CN101548092A - Fuel injector having a solenoid valve with a spherical seat - Google Patents
Fuel injector having a solenoid valve with a spherical seat Download PDFInfo
- Publication number
- CN101548092A CN101548092A CNA2007800449080A CN200780044908A CN101548092A CN 101548092 A CN101548092 A CN 101548092A CN A2007800449080 A CNA2007800449080 A CN A2007800449080A CN 200780044908 A CN200780044908 A CN 200780044908A CN 101548092 A CN101548092 A CN 101548092A
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- China
- Prior art keywords
- valve
- pressure
- fuel injector
- valve element
- valve member
- Prior art date
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Classifications
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- 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
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- 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
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- 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
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- 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
- F02M63/0071—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059 characterised by guiding or centering means in valves including the absence of any guiding means, e.g. "flying arrangements"
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/0012—Valves
- F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
- F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member
- F02M63/008—Hollow valve members, e.g. members internally guided
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- 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
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- 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
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- 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
- F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
- F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Fuel-Injection Apparatus (AREA)
- Magnetically Actuated Valves (AREA)
Abstract
The invention relates to a fuel injector (10) for injecting fuel into a combustion chamber of an internal combustion engine. An injection valve element (42) is actuated via pressure relief of a control space (36). Said control space (36) is loaded by a system pressure Rhosys. The control space (36) is relieved of pressure via a solenoid valve (22) of pressure-equalized configuration, the valve element (62) of which opens or closes a valve seat (80). The valve seat (80) comprises a spherical surface (86).
Description
Background technique
By EP-A 1 612 403 known a kind of sparger that is used for injecting fuel into the firing chamber of internal-combustion engine, wherein, injection valve member is controlled by the control valve of Electromagnetic Drive.Can close or discharge by the discharge throttle valve of control room by this control valve to fuel backflow part.The control room is limited by control piston on a side, and by this control piston control injection valve member, this injection valve member is discharged at least one spray-hole in the firing chamber of internal-combustion engine.Discharge throttle valve and be received in the parts, these parts are provided with the valve seat that narrows down carrying on the side in control room.A closure member can move in this valve seat, and this closure member is connected with the armature of solenoid valve.Structure has an edge on closure member for this reason, and this edge can move relative to the seat of conical configuration.Closure member can move on an axial stem, and this axial stem has the parts of discharging throttle valve to be connected integratedly with structure wherein.For make valve to liquid seal close, essential make high-precision surface and the high-precision cooperation on axial stem of design closing element, with the swing of avoiding closing element and the inclination that can cause thus-will make like this valve seat closure fully.
Go up the sparger that employed fuel injector for example can use Stroke Control for for example high pressure accumulator ejecting system (rail altogether), this sparger drives to control the pressure in the control room by a solenoid valve.The injection valve member that preferably is configured to needle-like is for example controlled by a servocontrol chamber.Solenoid valve is not pressure balanced usually and therefore needs high spring force, high electro-magnet switch power to reach the macrostructure space based on the size of spring and electromagnet.The shortcoming of this solenoid valve is to exist very big restriction aspect the order of multiple injection, so that can not realize very short in succession injection interval.
Usually to be needed much smaller spring force by pressure balanced solenoid valve, therefore to open in order causing, need little electromagnetism ferreous, little the reaching of Valve travel allows switching time faster thus.Structural type by this solenoid valve can be improved the multiple injection ability.Yet the valve of this pressure balance configuration needs the guiding of high pressure sealing and the sealing the margin of linear extension, and the diameter at sealing edge equals the guiding diameter of valve element, and this just allows the pressure balance of solenoid valve.
But crucially on by pressure balanced solenoid valve be such situation, that is along with the passing of operating time, wearing and tearing will appear on sealing the margin,, because when the injection valve member that is preferably configured as needle-like is closed, the mechanical load at the seat edge of linear extension is very big.This wearing and tearing have been supported in the pollution that directly reaches the very strong degree on the edge.This operating time from solenoid valve will cause wearing and tearing, and these wearing and tearing are not remarkable to the influence of the function of the solenoid valve of such formation.
Summary of the invention
Propose one by pressure balanced solenoid valve in according to the solution of the present invention, the valve element that wherein preferably is configured to needle-like has a valve seat that is made of the spheric seat of the anti-mechanical wear that produces because of spillage of material or distortion.As the valve seat of the solenoid valve that proposes according to the present invention with spheric seat on the sealing station of valve, promptly be configured to spheric seat on the seat at the valve element.This spheric seat for example can embody by the hemisphere configuration of end towards the seat of valve element of valve element.The end of for example hemisphere configuration of valve element can with funnel shape in valve member ground structure, for example be configured to bore the seat mating reaction of seat.Can be in addition, the conical surface be to be configured in the valve member yet, but this conical surface is configured on the end of valve element and the seat structure with the valve element cooperatively interacts that is configured on the valve member becomes hemisphere.These two kinds of configurations all can be realized spheric seat.
Preferably, this valve element that is configured to needle-like is arranged in the inner press-on pins that is bearing in actuator's housing loosely by one and leads, and can realize pressure balance thus.
If solenoid valve is provided with spheric seat, then can be for example with following the tracks of the compensation valve element that is preferably configured as needle-like and pedestal-promptly for example valve member-between parallelism error, consequently can realize the valve arrangement flexible program of favourable multi-part type like this.
A further improvement can reach by spheric seat and little pressure stage that works on closing direction that proposes according to the present invention.Close power by producing the hydraulic pressure that acts on the valve element in the pressure stage that works on the closing direction, can reduce the spring when valve is closed thus, this is again to playing occurring wear favourable effect, because the peak load of machinery occurs when spring.Damping characteristic during closed electromagnetic valve is improved by the pressure stage that acts on the closing direction, because set up the power of closing of a hydraulic pressure in the closed condition of the valve element that is preferably configured as needle-like, this closes the opening again of valve element that mechanical resistance only is preferably configured as needle-like.The multiple injection ability that this allows best valve harmony on the one hand and has improved the fuel injector of being operated by the solenoid valve with spheric seat that proposes according to the present invention on the other hand.
In addition a dampening chamber can be set in the high-pressure area of fuel injector, the speed of the valve element motion that is preferably configured as needle-like is advantageously optimized, the spring characteristic of the mechanical part aspect that causes thus and spring load are advantageously optimized.If the injection valve member that is preferably configured as needle-like constitutes one with the armature that electromagnetic coil by solenoid valve attracts, then can reach a little moving-mass, can realize the at interval short of each course of injection under the situation of damping characteristic optimization, this will advantageously influence the multiple injection ability.
Propose according to the present invention have a spheric seat can be used for controlling ejecting system by pressure balanced solenoid valve, especially in an advantageous manner as the control valve of fuel injector servo-controlled, that operate by solenoid valve.
Spheric seat can directly be configured in the valve member in particularly advantageous mode, is provided with a control room in this valve member, servocontrol chamber especially, and this valve member has sealed a pressure chamber of the injector body inside of fuel injector.This just allows to be particularly useful for favourable structure on the not only simple but also cost of fuel injector of high pressure accumulator ejecting system (rail altogether).
Description of drawings
Below will explain the present invention by accompanying drawing.Unique accompanying drawing is represented a cross section of the Fuelinjection nozzle of proposition according to the present invention, and this Fuelinjection nozzle is operated by a solenoid valve that comprises a spheric seat.
Embodiment
Can find out that by accompanying drawing fuel injector 12 wherein has system pressure p by one
Sys Pressure reservoir 12 load the fuel that is under the high pressure.System pressure p in the pressure reservoir 12
SysBy unshowned in the drawings high-pressure delivery device, for example high-pressure service pump produces and arrive fuel injectors 10 by pressure reservoir 12 by pressure duct 14.Pressure duct 14 leads to apply in the case of sprayer 16 and to the pressure chamber that represents with label 34 and is in system pressure p
SysUnder system pressure.
According to this figure, fuel injector 10 also comprises a nozzle body that only draws 18 and actuator's housing 20 here except that case of sprayer 16, in this actuator's housing the actuator that is configured to solenoid valve 22 has been installed.Actuator's housing 20 seals by housing lid 24.Housing lid 24 is provided with outside thread and can be threaded in the internal thread that correspondingly constitutes of actuator's housing 20 in the figure.Magnetic core 26, electromagnetic coil 28, the stop sleeve 30 that supports magnetic core 6 and the part of valve member 32 have been received by this magnetic core encirclement in the inside of actuator's housing 20.The valve member 32 that partly is received in actuator's housing 20 limits the described pressure chamber 34 of beginning part, feeds the pressure duct 14 from pressure reservoir 12 in this pressure chamber.
Be configured with control room 36 in valve member 32, this control room is by importing throttle valve 38 by being in system pressure p
SysUnder pressure chamber 34 inject fuel.Control room 36-is configured to servocontrol chamber-can be depressurized by discharging throttle valve 40 in the drawings.Discharge throttle valve 40 also is configured in the valve member 32 and feeds in the valve chamber of representing with label 84.
By import the system pressure p that throttle valve 38 forms in control room 36
SysBe applied on the end face 44 of the injection valve member 42 that is preferably configured as needle-like.Injection valve member 42 comprises a supporting disk 46, is supporting closing spring 48 thereon.The end portion supports that is positioned at supporting disk 46 opposites of closing spring 48 is on valve member 32.
From by system pressure p
SysA doughnut 52 extends by case of sprayer 16 in the pressure chamber 34 that loads.Be in system pressure p
SysUnder fuel flow to the nozzle box that represents with label 50 by this doughnut 52, this nozzle box is configured in the nozzle body 18.Be in system pressure p
SysUnder fuel arrive nozzle boxs 50 by at least one throttling position 56 from doughnut 52, this throttling position for example can be configured to be preferably configured as a grinding structure on the circumference of injection valve member 42 of needle-like.
Be in system pressure p
SysUnder fuel flow to the seat 58 of the injection valve member 42 that is preferably configured as needle-like through the annular space by nozzle box 50.In the view according to this figure, the spray-hole 60 on the end of the combustion chamber side of fuel injector 10 is by the injection valve member that is preferably configured as needle-like 42 sealings that are seated in its valve seat 58.
On the circumference of the injection valve member 42 that is preferably configured as needle-like, has the throttling position 56 that at least one is preferably configured as the grinding structure.Make by this at least one throttling position 56 and to be in system pressure p
SysUnder doughnut 52 be connected to each other on hydraulic pressure with nozzle box 50.
The solenoid valve 22 that is installed in actuator's housing 20 comprises valve spring 70, and this valve spring surrounds press-on pins 66.Valve spring 70 is supported on the downside of housing lid 24.Preferred pressure pin 66 is received in actuator's housing 20 loosely.The upper-end surface that 70 pairs of valve springs are configured to the valve element 62 of needle loads.Structure has armature card 64 on this valve element, and this armature card is arranged on the opposite of the electromagnetic coil 28 of solenoid valve 22.Press-on pins 66 is configured with a diameter, and this diameter is the guiding diameter 68 of valve element 62.The lower end surface of press-on pins 66 has constituted the border of pressure equalizing chamber 78 with the valve element 62 that is preferably configured as needle-like.Be connected with valve chamber 84 by through-flow attachment portion 74 by press-on pins 66 and by the pressure equalizing chamber 78 that valve element 62 limits.According to the form of implementation of the fuel injector proposed by the invention 10 shown in the accompanying drawings, this valve chamber 84 is on the one hand by the conical surface in the valve member 32 82 and limited by the spherical on the underpart of valve element 62 86 on the other hand.In form of implementation shown in the drawings, done on valve element 62 as the spherical 86 of spheric seat.By the valve element 62 that is preferably configured as needle-like on the end of valve member 32, can accomplish in an advantageous manner to valve element 62 and as the compensation of the parallelism error between the valve member 32 of pedestal as the spherical 86 of spheric seat.Can realize the valve arrangement of favourable multi-part type in addition by the structure that proposes according to the present invention.
With shown in the accompanying drawing by being configured in the spherical 86 on the valve element 62 and being located at spheric seat that the conical surface 82 in the valve member 32 constitutes on the contrary, the conical surface 82 also can be configured on the valve element 62 and spherical 86 also can be configured on the valve member 32.Can be still on valve member 32, all to realize spherical geometrical construction on the valve element 62 in addition.
Because guiding diameter 68 is substantially equal to the diameter of the spheric seat that is made of spherical 86, this plays the pressure balanced effect of solenoid valve 22.In propose the valve arrangement form according to the present invention, structure and the conical surface 82 mating reactions by spherical 86 have realized a spheric seat, and 80 ground are installed from the reverse side in seat zone because press-on pins 66 can not rely on valve seat.Can see through-flow attachment portion by label 74, it makes pressure equalizing chamber or dampening chamber 78 be connected with valve chamber 84.
A form of implementation of fuel injector shown in the figure obtains like this, that is, guiding thereon is preferably configured as on the press-on pins 66 of valve element 62 of needle-like and is created in the pressure stage that works on the closing direction.The increasing of the diameter of the spheric seat that the guiding diameter 68 of pressure stage that should work on the closing direction of the valve element 62 that is preferably configured as needle-like by being received in the press-on pins 66 in actuator's housing 20 loosely provided by spherical 86 relatively realizes.Close power by this valve that acts on the pressure stage generation hydraulic pressure on the closing direction, when valve element 62 is closed, reduced the spring of solenoid valve thus.The increasing of the diameter of the spheric seat that the damping characteristic when valve element 62 is closed can be provided by spherical 86 by guiding diameter 68 relatively by pressure stage-this pressure stage that acts on the closing direction obtains-is improved, because set up the power of closing of hydraulic pressure in the closed condition of spheric seat, this closes the reopening of valve element 62 that mechanical resistance only is preferably configured as needle-like.This allows the optimization of valve harmony again and the multiple injection ability of the fuel injector that proposes according to the present invention.
Can make the speed-optimization that valve element 62 opens and improve the spring characteristic by form the pressure equalizing chamber that is connected or dampening chamber 78 via through-flow attachment portion 74 and valve chamber 84.Be designed to parts if be preferably configured as the injection valve member 62 and the armature card 64 of needle-like, the little quality that will move then appears, this causes the damping characteristic optimized by being arranged on damping throttle valve in the through-flow attachment portion 74, thus at the interval of being undertaken by spray-hole 30 allowing when in short-term each fuel in succession sprays very in short-term.
The spheric seat of realizing by spherical 86 directly is configured on the valve member 32 in an advantageous manner, this valve member constituted as the border in the control room 36 of servocontrol chamber and with case of sprayer 16 in be in system pressure p
SysUnder pressure chamber 34 separately.Valve member 32 by stop sleeve 30, be supported on magnetic core 26 on this stop sleeve and housing lid 24-and put hermetically by this housing lid sealing housing 20-of actuator and lean against on the injector body 16.
The motion of opening that makes progress of the valve element of realizing when solenoid valve 22 energisings 62 that is preferably configured as needle-like causes the discharge degree in control room 36.The controlled quentity controlled variable that flows out in by control room 36 when the spheric seat that is provided by spherical 86 is opened flows in actuator's housing 20 and the backflow part 72 by low voltage side is discharged in the area of low pressure of fuel injection system.According to the control room that is preferably used as the servocontrol chamber 36 discharge degree of the fuel injector 10 of the form of implementation shown in the figure time, the end face 44 that is configured to the injection valve member 42 of needle-like moves in the control rooms 36.The valve seat of opening 58 by injection valve member 42 makes and is in system pressure p thus
SysUnder fuel flow in the firing chamber of internal-combustion engines through the opening 60 that at least one is configured on the end of combustion chamber side of fuel injector 10.
The opening characteristic that is preferably configured as the injection valve member 42 of needle-like can be optimized by being configured in the throttling position 56 that on its circumference at least one be preferably configured as the grinding structure.This at least one to be configured in throttling position 56 on the circumference of the injection valve member 42 that is preferably configured as needle-like be to be in system pressure p in the injector body 16
SysUnder doughnut 52 and the nozzle body 18 that is configured in fuel injector 10 in the hydraulic pressure attachment portion of nozzle box 50.
Describedly preferably be used in the ejecting system that is used for burner oil by pressure balanced solenoid valve 22, especially in an advantageous manner as the control valve of controlling fuel injector by solenoid valve 22 servoly, this fuel injector can use in high pressure accumulator ejecting system (rail altogether).
Claims (9)
1. be used for injecting fuel into the sparger (10) of a combustion in IC engine device, wherein, an injection valve member (42) is operated by the discharge degree of a control room (36), and this control room has been loaded a system pressure p
SysThe discharge degree in this control room (36) is realized by pressure balanced solenoid valve (22) by one, the valve element (62) of this solenoid valve opens or closes a valve seat (80), it is characterized in that: this a valve element (62) or a valve member (32) have a spherical (86).
2. according to the fuel injector (10) of claim 1, it is characterized in that: constructed the face (86) of a sphere on described valve element (62), the conical surface (82) in this face and the valve member (32) constitutes a valve seat (80).
3. according to the fuel injector (10) of claim 1, it is characterized in that: the face of described sphere (86) is configured in the described valve member (32), and the valve element (62) that this valve member and has a conical surface (82) constitutes described valve seat (80).
4. according to the fuel injector (10) of claim 1, it is characterized in that: described valve element (62) is directed on a press-on pins (66) and constitutes the border of a pressure equalizing chamber (78) with this press-on pins.
5. according to the fuel injector (10) of claim 4, it is characterized in that: described valve element (62) has a through-flow attachment portion (74) between described pressure equalizing chamber or dampening chamber (78) and described valve seat (80).
6. according to the fuel injector (10) of claim 5, it is characterized in that: in described through-flow attachment portion (74), constructed a throttling position (76).
7. according to the fuel injector (10) of claim 1, it is characterized in that: described valve element (62) is directed on a press-on pins (66), and the guiding diameter (68) of this press-on pins equals the internal diameter of described valve element (62).
8. according to the fuel injector (10) of claim 1, it is characterized in that: described valve element (62) is directed on a press-on pins (66), the guiding diameter (68) of this press-on pins is greater than the diameter of described valve seat (80), makes to form a pressure stage that works along the closing direction of described valve element (62).
9. according to the fuel injector (10) of claim 1, it is characterized in that: described valve seat (80) is configured on the valve member (32), and this valve member constitutes the border in described control room (36) and a relative area of low pressure and seals a pressure chamber (34) in the described injector body (16).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102006057025.1 | 2006-12-04 | ||
| DE102006057025A DE102006057025A1 (en) | 2006-12-04 | 2006-12-04 | Fuel injector for injecting fuel into combustion chamber of internal combustion engine, has pressure-compensating magnetic valve with valve element that opens or locks valve seat, where valve element or piece of valve has spherical surface |
| PCT/EP2007/060869 WO2008068093A1 (en) | 2006-12-04 | 2007-10-12 | Fuel injector having a solenoid valve with a spherical seat |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101548092A true CN101548092A (en) | 2009-09-30 |
| CN101548092B CN101548092B (en) | 2012-12-19 |
Family
ID=39111887
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200780044908.0A Expired - Fee Related CN101548092B (en) | 2006-12-04 | 2007-10-12 | Fuel injector having a solenoid valve with a spherical seat |
Country Status (5)
| Country | Link |
|---|---|
| EP (1) | EP2100026B1 (en) |
| CN (1) | CN101548092B (en) |
| AT (1) | ATE492719T1 (en) |
| DE (2) | DE102006057025A1 (en) |
| WO (1) | WO2008068093A1 (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2011124043A1 (en) * | 2010-04-08 | 2011-10-13 | 北京亚新科天纬油泵油嘴股份有限公司 | High-pressure common rail electric control fuel injector |
| CN102753871A (en) * | 2009-12-21 | 2012-10-24 | 罗伯特·博世有限公司 | Electromagnetically switchable valve for installation in an installation block |
| CN101784785B (en) * | 2007-07-30 | 2013-08-21 | 罗伯特·博世有限公司 | Fuel injection valve with improved tightness on the sealing seat of a pressure-compensated control valve |
| CN105102804A (en) * | 2013-04-11 | 2015-11-25 | 罗伯特·博世有限公司 | Fuel injection valve for internal combustion engines |
| CN112041555A (en) * | 2018-04-18 | 2020-12-04 | 利勃海尔零部件德根多夫有限公司 | Injector for injecting fuel |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102007011685A1 (en) * | 2007-03-09 | 2008-09-11 | Robert Bosch Gmbh | Fuel injector with improved control valve |
| DE102008001600A1 (en) * | 2008-05-06 | 2009-11-12 | Robert Bosch Gmbh | Fuel injector with a pressure valve having a control valve |
| DE102009046563A1 (en) * | 2009-11-10 | 2011-05-12 | Robert Bosch Gmbh | fuel injector |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3555264B2 (en) * | 1995-07-14 | 2004-08-18 | いすゞ自動車株式会社 | Fuel injection device for internal combustion engine |
| DE29807601U1 (en) * | 1998-04-27 | 1998-08-20 | FEV Motorentechnik GmbH & Co. KG, 52078 Aachen | Hydraulic slide valve |
| DE19952511B4 (en) * | 1999-10-30 | 2004-09-30 | Robert Bosch Gmbh | Common rail injector |
| EP1612403B1 (en) * | 2004-06-30 | 2007-01-10 | C.R.F. Società Consortile per Azioni | Servo valve for controlling an internal combustion engine fuel injector |
| AT500889B8 (en) * | 2004-08-06 | 2007-02-15 | Bosch Gmbh Robert | DEVICE FOR INJECTING FUEL IN THE COMBUSTION ENGINE OF AN INTERNAL COMBUSTION ENGINE |
| CN1773098A (en) * | 2005-07-25 | 2006-05-17 | 无锡油泵油嘴研究所 | Co-rail oil injection system electric control oil injector |
| DE102005062549A1 (en) * | 2005-12-27 | 2007-07-05 | Robert Bosch Gmbh | Fuel injector for internal combustion engine has control valve fully integrated into fuel injector, high pressure fuel storage device connected to control chamber and integrated into fuel injector |
| DE102006053128A1 (en) * | 2006-11-10 | 2008-05-15 | Robert Bosch Gmbh | Injector for injecting fuel |
-
2006
- 2006-12-04 DE DE102006057025A patent/DE102006057025A1/en not_active Withdrawn
-
2007
- 2007-10-12 AT AT07821236T patent/ATE492719T1/en active
- 2007-10-12 EP EP07821236A patent/EP2100026B1/en not_active Not-in-force
- 2007-10-12 DE DE502007006059T patent/DE502007006059D1/en active Active
- 2007-10-12 CN CN200780044908.0A patent/CN101548092B/en not_active Expired - Fee Related
- 2007-10-12 WO PCT/EP2007/060869 patent/WO2008068093A1/en active Application Filing
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101784785B (en) * | 2007-07-30 | 2013-08-21 | 罗伯特·博世有限公司 | Fuel injection valve with improved tightness on the sealing seat of a pressure-compensated control valve |
| CN102753871A (en) * | 2009-12-21 | 2012-10-24 | 罗伯特·博世有限公司 | Electromagnetically switchable valve for installation in an installation block |
| CN102753871B (en) * | 2009-12-21 | 2015-11-25 | 罗伯特·博世有限公司 | For be arranged in mounting blocks can electromagnetism switch valve |
| WO2011124043A1 (en) * | 2010-04-08 | 2011-10-13 | 北京亚新科天纬油泵油嘴股份有限公司 | High-pressure common rail electric control fuel injector |
| CN105102804A (en) * | 2013-04-11 | 2015-11-25 | 罗伯特·博世有限公司 | Fuel injection valve for internal combustion engines |
| CN105102804B (en) * | 2013-04-11 | 2018-04-27 | 罗伯特·博世有限公司 | Fuelinjection nozzle for internal combustion engine |
| CN112041555A (en) * | 2018-04-18 | 2020-12-04 | 利勃海尔零部件德根多夫有限公司 | Injector for injecting fuel |
| CN112041555B (en) * | 2018-04-18 | 2022-08-16 | 利勃海尔零部件德根多夫有限公司 | Injector for injecting fuel |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102006057025A1 (en) | 2008-06-05 |
| EP2100026A1 (en) | 2009-09-16 |
| EP2100026B1 (en) | 2010-12-22 |
| DE502007006059D1 (en) | 2011-02-03 |
| WO2008068093A1 (en) | 2008-06-12 |
| ATE492719T1 (en) | 2011-01-15 |
| CN101548092B (en) | 2012-12-19 |
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