- the switching valve 66 is energized, the outlet throttle 64 is connected to the low-pressure connection 21. As a result, the pressure in the control chamber 56 decreases. The sum now results in a force acting in the opening direction of the control piston 34 force. This now begins to move against the force of the spring 50 in Figures 2 and 3 upwards. As a result of the increase in volume, the pressure in the coupling space 94 drops. Due to the pressure relationship between the force difference between an end surface 96 of the nozzle needle 36 delimiting the coupling space 94 and the pressure surfaces 38, the nozzle needle 36 also moves in the figures 2 and 3 upwards, so it rises from its valve seat in the region of the fuel outlet openings 42. Thus, fuel from the rail 16 via the high-pressure port 17, the annular space 60, the channel 68, the pressure chamber 40 and the fuel outlet openings 42 are injected into the combustion chamber 20.
- the stroke of the nozzle needle 36 is limited by the stroke stop 80.
- the stroke of the nozzle needle 36 can, as shown in Figures 2 to 5, on the processing of the bore approach 80 or by a paragraph processing on the end face 96 of the nozzle needle 36 can be realized.
- the sealing surface 78 simultaneously forms the stroke stop for the end face 96 of the nozzle needle 36 (see Figure 6).
- control piston 34 will continue its lifting movement. Therefore, the free lift of the control piston 34 must always be greater than the maximum stroke of the nozzle needle 36. Due to the narrow guide clearance between the sleeve 88 and the control piston 34 and the resulting low leakage into the coupling chamber 94, the control piston 34 is braked so much in its stroke movement, that he can do only a little extra movement.
- a Hubeinstellelement 97 is disposed between the end face 96 and the stroke stopper 80, through which in addition an adjustment of a desired stroke of the nozzle needle 36 is possible.
- the switching valve 66 is brought back into its closed position, in which the connection of the control chamber 56 is locked to the low pressure port 21. Via the inlet throttle 58, the pressure in the control chamber 56 increases continuously. As a result, the control piston 34 is again moved in the closing direction, since the pressure in the coupling chamber 94 is initially lower than in the control chamber 56. As a result, the pressure rises in the
- FIG. 8 shows an alternative embodiment of a fuel injection device 18. It is not only here, but in principle that such elements and areas that have equivalent functions to previously described elements and areas, the same reference numerals and are not explained again in detail. For the sake of simplicity, only those reference signs which are required to explain the differences from a previous exemplary embodiment are essentially entered.
- the spring 90 which urges the sleeve 88 surrounding the coupling space 94 against the guide element 70, is not supported on the main body 26 but on the annular collar 52 or the shoulder formed by it. Both springs 90 and 50 thus act on the same annular collar 52 of the control piston 34. When designing the spring 50, therefore, the force component of the spring 90 acting in the opening direction must be taken into account.
- Another difference to the embodiment of Figures 2 and 3 lies in the two-part end body 28. This was divided so that the outlet throttle 64 in the remaining end body 28 and the inlet throttle 58 is in the now separate sleeve 99.
- the spring 50 presses the sleeve 99 via the sealing surface or sealing edge (without reference numeral) against the end body 28 and thus generates a sufficient separation of the annular space 60 relative to the control chamber 56th
- the advantage of the fuel injector shown in Figure 8 18 over that of Figures 2 and 3 is that the control piston 34 with the sleeve 99, the spring 50, the spring 90 and the sleeve 88 can form a preassembled unit, so that at the later assembly of all components of the fuel injection device 18, the sleeves 99 and 88 no longer need to be separated from the control piston 34.
- the recess 30 in the main body 26 of the housing 22 may be designed as a smooth through-hole, which allows the establishment of a comparatively large annular space 60 and a correspondingly large storage volume for the fuel.
- FIG. 9 A similar variant is shown in FIG. 9: In this case, instead of an annular collar 52 in the control piston 34, there is a circumferential groove 100, into which an annular coupling element 102 is inserted, against which, in turn, only in the closing direction of the valve element 32, a ring element 104 is supported. At this attack on the one hand, the spring 90 and on the other hand, the spring 50. Again, the control piston 34 with the sleeve 99, the spring 50, the sleeve 88 and the spring 90th and the coupling element 102 and the ring element 104 form a preassembled unit, which can be mounted as such and used in the final assembly in the recess 30 in the main body 26 of the housing 22.
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102006008648A DE102006008648A1 (de) | 2006-02-24 | 2006-02-24 | Kraftstoffeinspritzvorrichtung für eine Brennkraftmaschine |
PCT/EP2007/050300 WO2007098975A1 (de) | 2006-02-24 | 2007-01-12 | Kraftstoffeinspritzvorrichtung für eine brennkraftmaschine |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1989436A1 true EP1989436A1 (de) | 2008-11-12 |
EP1989436B1 EP1989436B1 (de) | 2010-03-17 |
Family
ID=37907846
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP07712013A Active EP1989436B1 (de) | 2006-02-24 | 2007-01-12 | Kraftstoffeinspritzvorrichtung für eine brennkraftmaschine |
Country Status (8)
Country | Link |
---|---|
US (1) | US8146839B2 (de) |
EP (1) | EP1989436B1 (de) |
JP (1) | JP4898840B2 (de) |
CN (1) | CN101389852B (de) |
BR (1) | BRPI0708231B1 (de) |
DE (2) | DE102006008648A1 (de) |
RU (1) | RU2426002C2 (de) |
WO (1) | WO2007098975A1 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1911966A2 (de) | 2006-10-10 | 2008-04-16 | Robert Bosch Gmbh | Kraftstoffinjektor für eine Brennkraftmaschine |
Families Citing this family (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102008040680A1 (de) | 2008-07-24 | 2010-01-28 | Robert Bosch Gmbh | Kraftstoff-Injektor |
DE102008041561B4 (de) | 2008-08-26 | 2022-05-19 | Robert Bosch Gmbh | Kraftstoffinjektor sowie Auslegungsverfahren für einen Kraftstoffinjektor |
DE102009007095A1 (de) * | 2009-02-02 | 2010-08-05 | Continental Automotive Gmbh | Einspritzventil |
DE102010030383A1 (de) | 2010-06-23 | 2011-12-29 | Robert Bosch Gmbh | Kraftstoffeinspritzvorrichtung mit hydraulischem Koppler |
DE102010039980A1 (de) | 2010-08-31 | 2012-03-01 | Man Diesel & Turbo Se | Zentriervorrichtung für eine Kraftstoffeinspritzdüse |
US8989088B2 (en) | 2011-01-07 | 2015-03-24 | Integrated Device Technology Inc. | OFDM signal processing in a base transceiver system |
CN102996309B (zh) * | 2012-12-04 | 2016-02-03 | 袁辉 | 高压共轨喷油器 |
DE102013221484A1 (de) * | 2013-10-23 | 2015-04-23 | Robert Bosch Gmbh | Kraftstoffinjektor |
CN104454274B (zh) * | 2014-12-03 | 2017-09-29 | 中国第一汽车股份有限公司无锡油泵油嘴研究所 | 一种喷油器 |
CN104847556A (zh) * | 2015-05-19 | 2015-08-19 | 中国重汽集团重庆燃油喷射系统有限公司 | 无静态泄漏喷油器 |
GB201520206D0 (en) * | 2015-11-17 | 2015-12-30 | Delphi Internat Operations Luxembourg S À R L | Fuel injector |
DE102018212665A1 (de) * | 2018-07-30 | 2020-01-30 | Robert Bosch Gmbh | Kolbenpumpe und Kraftstofffördereinrichtung für kryogene Kraftstoffe |
Family Cites Families (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CH495504A (de) * | 1968-08-28 | 1970-08-31 | Sopromi Soc Proc Modern Inject | Brennstoff-Einspritzventil mit elektromagnetischer Betätigung |
DE59308610D1 (de) * | 1992-12-23 | 1998-07-02 | Ganser Hydromag | Brennstoffeinspritzventil |
DE19500706C2 (de) * | 1995-01-12 | 2003-09-25 | Bosch Gmbh Robert | Zumeßventil zur Dosierung von Flüssigkeiten oder Gasen |
JPH08296521A (ja) * | 1995-02-28 | 1996-11-12 | Isuzu Motors Ltd | インジェクタの針弁制御装置 |
DE19900037A1 (de) * | 1999-01-02 | 2000-07-06 | Bosch Gmbh Robert | Kraftstoffeinspritzventil |
DE10006111A1 (de) * | 2000-02-11 | 2001-08-30 | Bosch Gmbh Robert | Kraftstoffeinspritzventil |
DE10014450A1 (de) * | 2000-03-23 | 2001-09-27 | Bosch Gmbh Robert | Vorrichtung zur Einspritzung von Kraftstoff mit variablem Einspritzdruckverlauf |
DE10033428C2 (de) * | 2000-07-10 | 2002-07-11 | Bosch Gmbh Robert | Druckgesteuerter Injektor zum Einspritzen von Kraftstoff |
DE10248379A1 (de) * | 2002-10-17 | 2004-04-29 | Robert Bosch Gmbh | Kraftstoff-Einspritzvorrichtung für eine Brennkraftmaschine |
DE102004004006A1 (de) * | 2004-01-27 | 2005-08-11 | Robert Bosch Gmbh | Integrierter hydraulischer Druckübersetzer für Kraftstoffinjektoren an Hochdruckspeichereinspritzsystemen |
DE102004024282A1 (de) * | 2004-05-15 | 2005-12-01 | Robert Bosch Gmbh | Pumpe-Düse-Einheit und Pumpe-Leitung-Düse-Einheit |
DE102004035313A1 (de) | 2004-07-21 | 2006-02-16 | Robert Bosch Gmbh | Kraftstoffinjektor mit zweistufigem Übersetzer |
DE102004037124A1 (de) * | 2004-07-30 | 2006-03-23 | Robert Bosch Gmbh | Common-Rail-Injektor |
DE102005004738A1 (de) * | 2005-02-02 | 2006-08-10 | Robert Bosch Gmbh | Kraftstoffinjektor mit direkter Nadelsteuerung für eine Brennkraftmaschine |
DE102005012929A1 (de) * | 2005-03-21 | 2006-09-28 | Robert Bosch Gmbh | Kraftstoffinjektor mit direkter Steuerung des Einspritzventilglieds und variabler Übersetzung |
-
2006
- 2006-02-24 DE DE102006008648A patent/DE102006008648A1/de not_active Withdrawn
-
2007
- 2007-01-12 WO PCT/EP2007/050300 patent/WO2007098975A1/de active Application Filing
- 2007-01-12 DE DE502007003146T patent/DE502007003146D1/de active Active
- 2007-01-12 JP JP2008555720A patent/JP4898840B2/ja active Active
- 2007-01-12 EP EP07712013A patent/EP1989436B1/de active Active
- 2007-01-12 CN CN2007800066789A patent/CN101389852B/zh active Active
- 2007-01-12 RU RU2008137722/06A patent/RU2426002C2/ru active
- 2007-01-12 BR BRPI0708231A patent/BRPI0708231B1/pt active IP Right Grant
- 2007-01-12 US US12/096,082 patent/US8146839B2/en active Active
Non-Patent Citations (1)
Title |
---|
See references of WO2007098975A1 * |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1911966A2 (de) | 2006-10-10 | 2008-04-16 | Robert Bosch Gmbh | Kraftstoffinjektor für eine Brennkraftmaschine |
EP1911966A3 (de) * | 2006-10-10 | 2009-07-01 | Robert Bosch Gmbh | Kraftstoffinjektor für eine Brennkraftmaschine |
Also Published As
Publication number | Publication date |
---|---|
JP4898840B2 (ja) | 2012-03-21 |
WO2007098975A1 (de) | 2007-09-07 |
JP2009527686A (ja) | 2009-07-30 |
DE502007003146D1 (de) | 2010-04-29 |
BRPI0708231A2 (pt) | 2011-05-17 |
DE102006008648A1 (de) | 2007-08-30 |
EP1989436B1 (de) | 2010-03-17 |
CN101389852A (zh) | 2009-03-18 |
RU2008137722A (ru) | 2010-03-27 |
CN101389852B (zh) | 2011-07-27 |
US20090020632A1 (en) | 2009-01-22 |
RU2426002C2 (ru) | 2011-08-10 |
US8146839B2 (en) | 2012-04-03 |
BRPI0708231B1 (pt) | 2018-11-21 |
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