EP1651861A1 - Schaltventil mit druckausgleich für einen kraftstoffinjektor mit druckverstärker - Google Patents
Schaltventil mit druckausgleich für einen kraftstoffinjektor mit druckverstärkerInfo
- Publication number
- EP1651861A1 EP1651861A1 EP04738705A EP04738705A EP1651861A1 EP 1651861 A1 EP1651861 A1 EP 1651861A1 EP 04738705 A EP04738705 A EP 04738705A EP 04738705 A EP04738705 A EP 04738705A EP 1651861 A1 EP1651861 A1 EP 1651861A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- valve
- pressure chamber
- fuel injector
- chamber
- 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 67
- 238000002347 injection Methods 0.000 claims abstract description 37
- 239000007924 injection Substances 0.000 claims abstract description 37
- 238000007789 sealing Methods 0.000 claims abstract description 37
- 230000006835 compression Effects 0.000 claims abstract description 10
- 238000007906 compression Methods 0.000 claims abstract description 10
- 238000002485 combustion reaction Methods 0.000 description 14
- 238000004519 manufacturing process Methods 0.000 description 9
- 238000013016 damping Methods 0.000 description 6
- 238000003754 machining Methods 0.000 description 3
- 238000005516 engineering process Methods 0.000 description 2
- 239000000243 solution Substances 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000003860 storage Methods 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
- F02M57/00—Fuel-injectors combined or associated with other devices
- F02M57/02—Injectors structurally combined with fuel-injection pumps
- F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
- F02M57/025—Injectors structurally combined with fuel-injection pumps characterised by the pump drive hydraulic, e.g. with pressure amplification
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/20—Varying fuel delivery in quantity or timing
- F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
- F02M59/366—Valves being actuated electrically
-
- 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
- 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
- F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
-
- 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
- F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
- F02M63/0045—Three-way 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
- F02M63/0073—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
Definitions
- Stroke-controlled injection systems with a high-pressure storage space are used to introduce fuel into the combustion chambers of direct-injection internal combustion engines.
- the advantage of these injection systems is that the injection pressure into the combustion chamber can be adapted over a wide range to the load and speed of the internal combustion engine.
- a high injection pressure is required to reduce emissions and achieve high specific performance.
- the achievable pressure level of high-pressure fuel pumps is limited for reasons of strength, so that pressure boosters in the fuel injectors are used to further increase the pressure in fuel injection systems.
- DE 101 23 913 AI relates to a fuel injection device for internal combustion engines with a fuel injector that can be supplied by a high-pressure fuel source. Between the fuel injector and the high-pressure fuel source, a pressure transmission device having a movable pressure booster piston is connected.
- the pressure booster piston separates a space that can be connected to the K-fuel high pressure source from a high pressure space that is connected to the fuel injector.
- the fuel pressure in the high-pressure chamber can be varied by filling a rear area of the pressure booster device with fuel or by emptying the rear area of fuel.
- the fuel injector has a movable closing piston for opening and closing injection openings.
- the closing piston protrudes into a closing pressure chamber, so that fuel pressure can be applied to the closing piston to achieve a force acting on the closing piston in the closing direction.
- the closing pressure chamber and the rear chamber are formed by a common closing pressure rear chamber, all partial areas of the closing pressure rear chamber being permanently connected to one another for the exchange of fuel.
- a pressure chamber is provided for supplying fuel to the injection openings and for applying a force acting in the opening direction to the closing piston.
- a high-pressure chamber is connected to the high-pressure fuel source in such a way that, apart from pressure fluctuations, at least the fuel pressure of the high-pressure fuel source can constantly be present in the high-pressure chamber, the pressure chamber and the high-pressure chamber through a common injection chamber are formed. All parts of the injection chamber are permanently connected to each other for the exchange of fuel.
- DE 102294 15.1 relates to a device for damping the needle stroke on pressure-controlled fuel injectors.
- a device for injecting fuel into a combustion chamber of an internal combustion engine which comprises a fuel injector which can be acted upon by fuel under high pressure via a high-pressure source.
- the fuel injector is actuated via a metering valve, an injection valve member being enclosed by a pressure chamber and the injection valve member being acted upon in the closing direction by a closing force.
- the injection valve member is associated with an independently movable damping element, which delimits a damping space and has at least one overflow channel for connecting the damping space to a further hydraulic space.
- the control of the fuel injector is carried out with a 3/2-way valve, whereby although an inexpensive and space-saving injector can be represented, this valve has to control a relatively large return flow rate of the pressure intensifier.
- a direct-switching switching valve designed as a 3/2-way valve which is completely pressure-balanced. Both a sealing seat and a slide seal are formed on the valve needle of the switching valve. There is a first one on the switching valve above a low pressure chamber first pressure chamber and a second pressure chamber. To achieve pressure equalization, the diameter of the sealing seat and the diameter of the valve needle are almost identical, so that the fuel pressure from a first pressure chamber and the fuel pressure from a second pressure chamber are unable to exert any forces on the valve needle.
- an extension can be formed on the valve needle at the end facing the low pressure chamber.
- the sealing seat which is located above the low pressure chamber, can be designed either as a flat seat or as a conical seat.
- the actuator actuating the direct switching switching valve can be designed both as a piezo actuator and as a magnetic actuator.
- needle stroke damping can be provided with which the movement of the injection valve member can be limited in the smallest possible way.
- the solution according to the invention has the advantage over switching valves designed as 3/2-servo valves that they are much simpler and therefore more economical to manufacture in terms of manufacturing effort, since only a one-piece valve needle is required and the hydraulic control chamber with the tolerance-critical ones Chokes and the necessary pilot valve are not required.
- the design in a one-piece valve housing ensures a smaller number of parts and a high manufacturing accuracy between the needle guide and the needle seat.
- the valve housing can advantageously also be formed in two parts, in connection with a sealing seat designed as a flat seat.
- the sealing seat of the flat seat lies in a second body part designed as a sealing plate.
- Figure 1 shows a fuel injector with pressure booster, which is controlled via the differential pressure chamber and is switched via a direct switching 3/2-way valve and
- FIG. 2 shows a further embodiment variant of a fuel injector, the 3/2 switching valve of which has a valve needle on which an extension is formed in the region of the low-pressure space of the switching valve, and
- Figure 3 is a multi-part valve housing of a direct switching 3/2-way valve.
- FIG. 1 shows a fuel injector with a pressure booster, which can be controlled via a differential pressure chamber and can be actuated by means of a direct-switching 3/2-way valve.
- a pressure source 1 which can be, for example, a high-pressure accumulator (common rail) of a fuel injection system, is connected to a pressure booster 3 via a high-pressure feed line.
- the high-pressure feed line 2 opens into a working space 4 of the pressure amplifier 3.
- the working space 4 is separated from a differential pressure space 6 which can be relieved of pressure and acted upon by means of a booster piston 5.
- An end face of the booster piston 5 acts on a compression chamber 8 of the pressure booster 3.
- a return spring 7 is assigned to the booster piston 5 of the pressure booster 3 and supports the return movement of the booster piston 5 to its rest position.
- An overflow line 9 extends from the working space 4 of the pressure booster 3 to a switching valve 22.
- the differential pressure chamber 6 of the pressure booster 3 is also connected via a control line 10 to the switching valve 22, which can be actuated via an actuator 37.
- the actuator 37 can be designed as a magnetic valve comprising a magnetic coil 38 or can also be designed as a piezo actuator.
- a pressure chamber supply line 11 extends from the compression chamber 8 of the pressure booster 3 to a pressure chamber 12 which is formed in the body of a fuel injector.
- An injection valve member 13 is received in the body of the fuel injector.
- the injection valve member 13 has a pressure stage 14 in the area of the pressure chamber 12.
- the injection valve member 13 is acted upon in its closing direction by a closing spring 15 accommodated in a control chamber.
- An annular gap 16 extends from the pressure chamber 12, via which the pressure chamber 12 is pressurized Fuel injection openings 17 flows.
- the injection openings 17 open into a combustion chamber 18 of a self-igniting internal combustion engine.
- a branch 20 branches from the branch line, in which a filling valve 21 is accommodated, which Compression chamber 8 of the pressure booster 3 opens and serves to refill it when the booster piston 5 is reset.
- the control line 10 leading from the differential pressure chamber 6 to the switching valve 22 opens into a second pressure chamber 29 in the valve housing 35 of the switching valve 22.
- the switching valve 22 comprises a valve needle 23.
- the valve needle 23 has a diameter 27 in its guide area within the one-piece valve housing 35, which corresponds to a diameter 26 on a sealing seat 24 on the valve needle 23.
- the one-piece valve needle 23 of the switching valve 22 which is designed as a direct-switching 3/2-way valve, is pressure-balanced.
- the one-piece valve needle 23 of the switching valve 22 has a slide seal 25.
- the overflow line 9 opening into the first pressure chamber 28 of the switching valve 22 from the working chamber 4 can be closed against the second pressure chamber 29.
- the sealing seat 24 is closed, the second pressure chamber 29 is closed against a low pressure chamber 30.
- a return 32.2 on the low-pressure side branches off from the low-pressure chamber 30 and leads to a fuel reservoir, not shown in FIG. 1.
- the slide seal 25 of the one-piece valve needle 23 is formed by a control edge 33 on the housing side and a control edge 34 on the valve needle side and is located opposite the sealing seat 24 at the low-pressure end of the one-piece valve needle 23.
- the valve needle 23 is advantageously formed in one piece and embedded in a valve housing 35, which is also formed in one piece.
- the valve needle 23 is acted upon in the closing direction by a closing spring 36, so that the sealing seat 24 always closes the second pressure chamber 29 for the return 32.2 on the low-pressure side when the actuator 37 is not actuated.
- the sealing seat 24 can be designed as a sealing edge or as a sealing surface.
- the actuator 37 is designed as a magnetic actuator, containing a coil 38. Opposite the lower annular surface of the coil 38 of the magnetic actuator, the one-piece valve needle 23 has a plate 39.
- the switching valve 22 In the deactivated idle state of the pressure booster 3, the switching valve 22 is in a closed position due to the closing spring 36 acting on the valve needle 23. In this position, shown in FIG. 1, of the one-piece valve needle 23, the differential pressure chamber 6 is connected to the working chamber 4 via the opened slide seal 25 of the switching valve 22 and the control line 10, the overflow line 9. As a result, the same pressure prevails in the differential pressure chamber 6 of the pressure booster 3 as in the working chamber 4 of the pressure booster 3. In contrast, due to the closing force of the closing spring 36, the sealing seat 24 is closed to the low pressure chamber 30, so that the differential pressure chamber 6 is decoupled from the low pressure side return and the pressure booster 3 is in itself is in its pressure-balanced state and no pressure intensification occurs.
- the differential pressure chamber 6 is relieved of pressure. This is done by a control, i.e. opening of the switching valve 22, which can take place, for example, by energizing the solenoid coil 38, so that the plate 39 on the top of the valve needle 23 is pulled in the direction of the coil 38. Because of this, the valve needle 23 moves upward. In this case, the control edges 33, 34 of the slide seal 25 are covered so that it closes, whereas the sealing seat 24 opens at the low-pressure end of the one-piece valve needle 23. As a result, the differential pressure space 6 is decoupled from the working space 4, i. H.
- the pressure source 1 and the differential pressure chamber 6 are pressure-relieved via the control line 10, which opens into the second pressure chamber 29, the open sealing seat 24 in the low-pressure side return 32.2.
- the booster piston 5 of the pressure booster 3 moves into the compression space 8, so that fuel under extremely high pressure passes from the latter into the pressure space 12 via the pressure space feed line 11.
- the hydraulic force building up in the pressure chamber 12 acts on the hydraulically active surface of the pressure stage 14 and moves the injection valve member 13 into an open position against the action of the closing spring 15, so that fuel flowing from the pressure chamber 12 via the annular gap 16 into the injection openings 17 the combustion chamber 18 of the internal combustion engine can be injected.
- the switching valve 22, which is designed as a direct switching 3/2-way valve, is activated, ie closed.
- the one-piece valve needle 23 moves into its lower starting position via the action of the closing spring 36.
- the sealing seat 24 closes and the slide seal 25 opens, formed by the control edges 33 and 34, respectively.
- the overflow line 9, the first pressure chamber 28, the second pressure chamber 29 and the control line 10 is built in the differential limit pressure chamber 6 of the pressure booster 3 system pressure, whereby the pressure booster 3 is deactivated, that is, supported by the return spring 7 returns to its rest position.
- the injection valve member 13 closes because the pressure in the pressure chamber 12 also decreases when the compression chamber 8 is depressurized.
- the pressure balance of the switching valve 22, which is designed as a direct switching 3/2-way valve, is determined by matching diameters 26 in the area of the sealing seat 24 and in the area of the valve needle 23, cf. Needle diameter 27 reached in the one-piece housing 35. As a result, both the fuel pressure in the first pressure chamber 28 and the fuel pressure in the second pressure chamber 29 exert no forces on the one-piece valve needle 23.
- this adjusting spring can also be accommodated in another room of the pressure booster 3, or a restoring force can be generated hydraulically.
- the sealing seat 24 can be designed, for example, as a flat seat or, as indicated in FIG. 1, as a conical seat. In conjunction with a two-part valve housing, considerable manufacturing advantages can be achieved by designing the sealing seat 24 as a flat seat. In the case of a two-part valve housing 35, the sealing seat 24 in the form of a flat seat can lie in a second valve housing part in the form of a sealing plate 35.2 (FIG. 3). Due to the improved accessibility to the machining of the sealing seat 24 and of the slide edges and valve chambers, a more cost-effective production of the valve can be achieved when using a two-part valve housing. In addition to the variant of the actuator 37 shown in FIG.
- a piezo actuator can also be used to actuate the one-piece valve needle 23 of the direct-switching 3/2-way valve 22.
- a damping piston can be assigned to the injection valve 13, which dampens the opening speed of the injection valve member 13 when the pressure booster 3 is activated and by its compression valve. Dampens space 8 flowing into the pressure space 12, fuel under increased pressure.
- FIG. 2 shows a further embodiment variant of a direct switching 3/2-way valve, the valve needle of which has an extension on the low-pressure side.
- valve needle 23 In contrast to the embodiment variant shown in FIG. 1, there is an extension 31 on the valve needle 23 below the sealing seat 24, which protrudes into the low-pressure chamber 30.
- a first return 32.1 on the medium pressure side runs above the extension 31 of the one-piece valve needle 23, while a second return 32.2 on the low pressure side branches off below the extension 31.
- the valve needle 23 according to the embodiment variant according to FIG. 2 comprises a slide seal 25 which is formed by a control edge 34 on the valve needle side and a control edge 33 on the valve housing side.
- the guide diameter 27 of the valve needle 23 and the seat diameter 26 of the sealing seat 24 correspond to one another.
- the mode of operation of the embodiment variant corresponds to the mode of operation of the fuel injector with pressure booster 3 shown in FIG. 1, which is actuated via the direct-switching switching valve 22, the valve needle 23 of which without the extension 31 shown in FIG Low pressure room 30 is procured.
- the switching valve 22 is a 3/2-way direct switching - Valve formed, and due to the one-piece valve needle 23, be it with or without extension 31, it can be manufactured much more simply and more cheaply in terms of production technology and can ensure the one-piece design of the valve housing 35 of the switching valve 22 designed as a direct switching 3/2-way valve sufficient manufacturing accuracy and thus a tolerable tightness in high-pressure injection systems for direct-injection internal combustion engines.
- FIG. 3 The design variant of a direct switching 3 / 2- Directional control valves with a multi-part valve housing is shown in Figure 3.
- the multi-part valve housing 35 comprises a first housing part 35.1, in which the valve needle 23 of the directly switching switching valve 22 is guided.
- a plate 39 is formed opposite a magnetic coil 38, which in turn is acted upon by the closing spring 36.
- the housing-side control edge 33 which interacts with the valve-needle-side control edge 34, is formed.
- the sealing seat 24 is preferably designed as a flat seat.
- the low-pressure chamber 30 is sealed by the sealing seat 24.
- This can be designed in a particularly simple manner in terms of production technology as a blind hole from which a second return 32.2 on the low-pressure side branches off.
- the control line 10 opens into the second pressure chamber 29, the overflow line 9 branching off from the working chamber 4 of the pressure booster 3 opens into the first pressure chamber 28.
- the second valve housing part 35.2 of the multi-part valve housing 35 can be an independent component which is formed separately from the injector body of a fuel injector.
- the second valve housing part 35.2 designed as a sealing plate can, however, just as well be formed by the injector housing itself.
- the return lines 32.1, 32.2 shown on the low-pressure side in the embodiment variant according to FIG. 2 can be brought together and connected to both return lines 32.1, 32.2 together with the return system.
- the switching valve 22 which is proposed as a direct switching 3/2-way valve and is proposed according to the invention, can be used with pressure boosters 3 which are controlled by controlling the pressure in the differential pressure chamber 6.
- pressure boosters 3 which are controlled by controlling the pressure in the differential pressure chamber 6.
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
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10334771A DE10334771A1 (de) | 2003-07-30 | 2003-07-30 | Schaltventil mit Druckausgleich für einen Kraftstoffinjektor mit Druckverstärker |
PCT/DE2004/001254 WO2005015000A1 (de) | 2003-07-30 | 2004-06-17 | Schaltventil mit druckausgleich für einen kraftstoffinjektor mit druckverstärker |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1651861A1 true EP1651861A1 (de) | 2006-05-03 |
EP1651861B1 EP1651861B1 (de) | 2010-09-01 |
Family
ID=34088947
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP04738705A Expired - Lifetime EP1651861B1 (de) | 2003-07-30 | 2004-06-17 | Schaltventil mit druckausgleich für einen kraftstoffinjektor mit druckverstärker |
Country Status (5)
Country | Link |
---|---|
US (1) | US7316361B2 (de) |
EP (1) | EP1651861B1 (de) |
JP (1) | JP4113223B2 (de) |
DE (2) | DE10334771A1 (de) |
WO (1) | WO2005015000A1 (de) |
Families Citing this family (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102004061800A1 (de) * | 2004-12-22 | 2006-07-06 | Robert Bosch Gmbh | Injektor eines Kraftstoffeinspritzsystems einer Brennkraftmaschine |
US8100110B2 (en) * | 2005-12-22 | 2012-01-24 | Caterpillar Inc. | Fuel injector with selectable intensification |
JP4415962B2 (ja) * | 2006-03-17 | 2010-02-17 | 株式会社デンソー | インジェクタ |
DE102007009167A1 (de) * | 2007-02-26 | 2008-08-28 | Robert Bosch Gmbh | Mehrwegeventil |
JP4245639B2 (ja) * | 2007-04-13 | 2009-03-25 | トヨタ自動車株式会社 | 内燃機関の燃料噴射弁 |
DE102007018040A1 (de) | 2007-04-13 | 2008-10-16 | Robert Bosch Gmbh | Kraftstoffinjektor mit integriertem Druckverstärker |
JP4734351B2 (ja) * | 2008-01-28 | 2011-07-27 | 日立オートモティブシステムズ株式会社 | 燃料噴射弁及び内燃機関 |
US7980224B2 (en) * | 2008-02-05 | 2011-07-19 | Caterpillar Inc. | Two wire intensified common rail fuel system |
US7832374B2 (en) * | 2008-10-21 | 2010-11-16 | Gm Global Technology Operations, Inc. | Fuel pressure amplifier |
DE102011000872A1 (de) | 2011-02-22 | 2012-08-23 | Jochen Mertens | Verfahren zur Einspritzung eines Kraftstoffs sowie zugehörige Vorrichtung |
KR101349647B1 (ko) * | 2012-02-17 | 2014-01-16 | 자동차부품연구원 | 직접분사식 디젤엔진용 인젝터 |
US8775054B2 (en) | 2012-05-04 | 2014-07-08 | GM Global Technology Operations LLC | Cold start engine control systems and methods |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2041170B (en) * | 1979-01-25 | 1983-02-16 | Lucas Industries Ltd | Flow control valve |
US5163479A (en) * | 1991-01-11 | 1992-11-17 | The Boc Group, Inc. | Pressure equalizing system and valve |
US6029632A (en) * | 1998-07-21 | 2000-02-29 | Daimlerchrysler Ag | Fuel injector with magnetic valve control for a multicylinder internal combustion engine with direct fuel injection |
DE19951554A1 (de) * | 1999-10-26 | 2001-05-10 | Bosch Gmbh Robert | Kraftstoffinjektor mit integrierter Durchflussbegrenzung |
WO2001053696A2 (de) * | 2000-01-20 | 2001-07-26 | Robert Bosch Gmbh | Einspritzeinrichtung und verfahren zum einspritzen von fluid |
DE10008268A1 (de) | 2000-01-20 | 2001-08-02 | Bosch Gmbh Robert | Einspritzeinrichtung und Verfahren zum Einspritzen von Fluid |
DE10031580A1 (de) * | 2000-06-29 | 2002-01-17 | Bosch Gmbh Robert | Druckgesteuertes Steuerteil für Common-Rail-Injektoren |
DE10031574B4 (de) * | 2000-06-29 | 2008-12-04 | Robert Bosch Gmbh | Druckgesteuerter doppelschaltender Hochdruckinjektor |
DE10218635A1 (de) * | 2001-05-17 | 2002-11-28 | Bosch Gmbh Robert | Kraftstoffeinspritzeinrichtung |
US6805101B2 (en) * | 2001-05-17 | 2004-10-19 | Robert Bosch Gmbh | Fuel injection device |
-
2003
- 2003-07-30 DE DE10334771A patent/DE10334771A1/de not_active Withdrawn
-
2004
- 2004-06-17 WO PCT/DE2004/001254 patent/WO2005015000A1/de active Application Filing
- 2004-06-17 US US10/566,245 patent/US7316361B2/en not_active Expired - Fee Related
- 2004-06-17 EP EP04738705A patent/EP1651861B1/de not_active Expired - Lifetime
- 2004-06-17 DE DE502004011616T patent/DE502004011616D1/de not_active Expired - Lifetime
- 2004-06-17 JP JP2005518186A patent/JP4113223B2/ja not_active Expired - Fee Related
Non-Patent Citations (1)
Title |
---|
See references of WO2005015000A1 * |
Also Published As
Publication number | Publication date |
---|---|
US7316361B2 (en) | 2008-01-08 |
DE502004011616D1 (de) | 2010-10-14 |
DE10334771A1 (de) | 2005-02-24 |
EP1651861B1 (de) | 2010-09-01 |
WO2005015000A1 (de) | 2005-02-17 |
JP2006514217A (ja) | 2006-04-27 |
US20060202139A1 (en) | 2006-09-14 |
JP4113223B2 (ja) | 2008-07-09 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP1520096B1 (de) | Speichereinspritzsystem mit variodüse und druckübersetzungseinrichtung | |
EP1593839B1 (de) | Kraftstoffinjektor für Verbrennungskraftmaschinen mit mehrstufigem Steuerventil | |
EP1613856B1 (de) | Servoventilangesteuerter kraftstoffinjektor mit druckübersetzer | |
EP1654455B1 (de) | Steuerventil für einen einen drucküberbesetzer enthaltenden kraftstoffinjektor | |
DE10315015B4 (de) | Kraftstoffinjektor mit Druckverstärker und Servoventil mit optimierter Steuermenge | |
EP1613855B1 (de) | Kraftstoffinjektor mit leckagefreiem servoventil | |
WO2002084106A1 (de) | Ventil zum steuern von flüssigkeiten | |
EP1651862B1 (de) | Schaltventil für einen kraftstoffinjektor mit druckübersetzer | |
EP1651861B1 (de) | Schaltventil mit druckausgleich für einen kraftstoffinjektor mit druckverstärker | |
WO2008061844A1 (de) | Kraftstoffinjektor | |
DE10033428C2 (de) | Druckgesteuerter Injektor zum Einspritzen von Kraftstoff | |
EP1925812B1 (de) | Kraftstoffeinspritzventil für Brennkraftmaschinen | |
EP1558843A1 (de) | Kraftstoff-einspritzeinrichtung für brennkraftmaschinen | |
EP1682769B1 (de) | Kraftstoffinjektor mit mehrteiligem, direktgesteuertem einspritzventilglied | |
DE102005032464A1 (de) | Kraftstoffinjektor mit Vorsteuerraum | |
EP1939441A2 (de) | Kraftstoffinjektor | |
DE102008042227A1 (de) | Kraftstoff-Injektor | |
EP1392965B1 (de) | Druckverstärker einer kraftstoffeinspritzeinrichtung | |
DE10141221A1 (de) | Druck-Hub-gesteuerter Injektor für Kraftstoffeinspritzsysteme | |
DE10325620A1 (de) | Servoventilangesteuerter Kraftstoffinjektor mit Druckübersetzer | |
DE102007009167A1 (de) | Mehrwegeventil | |
DE10315489B3 (de) | Kraftstoffinjektor mit Druckübersetzer und in ein Düsenmodul integriertem Dämpfungskolben | |
DE10066102B4 (de) | Steuerventil für einen Einspritzinjektor | |
DE102007001365A1 (de) | Injektor mit Steuer- und Schaltkammer | |
DE102008044043A1 (de) | Kraftstoffinjektor |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
17P | Request for examination filed |
Effective date: 20060228 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): DE FR GB |
|
17Q | First examination report despatched |
Effective date: 20060721 |
|
DAX | Request for extension of the european patent (deleted) | ||
RBV | Designated contracting states (corrected) |
Designated state(s): DE FR GB |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
RIC1 | Information provided on ipc code assigned before grant |
Ipc: F02M 63/00 20060101ALI20100315BHEP Ipc: F02M 57/02 20060101AFI20100315BHEP Ipc: F02M 59/36 20060101ALI20100315BHEP |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): DE FR GB |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D Free format text: NOT ENGLISH |
|
REF | Corresponds to: |
Ref document number: 502004011616 Country of ref document: DE Date of ref document: 20101014 Kind code of ref document: P |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
26N | No opposition filed |
Effective date: 20110606 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 502004011616 Country of ref document: DE Effective date: 20110606 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 13 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: GB Payment date: 20160628 Year of fee payment: 13 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20160621 Year of fee payment: 13 |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20170617 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST Effective date: 20180228 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170617 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170630 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20220822 Year of fee payment: 19 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R119 Ref document number: 502004011616 Country of ref document: DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20240103 |