CN107667217A - Valve gear and fuel injection system for fuel injection system - Google Patents
Valve gear and fuel injection system for fuel injection system Download PDFInfo
- Publication number
- CN107667217A CN107667217A CN201680034294.7A CN201680034294A CN107667217A CN 107667217 A CN107667217 A CN 107667217A CN 201680034294 A CN201680034294 A CN 201680034294A CN 107667217 A CN107667217 A CN 107667217A
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- Prior art keywords
- valve gear
- valve
- diameter
- high pressure
- fuel injection
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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
- 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
- F02M63/0003—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure
- F02M63/0005—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure using valves actuated by fluid 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
- F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
- F02M63/005—Pressure relief valves
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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
Abstract
The present invention relates to one kind to be used for fuel injection system（22）Valve gear（10）, the valve gear（10）With high pressure charging hole（20）With with valve seat（18）The potted component of interaction（14）For opening and closing the high pressure charging hole（20）, wherein, the high pressure charging hole is being adjacent to valve seat（18）Place has the first diameter（DH1）And away from valve seat（18）Place has Second bobbin diameter（DH2）, the Second bobbin diameter is less than the first diameter（DH1）To form aperture（48）.In addition, the present invention relates to a kind of fuel injection system（22）, the fuel injection system（22）Including the valve gear（10）.
Description
Technical field
The present invention relates to a kind of valve gear for fuel injection system, the valve gear is particularly capable of being used as being used to make combustion
Expect the pressure limiting valve of the high-pressure area release of spraying system.In addition, the present invention relates to a kind of fuel injection system, the fuel injection systems
Valve gear of the system with the type.
Background technology
Fuel injection system is used at least one combustion chamber of fuel injection to internal combustion engine, in the fuel injection system
In, fuel is compressed into high pressure first, to meet requirement of the injection period for prespecified discharge value.
Here, diesel fuel is generally compressed into 1500 bars to 3000 bars of pressure limit, and Fuel Petroleum is compressed
To 200 bars to 350 bars of pressure limit.In order to protect some elements in fuel injection system, for example, sensor or so-called
Common rail, the common rail is positioned at the downstream of high pressure fuel pump as fuel storage region domain for depositing in fuel injection system
Fuel is stored up, valve gear is generally arranged in fuel injection system, and the valve gear is ensured too high pressure from fuel injection system
Middle discharge.The valve gear being designed in the fuel injection system of the pressure limiting valve of the type generally has the unlatching pressure of fixed setting
Power, the valve gear are opened under the Opening pressure, to prevent the restriction element by the high crushing in fuel injection system
It is bad.
Substantial amounts of air is remained in fuel injection system, particularly before internal combustion engine starts for the first time, because
It is not filled up completely with for fuel injection system by fuel also.
As the result that air in fuel injection system be present, it is possible to be designed to the valve gear of pressure limiting valve with mistake
Opened in obvious stroke.The normal travel of potted component is generally between 3 μm and 30 μm.But in the case of an error,
That is in the case of air plankton being present in fuel injection system, stroke of the potted component in valve gear is sized to
1mm is increased to, however, the damage of this element that can result in valve gear.The damage may cause to reveal, and so valve fills
Put and lose its major function.For reduce by the excessive stroke of air impact for, reduce valve gear valve seat it is straight
Footpath is not suitably to select, because its object is to make valve gear in the case of high throughflow（About 100 l/h（L/h）
In the range of）Opening pressure unlike low pass stream in the case of（In the range of about 6 l/h）Opening pressure it is much larger.
Fig. 6 shows currently used known valve gear 10, for example, the valve gear is used as in fuel injection system
Pressure limiting valve 12, Fig. 7 shows characteristic curve, and in the characteristic curve, the Opening pressure of the pressure limiting valve 12 shown in Fig. 6 is set
The through-current capacity of pressure limiting valve 12 is determined by into it.
Valve gear 10 has potted component 14, and the potted component interacts with the valve seat 18 being arranged in valve plate 16, with
Just high pressure charging hole 20 is therefore closed, the high pressure charging hole guides the fluid in valve gear 10.Figure 7 illustrates Opening pressure
Characteristic curve depends on the diameter D of valve seat 18VS.Here, the oblique line in chart 7 represents that the Opening pressure of Fig. 6 valve gear 10 is special
Linearity curve.Colorful zone marker has gone out tolerance pressure scope, and the Opening pressure of valve gear 10 can be located at the tolerance pressure
In the range of power.As it can be seen, Opening pressure increases with the through-flow increase by valve gear 10, but will not be excessive
Ground increase.In present exemplary, the pressure difference of the upper Opening pressure between low pass flow and high pass flow is not more than about 100
Bar.
Therefore aim at and propose a kind of valve gear, the valve gear has flat Opening pressure characteristic curve.It is however, flat
Smooth Opening pressure characteristic curve can only utilize the sufficiently large diameter D of valve seat 18VSTo realize.Therefore disadvantageously：Reduce
The diameter D of valve seat 18VSTo offset the shakiness due to the air plankton in fuel injection system and associated valve gear 10
The qualitative and caused negative effect for valve gear 10.
Because in the diameter D of valve seat 18VSIn the case of reduction, it is big it is through-flow in the case of Opening pressure rapidly uprise.
The content of the invention
Therefore, it is an object of the present invention to propose a kind of valve gear, wherein, although in flat Opening pressure characteristic curve
Under, but the air plankton in the fluid to be guided by the valve gear only has the shadow of very little to the stability of the valve gear
Ring.
The target is realized by the valve gear of the feature with claim 1.
Fuel injection system with such valve gear is the theme of other independent claims.
The advantageous embodiment of the present invention is the theme of dependent claims.
Valve gear for fuel injection system has high pressure charging hole and valve seat, and the high pressure charging hole is used to spray fuel
The high-pressure area for penetrating system is fluidly connected to valve gear, longitudinal axis of the valve seat along valve gear and potted component phase interaction
It is configured for opening and closing high pressure charging hole.High pressure charging hole has the first diameter with valve seat adjacent, and with valve
Seat place spaced apart includes the aperture with Second bobbin diameter, and the Second bobbin diameter is less than the first diameter.
Aperture in high pressure charging hole（The aperture is connected to the flow direction that valve gear is flowed into along fluid from high-pressure area
On valve seat upstream）Ensure that the stroke of the valve gear for opening high pressure charging hole is limited, so valve gear is bright
It is aobvious stable.Aperture and valve base chamber are every being provided separately, so that the Opening pressure characteristic curve of valve gear continues with flat side
Formula extends, because the diameter of valve seat keeps constant.Therefore, specified by the maximum of valve gear it is through-flow in the case of, aperture pair
The normal function of the valve gear has little to no effect.Only when valve gear has the trend for becoming unstable（If fuel sprays
Penetrate in system and bubble or air plankton be present and therefore the stroke of valve gear generally becomes much larger）Aperture is just worked, from
And cause pressure drop and therefore limit stroke.
First diameter in high pressure charging hole is preferably substantially equivalent to the diameter of valve seat.Here, valve seat and high pressure charging
First diameter in the hole especially model with the value in the range of 0.7mm to 0.85mm, preferably with 0.75mm to 0.8mm
Enclose interior value.If the diameter of valve seat and high pressure charging hole is preferably located in the prescribed limit, then valve can be realized
The flat Opening pressure characteristic curve of device.
The Second bobbin diameter in aperture advantageously has 0.4mm to 0.6mm value.So, aperture can advantageously fire
Worked when bubble be present in material spraying system, and pressure drop can be caused, so the stroke of valve gear can be limited,
Otherwise the trip will become too much.Therefore, it is also advantageous in that longitudinal axis of the aperture along valve gear has 0.8mm extremely
1.2mm length.
It is preferably provided for connecting the transitional region of the first diameter and Second bobbin diameter, the transitional region is relative to valve gear
Longitudinal axis obliquely set.So, it is preferably able to realize between two in high pressure charging hole diameters soft
Transition, thus, it is possible to prevent to be vortexed in the transition position.
It is advantageously improved at one in scheme, is configured to spaced apart extremely with valve seat towards the top edge in the aperture of valve seat
Few 0.8mm to 1.2mm spacing.In upstream orifice relative to the position of valve seat and under the positive space formed,
In the case of the relative high throughflow by valve gear, the aperture preferably is practically without negatively affecting to Opening pressure, from
And to continue the flat Opening pressure characteristic curve for keeping valve gear.Therefore, the structure spaced apart as the aperture
As a result, for example, in the case of in the case of flowing through the 6 l/h through-current capacity of the fluid of valve gear with 100 l/h through-current capacity,
The Opening pressure of valve gear is located in the range of identical.
In an improvement project, aperture is formed in bushing, and the bushing is depressed into high pressure charging hole, and the bushing
With through flow hole for fluidly connecting high-pressure area and valve seat.So, high pressure charging hole can be as known
Manufactured, and only an add ons are depressed into high pressure charging hole, then form aperture by this way.Such one
Come, the machining steps in high pressure charging hole can be preferably avoided.
Here, the aperture is preferably provided in the end of the bushing towards valve seat.However, as an alternative, aperture
It can be centrally positioned in along the longitudinal axis of valve gear in bushing.This, which can have, has the advantage that：So, can be in hole
The more stubbed transition in edge is realized between the minor diameter and high pressure charging hole or the major diameter of through flow hole of mouth, thus preferably
The vortex in high pressure charging hole or through flow hole can be avoided.
If the aperture is realized by way of setting bushing, then advantageously bushing as it is overall be also arranged to
Seal receptacle is at a spacing.
High pressure charging hole and valve seat are preferably formed in valve plate, therefore to enable the installation of valve gear have than high
The simpler design of design that pressure charging hole and valve seat are collectively forming with other elements by single housing part.
In high pressure charging hole, high pressure charging hole has the first diameter in the region of valve seat, and this is greater diameter than
Two diameters, the Second bobbin diameter are present in the region in the aperture in high pressure charging hole.It is advantageously improved at one in scheme, in addition,
The upstream in the aperture of high pressure charging hole in the flowing direction（It is i.e. further spaced apart with valve seat）With the 3rd diameter, the 3rd
Diameter is preferably more than the first diameter, so as to hence in so that the main laminar flow from high-pressure area to valve seat can be realized.
In a kind of favourable improvement scheme, prestress spring is provided with, the prestress spring is in particularly constructed as
Helical spring, to be answered on the direction of valve seat along the longitudinal axis of valve gear using prestress to potted component pre-add
Power.
In particularly preferred improvement project, valve gear is configured to electromagnetic valve device, and it has can be along valve gear
Longitudinal axis movement armature.Thus the opening travel of valve gear may be influenceed on one's own initiative.Armature is preferably provided in pre-add
Between stress spring and potted component, so as to which therefore there is favorable influence to the precharge pressure of prestress spring.It is especially excellent
Choosing, armature, prestress spring and potted component are unconnected elements, and they only pass through the pre-add of prestress spring
Pressure is mechanically coupled to one another.This can be avoided in component wear（Such as the pin fracture in valve gear）Valve gear no longer acts as
With because such pin for power transmission be present.
Potted component is preferably constructed to sphere, and the sphere especially has 1mm to 1.5mm diameter.Enter one
Preferably, valve gear has at least one tap for exporting fluid from valve gear to step.Here, at least one discharge
The diameter in hole is preferably more than the diameter of potted component.The major diameter of tap is favourable, therefore to realize fluid
From the quick outflow of valve gear.If the stroke of valve gear（That is the spacing of potted component and valve seat）Then become too much,
It can then happens is that, potted component is lost via tap, because tap has the diameter bigger than potted component.In order to
Potted component is avoided to be lost via tap, it is advantageous that the aperture connected by upstream limits the trip.
It is particularly preferred that valve gear is configured to pressure limiting valve for the high-pressure area release for fuel injection system,
Pressure limiting valve especially be designed to cause it for the fuel injection system release in 200 bars to 3000 bars of pressure limit.
Herein, it is therefore particularly preferred that unloaded in the range of 1500 bars and 3000 bars, this pressure corresponded in diesel applications situation
Scope.
There is high pressure fuel pump for the fuel injection system at least one combustion chamber by fuel injection to internal combustion engine
For loading fuel with high pressure, and the fuel storage region domain with the downstream for being positioned at high pressure fuel pump adds for storage
The fuel of pressure, valve gear as described above is provided with high pressure fuel pump and/or fuel storage region domain.So, can
The excess pressure in fuel injection system is avoided, thus reduces the risk of some damage parts in fuel injection system.
Brief description of the drawings
Hereinafter by accompanying drawing, present invention will be further described is advantageously improved scheme, wherein：
Fig. 1 shows the longitdinal cross-section diagram of fuel injection system, and the fuel injection system has high pressure fuel pump, fuel storage region
Domain and the valve gear as pressure limiting valve；
Fig. 2 shows the longitdinal cross-section diagram by valve gear, and the valve gear can be arranged on the fuel injection system according to Fig. 1
In；
Fig. 3 shows the detail view of the longitdinal cross-section diagram of Fig. 2 in the valve seat area of valve gear in first embodiment；
Fig. 4 shows the detail view of the longitdinal cross-section diagram of Fig. 2 in valve seat area in second embodiment；
Fig. 5 shows the detail view of the longitdinal cross-section diagram of Fig. 2 in valve seat area in 3rd embodiment；
Fig. 6 shows the longitudinal cross-section detail view of the valve gear of the prior art in valve seat area；And
Fig. 7 shows the chart for the desired Opening pressure for representing the valve gear that Fig. 2 is shown into Fig. 6, and the Opening pressure depends on
In passing through the through-flow of valve gear.
Embodiment
Fig. 1 shows the longitdinal cross-section diagram of fuel injection system 22, by the fuel injection system, fuel can spray to
In at least one combustion chamber of internal combustion engine.Fuel injection system 22 has high pressure fuel pump 24 and fuel storage region domain 26.
Fuel loads high pressure by high pressure fuel pump 24, for example, diesel oil of the pressure between 1500 bars and 3000 bars or
Gasoline of the pressure between 200 bars and 350 bars.Therefore, fuel enters high pressure fuel pump via inlet valve 28 from area of low pressure 30
In 24 pressure space 32.Pump piston 34（It is driven by drive device 36）Moved in pressure space 32 alternating translational, and
And the volume of pressure space 32 is reduced or increased in this process.So, the fuel in pressure space 32 is compressed, and
Therefore it is loaded pressure.After compression in pressure space 32, fuel through outlet valve 38 leaves pressure space 32 and enters combustion
Expect in storage region 26.
Pressurized fuel is stored in fuel storage region domain 26, until it is injected into the combustion chamber of internal combustion engine.Fuel is deposited
Storage area domain 26 forms a part for the high-pressure area 40 of fuel injection system 22.In order to protect high-pressure area 40 from excessive pressure
Power load, valve gear 10 is provided with, the valve gear is configured to pressure limiting valve 12, exists so as to therefore in high-pressure area 40 excessive
Fuel is discharged from high-pressure area 40 in the case of pressure.For this.As shown in fig. 1, valve gear 10 is configured such that it will
High-pressure area 40 is connected to the pressure space 32 of high pressure fuel pump 24.In the embodiment illustrated in fig. 1, therefore pressure limiting valve 12 will
Excessive fuel is expelled in pressure space 32.However, it is also feasible that pressure limiting valve 12 is arranged so that it discharges fuel
Into the area of low pressure 30 of the upstream of high pressure fuel pump 24.
In the embodiment illustrated in fig. 1, pressure limiting valve 12 is arranged in the pump case 42 of high pressure fuel pump 24, with outlet valve
38 is adjacent.Alternatively, however, or in addition, pressure limiting valve 12 can be also arranged on the housing in fuel storage region domain 26.
Show the pressure limiting valve 12 as simple check-valves in Fig. 1, and therefore its have with hereafter described in reality
Apply the slightly different construction of example.However, it realizes identical purpose in principle.
Fig. 2 shows the longitdinal cross-section diagram of valve gear 10 in the first embodiment, and the valve gear is the theme of the application.
Valve gear 10 has valve plate 16, and valve seat 18 and high pressure charging hole 20 are constructed in the valve plate, and high pressure charging hole 20 will
Valve gear 10 is connected to the high-pressure area 40 of fuel injection system 22.Potted component 14 is provided for closing high pressure charging hole
20, the potted component 14 is in particularly constructed as sphere 44.In addition to high pressure charging hole 20, also set up in valve gear 10
There is tap 46, by the tap 46, fluid can leave valve gear 10.The fluid is preferably fuel.Should by pre-add
Power spring 54（Particularly helical spring）, potted component 14（The potted component is configured to move in valve chest 52）By
The prestress F of the prestress spring 54 acted on along the longitudinal axis 56 of valve gear 10VIt is pressed on valve seat 18, and therefore valve
Device 10 remains turned-off.The pressure of fluid only in high pressure charging hole 20 overcomes the prestress of prestress spring 54
FVWhen, the ability of potted component 14 is lifted from valve seat 18, and therefore discharges through-flow, and whereby, fluid can be flowed by tap 46
Go out valve gear 10 and therefore also flow out high-pressure area 40, high-pressure area 40 is relaxed.
Fig. 3 shows the detail view of the valve gear 10 of Fig. 2 in the first embodiment of valve gear 10.
Here, high pressure charging hole 20 is realized by the simple hole in valve plate 16 and has multiple diameters.High pressure charging
The first diameter D in hole 20H1It is disposed adjacent with valve seat 18, and its diameter DH1With the diameter D of valve seat 18VSIt is substantially the same.With
The position spaced apart of valve seat 18, i.e., with the flow direction of the fluid that flows through valve gear 10 on the contrary, high pressure charging hole 20 has the
Two diameter DH2, Second bobbin diameter DH2Less than the first diameter DH1.So, aperture 58 is configured with high pressure charging hole 20, such as
If air plankton being present in fluid in fruit fuel injection system 22, then the aperture functions to, and does not therefore have hole
The valve of mouth 58 will become unstable, i.e. formation of the potted component 14 away from valve seat 18 is excessive.Aperture 58 in the flowing direction
Upstream end, high pressure charging hole have the 3rd diameter DH3, the 3rd diameter is more than Second bobbin diameter DH2And it is more than the first diameter DH1。
In this region, valve gear 10 is connected to the high-pressure area 40 of fuel injection system 22 by high pressure charging hole 20, and favorably
Be this high pressure charging hole 20 have expand diameter DH3, valve dress is flow to possibly as laminar flow therefore to enable to flow to end
Put in 10.In each case, from the 3rd diameter DH3To Second bobbin diameter DH2And from Second bobbin diameter DH2To the first diameter DH1Deposit
In transitional region 60, corresponding diameter is connected to each other by the transitional region 60, and the transitional region is relative to valve gear 10
Longitudinal axis 56 be obliquely installed, therefore similarly to contribute to laminar flow by valve gear 10.
First diameter DH1And the diameter D of valve seat 18VSIn the range of 0.7mm to 0.85mm, in the present example
Between 0.75mm and 0.8mm.On the contrary, the diameter D in the region in aperture 58H2Scope in 0.4mm to 0.6mm
It is interior.
The top edge 62 in aperture 58（The top edge is configured to face valve seat 18）, should with the interval d spaced apart of valve seat 18
Interval is in the range of 0.8mm to 1.2mm.By means of aperture 58 along flow direction the quilt at the interval d of the upstream of valve seat 18
The fact that connection, more stable valve gear 10 can be realized first, and secondly it may be said that be able to maintain that be not open 58 valve
The flat Opening pressure characteristic curve of device 10.
Fig. 4 shows the second embodiment of valve gear 10, and bushing 64 is set, and the bushing is depressed into high pressure charging hole 20
In, and the bushing has through flow hole 66, and by the through flow hole, fluid can reach valve seat 18 by high-pressure area 40.Here,
Aperture 58 is formed by the contraction of through flow hole 66.In the fig. 4 embodiment, the face valve of bushing 64 is arranged in this aperture 58
At the end 68 of seat 18.Alternatively, however, can also be arranged to opening 58 in the 3rd embodiment of valve gear 10 medially to set
Put in bushing 64, as shown in Figure 5.
All solutions tool being shown in which has the advantage that：The stability of valve gear 10 first is significantly increased, and
Secondly at the same time the Opening pressure characteristic curve of valve gear 10 extends relatively flat, and the Opening pressure characteristic curve depends on
Pass through the through-flow of valve gear 10.
Claims (10)
1. one kind is used for fuel injection system（22）Valve gear（10）, the valve gear（10）With high pressure charging hole（20）With
For by the fuel injection system（22）High-pressure area（40）It is connected to the valve gear（10）, and have along described
Valve gear（10）Longitudinal axis（56）With potted component（14）The valve seat of interaction（18）For described in opening and closing
High pressure charging hole（20）, the high pressure charging hole（20）With the valve seat（18）Adjacent has the first diameter（DH1）And
With the valve seat（18）Place spaced apart has aperture（58）, the aperture（58）With Second bobbin diameter（DH2）, described second is straight
Footpath（DH2）Less than first diameter（DH1）.
2. valve gear according to claim 1（10）, it is characterised in that the high pressure charging hole（20）It is described first straight
Footpath（DH1）It is approximately equivalent to the diameter of the valve seat（DVS）, and especially there is 0.7mm to 0.85mm value, it is more special
There is no 0.75mm to 0.8mm value, and/or characterized in that, the Second bobbin diameter（DH2）With 0.4mm to 0.6mm's
Value, and/or characterized in that, transitional region（60）It is provided for connecting first diameter（DH1）With the Second bobbin diameter
（DH2）, the transitional region（60）Relative to the valve gear（10）Longitudinal axis（56）It is obliquely installed.
3. valve gear according to claim 1 or 2（10）, it is characterised in that towards the valve seat（18）The aperture
（58）Top edge（62）It is configured to and the valve seat（18）At least 0.8mm to 1.2mm spaced apart spacing, and/or its
It is characterised by, along the valve gear（10）Longitudinal axis（56）The aperture（58）Length be 0.8mm to 1.2mm.
4. the valve gear according to any one of claims 1 to 3（10）, it is characterised in that the aperture（58）Formed
Bushing（64）In, the bushing（64）It is depressed into the high pressure charging hole（20）In, and the bushing（64）With through flow hole
（66）For fluidly connecting the high-pressure area（40）With the valve seat（18）.
5. valve gear according to claim 4（10）, it is characterised in that the aperture（58）It is arranged on towards the valve seat
（18）The bushing（64）End（68）Place, or characterized in that, the aperture（58）Along the valve gear（10）
Longitudinal axis（56）It is centrally arranged at the bushing（64）In.
6. the valve gear according to any one of claim 1 to 5（10）, it is characterised in that the high pressure charging hole（20）
With the valve seat（18）Formed in valve plate（16）In, and/or characterized in that, prestress spring（54）, particularly spiral bullet
Spring is set, for using in the valve seat（18）Direction on along the valve gear（10）Longitudinal axis（56）It is pre-
Plus-pressure（FV）To the potted component（14）Prestress.
7. the valve gear according to any one of claim 1 to 6（10）, the valve gear is configured to electromagnetic valve device,
The electromagnetic valve device has can be along the valve gear（10）Longitudinal direction axially（56）Mobile armature, and the armature
It is typically provided at the prestress spring（54）With the potted component（14）Between, the armature and the prestress
Spring（54）And the potted component（14）Unconnected element in particular, it only passes through the prestress spring（54）
Prestress（FV）It is mechanically coupled to one another.
8. the valve gear according to any one of claim 1 to 7（10）, it is characterised in that the potted component（14）Quilt
It is configured to sphere（44）, it is in particularly constructed as that there is 1mm to the sphere of 1.5mm diameters（44）, it is preferable that it is at least one
Tap（46）It is provided for from the valve gear（10）Export fluid, the tap（46）Diameter be more than it is described close
Seal element（14）Diameter.
9. the valve gear according to any one of claim 1 to 8（10）, the valve gear（10）It is configured to pressure limiting valve
（12）For for fuel injection system（22）High-pressure area（40）Release, the pressure limiting valve（12）Especially it is configured to
For in 200 bars to 3000 bars, the especially fuel injection system in 1500 bars to 3000 bars of pressure limit
（22）Release.
10. a kind of be used for the fuel injection system at least one combustion chamber of fuel injection to internal combustion engine（22）, the combustion
Expect spraying system（22）With high pressure fuel pump（24）For loading fuel with high pressure, and have and be positioned at the high compression ignition
Expect pump（24）Downstream fuel storage region domain（26）For storing pressurized fuel, according to any one of claim 1 to 9 institute
The valve gear stated（10）It is arranged on the high pressure fuel pump（24）And/or the fuel storage region domain（26）Place.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102015210800.7 | 2015-06-12 | ||
| DE102015210800.7A DE102015210800A1 (en) | 2015-06-12 | 2015-06-12 | Valve device for a fuel injection system and fuel injection system |
| PCT/EP2016/062518 WO2016198311A1 (en) | 2015-06-12 | 2016-06-02 | Valve device for a fuel injection system and fuel injection system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN107667217A true CN107667217A (en) | 2018-02-06 |
Family
ID=56097123
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201680034294.7A Pending CN107667217A (en) | 2015-06-12 | 2016-06-02 | Valve gear and fuel injection system for fuel injection system |
Country Status (5)
| Country | Link |
|---|---|
| EP (1) | EP3308011A1 (en) |
| KR (1) | KR20170059470A (en) |
| CN (1) | CN107667217A (en) |
| DE (1) | DE102015210800A1 (en) |
| WO (1) | WO2016198311A1 (en) |
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|---|---|---|---|---|
| CN101432518A (en) * | 2006-04-25 | 2009-05-13 | 罗伯特·博世有限公司 | High pressure fuel pump |
| CN102588656A (en) * | 2010-10-21 | 2012-07-18 | 康卓彬德电磁技术有限公司 | High pressure regulating valve |
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| JPS62134916A (en) * | 1985-12-06 | 1987-06-18 | Daihen Corp | Winding machine |
| DE19822671A1 (en) * | 1998-05-20 | 1999-11-25 | Bosch Gmbh Robert | Pressure limiting valve for internal combustion engine |
| DE19827267A1 (en) * | 1998-06-18 | 1999-12-23 | Bosch Gmbh Robert | Fuel injection valve for high pressure injection with improved control of the fuel supply |
| DE10059425A1 (en) * | 2000-11-30 | 2002-06-06 | Bosch Gmbh Robert | Fuel injection pump for internal combustion engines, in particular diesel engines |
| DE10112163A1 (en) * | 2001-03-14 | 2002-09-19 | Bosch Gmbh Robert | Accumulator injection system (common rail) for internal combustion engines |
| US7441546B2 (en) * | 2005-07-28 | 2008-10-28 | Denso Corporation | Valve apparatus |
| EP2728163B1 (en) * | 2012-10-30 | 2016-08-17 | Delphi International Operations Luxembourg S.à r.l. | Valve arrangement |
| JP5857980B2 (en) * | 2013-02-06 | 2016-02-10 | 株式会社日本自動車部品総合研究所 | solenoid valve |
| DE102013214589A1 (en) * | 2013-07-25 | 2015-01-29 | Robert Bosch Gmbh | Switching valve for a fuel injector |
-
2015
- 2015-06-12 DE DE102015210800.7A patent/DE102015210800A1/en not_active Ceased
-
2016
- 2016-06-02 WO PCT/EP2016/062518 patent/WO2016198311A1/en active Application Filing
- 2016-06-02 EP EP16726580.0A patent/EP3308011A1/en not_active Ceased
- 2016-06-02 KR KR1020177010975A patent/KR20170059470A/en not_active Application Discontinuation
- 2016-06-02 CN CN201680034294.7A patent/CN107667217A/en active Pending
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101432518A (en) * | 2006-04-25 | 2009-05-13 | 罗伯特·博世有限公司 | High pressure fuel pump |
| CN102588656A (en) * | 2010-10-21 | 2012-07-18 | 康卓彬德电磁技术有限公司 | High pressure regulating valve |
Also Published As
| Publication number | Publication date |
|---|---|
| EP3308011A1 (en) | 2018-04-18 |
| DE102015210800A1 (en) | 2016-12-15 |
| KR20170059470A (en) | 2017-05-30 |
| WO2016198311A1 (en) | 2016-12-15 |
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Application publication date: 20180206 |
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