CN101548092B - Fuel injector having a solenoid valve with a spherical seat - Google Patents

Fuel injector having a solenoid valve with a spherical seat Download PDF

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Publication number
CN101548092B
CN101548092B CN200780044908.0A CN200780044908A CN101548092B CN 101548092 B CN101548092 B CN 101548092B CN 200780044908 A CN200780044908 A CN 200780044908A CN 101548092 B CN101548092 B CN 101548092B
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CN
China
Prior art keywords
valve
pressure
fuel injector
valve element
valve member
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Expired - Fee Related
Application number
CN200780044908.0A
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Chinese (zh)
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CN101548092A (en
Inventor
N·艾森门格尔
H-C·马盖尔
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of CN101548092A publication Critical patent/CN101548092A/en
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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
    • 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
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • 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"
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member
    • F02M63/008—Hollow valve members, e.g. members internally guided
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/28—Details of throttles in fuel-injection apparatus
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • 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

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  • 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

Fuel injector with solenoid valve of band spheric seat
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 through 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 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 through 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 little spring force by pressure balanced solenoid valve, therefore to open in order causing, need little electromagnetism ferreous, Valve travel is little and allow 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 preferable configuration becomes the injection valve member closure of needle-like, 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 sees that these wearing and tearing are not remarkable to the influence of the function of the solenoid valve of such formation with causing wearing and tearing.
Summary of the invention
In scheme according to the present invention, propose one by pressure balanced solenoid valve, the valve element that wherein preferably is configured to needle-like has a valve seat that is made up 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 through the hemisphere configuration of end towards the seat of valve element of valve element.The end of the 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 preferable configuration valve element that becomes 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.
Further improvement can reach through the spheric seat that proposes according to the present invention and one acting little pressure stage on closing direction.Close power through producing the hydraulic pressure that acts on the valve element in acting pressure stage 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 when spring, occurs.Damping characteristic during closed electromagnetic valve is improved through the pressure stage that acts on the closing direction; Because in preferable configuration becomes the closed condition of valve element of needle-like, set up the power of closing of a hydraulic pressure, this is closed mechanical resistance and ends opening again of valve element that preferable configuration becomes 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; Make preferable configuration become the speed of the valve element motion of needle-like advantageously to be optimized thus on the one hand, the spring characteristic of the mechanical part aspect that causes thus and spring load are advantageously optimized.If the injection valve member that preferable configuration becomes needle-like constitutes one with the armature that electromagnetic coil by solenoid valve attracts; Then can reach a little moving-mass; Under the situation of damping characteristic optimization, can realize the at interval short of each course of injection, 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 with particularly advantageous mode, in this valve member, is provided with a control room, servocontrol chamber especially, and this valve member has sealed an inner pressure chamber of injector body 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 come at length to 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 through one SysPressure reservoir 12 load and be in the fuel under the high pressure.System pressure p in the pressure reservoir 12 SysThrough unshowned in the drawings high-pressure delivery device, for example high-pressure service pump produces and arrive fuel injectors 10 by pressure reservoir 12 through pressure duct 14.Pressure duct 14 leads to apply in the case of sprayer 16 and to the pressure chamber that representes 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 through 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 26 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, in this pressure chamber, feeds the pressure duct 14 from pressure reservoir 12.
In valve member 32, be configured with control room 36, this control room is through 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 through 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.
Through import the system pressure p that throttle valve 38 forms in control room 36 SysBe applied on the end face 44 of injection valve member 42 that preferable configuration becomes needle-like.Injection valve member 42 comprises a supporting disk 46, is supporting closing spring 48 above that.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 through case of sprayer 16 in the pressure chamber 34 that loads.Be in system pressure p SysUnder fuel flow to the nozzle box that representes with label 50 through this doughnut 52, this nozzle box is configured in the nozzle body 18.Be in system pressure p SysUnder fuel from doughnut 52 through at least one 56 arrival nozzle box 50, throttling position, this throttling position for example can be configured to a grinding structure on the circumference of injection valve member 42 that preferable configuration becomes needle-like.
Injection valve member 42 comprises a pressure stage 54 in by nozzle box's 50 area surrounded at it in ejectisome 18.
Be in system pressure p SysUnder fuel by nozzle box 50 flow to through the annular space preferable configuration become needle-like injection valve member 42 the seat 58.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 being seated in injection valve member 42 sealings that preferable configuration in its valve seat 58 becomes needle-like.
Become in preferable configuration on the circumference of injection valve member 42 of needle-like and have the throttling position 56 that at least one preferable configuration becomes the grinding structure.Make through 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 becomes the valve element 62 of needle-like to constitute the border of pressure equalizing chamber 78 with preferable configuration.Be connected with valve chamber 84 through through-flow attachment portion 74 press-on pins 66 and 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 the conical surface in the valve member 32 82 and limited 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.Valve element 62 through becoming needle-like in preferable configuration 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 through 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 the diameter of the spheric seat that guiding diameter 68 is substantially equal to be made up 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 through spherical 86 have realized a spheric seat, do not install from the reverse side in seat zone because press-on pins 66 can rely on valve seat 80 ground.Can see through-flow attachment portion through 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, guide preferable configuration to become on the press-on pins 66 of valve element 62 of needle-like above that and be created in acting pressure stage on the closing direction.Should become the increasing of the diameter of the spheric seat that the guiding diameter 68 through being received in the press-on pins 66 in actuator's housing 20 loosely of acting pressure stage on the closing direction of valve element 62 of needle-like provides by spherical 86 relatively to realize in preferable configuration.Close power through 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 through guiding diameter 68 through pressure stage-this pressure stage that acts on the closing direction relatively obtains-is improved; Because in the closed condition of spheric seat, set up the power of closing of hydraulic pressure, this is closed mechanical resistance and ends opening again of valve element 62 that preferable configuration becomes 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 through form the pressure equalizing chamber that is connected or dampening chamber 78 via through-flow attachment portion 74 and valve chamber 84.If preferable configuration becomes the injection valve member 62 of needle-like and armature card 64 to be designed to parts; The little quality that will move then appears; This causes the damping characteristic optimized through being arranged on damping throttle valve in the through-flow attachment portion 74, is carrying out allowing interval very in short-term when in short-term each fuel in succession sprays through spray-hole 30 thus.
The spheric seat of realizing through 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 the pressure chamber opened in 34 minutes.Valve member 32 through stop sleeve 30, be supported on magnetic core 26 and housing lid 24-on this stop sleeve and put hermetically by this housing lid sealing housing 20-of actuator and lean against on the injector body 16.
The preferable configuration that when solenoid valve 22 energisings, realizes becomes the motion of opening that makes progress of the valve element 62 of needle-like to cause the discharge degree in control room 36.The controlled quentity controlled variable that when the spheric seat that is provided by spherical 86 is opened, flows out in by control room 36 flows in actuator's housing 20 and the backflow part 72 through 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, be configured in the end face 44 immigration control rooms 36 of injection valve member 42 of needle-like.The valve seat of opening 58 through 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.
Preferable configuration becomes the opening characteristic of the injection valve member 42 of needle-like to become the throttling position 56 of grinding structure to optimize through at least one preferable configuration that is configured on its circumference.This at least one to be configured in throttling position 56 on the circumference of injection valve member 42 that preferable configuration becomes 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.
Saidly 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 (8)

1. be used for injecting fuel into the fuel injector (10) of a combustion chambers of internal combustion engines, wherein, an injection valve member (42) is operated through 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) through 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); And said valve element (62) has a through-flow attachment portion (74) between pressure equalizing chamber or dampening chamber (78) and said valve seat (80), and wherein, this valve element (62) is directed on a press-on pins that is supported loosely (66) at actuator's housing that is arranged in inside.
2. according to the fuel injector (10) of claim 1, it is characterized in that: on said valve element (62), constructed this spherical (86), the conical surface (82) in this spherical and the said valve member (32) constitutes said valve seat (80).
3. according to the fuel injector (10) of claim 1, it is characterized in that: said spherical (86) is configured in the said valve member (32), and said valve element (62) has a conical surface (82), and said spherical (86) constitutes said valve seat (80) with this conical surface.
4. according to the fuel injector (10) of claim 1, it is characterized in that: said valve element (62) is directed on this press-on pins (66) and constitutes the border of this pressure equalizing chamber (78) with this press-on pins.
5. according to the fuel injector (10) of claim 1, it is characterized in that: in said through-flow attachment portion (74), constructed a throttling position (76).
6. according to the fuel injector (10) of claim 1, it is characterized in that: the guiding diameter (68) of this press-on pins (66) equals the internal diameter of said valve element (62).
7. according to the fuel injector (10) of claim 1, it is characterized in that: the guiding diameter (68) of this press-on pins (66) makes to form an acting pressure stage of closing direction along said valve element (62) greater than the diameter of said valve seat (80).
8. according to the fuel injector (10) of claim 1; It is characterized in that: said valve seat (80) is configured on the said valve member (32), and this valve member constitutes the pressure chamber (34) in the border in said control room (36) and the injector body (16) that said fuel injector (10) is sealed in a relative area of low pressure.
CN200780044908.0A 2006-12-04 2007-10-12 Fuel injector having a solenoid valve with a spherical seat Expired - Fee Related CN101548092B (en)

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 CN101548092A (en) 2009-09-30
CN101548092B true CN101548092B (en) 2012-12-19

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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)

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DE102007011685A1 (en) * 2007-03-09 2008-09-11 Robert Bosch Gmbh Fuel injector with improved control valve
DE102007035698A1 (en) * 2007-07-30 2009-02-05 Robert Bosch Gmbh Fuel injection valve with improved tightness at the sealing seat of a pressure-balanced 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
DE102009060029A1 (en) * 2009-12-21 2011-06-22 Robert Bosch GmbH, 70469 Electromagnetically switchable valve for installation in a built-in block
CN102213165B (en) * 2010-04-08 2013-02-13 北京亚新科天纬油泵油嘴股份有限公司 High pressure common rail electronic control fuel injector
DE102013206383A1 (en) * 2013-04-11 2014-10-16 Robert Bosch Gmbh Fuel injection valve for internal combustion engines
DE102018109206A1 (en) * 2018-04-18 2019-10-24 Liebherr-Components Deggendorf Gmbh Injector for injecting fuel

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DE102006057025A1 (en) 2008-06-05
CN101548092A (en) 2009-09-30
WO2008068093A1 (en) 2008-06-12
DE502007006059D1 (en) 2011-02-03
EP2100026A1 (en) 2009-09-16
ATE492719T1 (en) 2011-01-15

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