CN208534664U - Medium and heavy-duty engines monomer crosspointer valve twin-jet nozzle high pressure common rail injector - Google Patents
Medium and heavy-duty engines monomer crosspointer valve twin-jet nozzle high pressure common rail injector Download PDFInfo
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- CN208534664U CN208534664U CN201820796050.9U CN201820796050U CN208534664U CN 208534664 U CN208534664 U CN 208534664U CN 201820796050 U CN201820796050 U CN 201820796050U CN 208534664 U CN208534664 U CN 208534664U
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Abstract
A kind of medium and heavy-duty engines monomer crosspointer valve twin-jet nozzle high pressure common rail injector, including magnetic core valve seat, ball valve ejector rod base installation nut, ball valve ejector rod base, needle control-rod pedestal, oil nozzle installation nut and oil nozzle valve body；There are two solenoid valves for setting in magnetic core valve seat, there are two needle control-rods for setting in needle control-rod pedestal, there are two needle chambers for the setting of oil nozzle valve inner, lower end setting is there are two atomizer, and there are two the intracavitary settings of needle is connected with needle control-rod, the oil nozzle needle for controlling two atomizers respectively.In addition, ball valve mandril and high pressure sealing ball valve split settings further decrease required electromagnetic force by the way that ball valve mandril is designed as enlarged diameter section and reduced diameter section.
Description
Technical field
The present invention relates to Fuel Feeding System for Diesel Engine commander domain more particularly to a kind of monomers of suitable medium and heavy-duty engines
Crosspointer valve twin-jet nozzle high pressure common rail injector.
Background technique
To improve the fuel economy of diesel engine and the discharge amount of the improvement original pernicious gas of engine, and optimization diesel oil
Machine noise and vibration need to improve the effect of air Yu fuel oil mixed aerosol, and first delay to the control realization of fuel injection rate
Anxious trend afterwards.Currently in the diesel engine high-pressure co-rail system that market accounts for absolutely leading scheme status, widespread consensus and method are
The fuel pressure levels for constantly improving common rail system mention high injection pressure to enhance fuel atomization effect, for example, from before compared with
It is even higher that 1800bar, 2200bar are increased to for universal 1600bar；And utilize the pre- of multiple minimum oil mass (0.5~1mg)
Injection is so that injection rate realizes anxious jeting effect after the rate of heat release being intended under ideal conditions is first delayed；Even same
Secondary course of injection mid-early stage use carries out the injection of front portion period with pressure identical in high pressure oil rail, in the latter portion of oil spout
It is further increased in oil injector body by the fluid power enlarger inside oil injector body at times and pressure is sprayed at atomizer end,
To achieve the effect that improve injection rate and reinforce jet atomization.
But fuel oil high-pressure system stress level is improved too much, it will lead to the side such as material selection, part size, technique
In face of the higher requirement of processing and manufacturing aspect.In addition in current diesel injector when only one atomizer, due to one
The spray orifice aperture of a atomizer and nozzle hole number first have to injection rate requirement needed for meeting normal fuel delivery, it is therefore desirable to
Certain enough fuel oils spray sectional area；But oil mass needed for pilot injection is again minimum, therefore sprays required injection duration
Short, oil nozzle needle lift is about to begin closing when sufficiently opening not yet, thus the pilot injection of minimum oil mass be all often
Mouth end far below system fuel pressure is sprayed and is carried out under pressure, and throttling is serious, leads to this part of fuel-injected of pilot injection
Atomization quality is not high, is harmful to the particulate emission of original machine.
Currently, twin-jet nozzle fuel injector is essentially all for fuel combination, as patent document CN105781836 A is disclosed
A kind of double electromagnetism hybrid fuel jet devices of combined type supercharging fuel-non pressurized combustion gas, are controlled using two solenoid valves respectively
The course of injection of combustion gas and fuel oil, by changing two electromagnetic valve work states and job order, injection apparatus, which can be realized, only to be sprayed
Penetrate fuel oil or combustion gas, two kinds of fuel at the same spray, multiple-working modes, the engine such as two kinds of fuel sequencings injections can be pure
It works under fuel oil or oil pilot combustion gas mode；Patent document CN1036670850A disclose a kind of dual fuel injector and
Using the common rail fuel system of the dual fuel injector, each fuel injector includes injector body, is limited fluidly
It is connected to the first fuel inlet of the first common rail and is fluidly connected to the second fuel inlet of the second common rail.By making first
Electric actuator, which is powered, to be conducive to opening direct operation stop part from first jet outlet group injecting LPG in liquefied condition.By making second
Electric actuator is powered to open intake valve and come gas nozzle chamber full of the big pressurized fuel gas of pressure ratio valve opening pressure
Traditional spring biasing stop part is opened to promote gaseous fuel to eject second nozzle outlet group, to realize from second nozzle
Mouth group injection gaseous fuel.
There has been no for the application example for using twin-jet nozzle fuel injector on diesel engine at present.The present invention provides a kind of medium and heavy
Use for diesel engine monomer crosspointer valve twin-jet nozzle high pressure common rail injector, the fuel injector have the fuel injector of application relative to traditional scheme
Fuel injection mode can be made more flexible, the smaller small oil mass injection of quality is steadily obtained, can not greatly improve
It is realized in the case of oily rail pressure power closer to the control of injection rate needed for diesel engine ideal burning and good air and fuel oil
Mixed aerosol effect.
Summary of the invention
The present invention is directed to not increase substantially diesel common rail system pressure levels and cylinder of diesel engine to cover fuel injector installation
Under the conditions of space is limited, invention designs one kind and has good high pressure (meeting or exceeding 1600 bars) fuel sealing function
New-type seal ball-valve control mechanism, design a kind of only one compact oil injector body on this basis but have two components
Open the fuel injector of the high pressure fuel spray orifice of independent control.So that this new-type fuel injector is more more suitable than current traditional scheme fuel injector
Diesel combustion feature is answered, controls diesel injection rate more flexiblely, is conducive to the mist for further improving high-pressure diesel injection
Change effect, improves engine original machine emission level；Advantageous optimization injection rate rule, it is horizontal further to excavate diesel powered.
The purpose of the present invention is what is be achieved through the following technical solutions.
A kind of medium and heavy-duty engines monomer crosspointer valve twin-jet nozzle high pressure common rail injector, including magnetic core valve seat, ball valve top
Bar pedestal installs nut, ball valve ejector rod base, needle control-rod pedestal, oil nozzle installation nut and oil nozzle valve body；It is characterized by:
There are two solenoid valves, each solenoid valve to all have armature compression ring, solenoid valve armature, magnetic core and be fixed and clamped for setting in magnetic core valve seat
Ring, magnetism-isolating loop, electromagnetic valve coil, solenoid valve magnetic core, air gap adjustment ring, armature preloading spring and ball valve mandril；Ball valve mandril is worn
It is located in ball valve ejector rod base, ball valve mandril seal sleeve is provided in the recess of ball valve ejector rod base；Ball valve mandril is in ball valve
There is in tip-lever support enlarged diameter section and reduced diameter section, the inner hole cylindrical surface precision-fit of reduced diameter section and ball valve ejector rod base, greatly
Diameter segment and ball valve mandril seal sleeve inner hole cylindrical surface precision-fit；There are two needles to control for setting in needle control-rod pedestal
Bar；There are two needle chambers for the setting of oil nozzle valve inner, and there are two atomizers for lower end setting；There are two the intracavitary settings of needle and needle
Control-rod be connected, the oil nozzle needle for controlling two atomizers respectively.
Further, ball valve ejector rod base lower end is provided with ball valve pedestal, setting and high pressure sealing ball valve in ball valve pedestal
The bellmouth to match, high pressure sealing ball valve control the connection of high pressure fuel and low pressure drainback passage；High pressure sealing ball valve body
Be mostly within high pressure fuel, high pressure sealing ball valve contacts to form a seal band with the bellmouth of ball valve pedestal,
When high pressure sealing ball valve is pushed away ball valve pedestal by ball valve mandril, pressure release effect is generated at seal band.
Further, high pressure sealing ball valve contacts the section that the seal band to be formed is surrounded with the bellmouth of ball valve pedestal
Product is equal or suitable with the difference of the enlarged diameter section of ball valve mandril and the sectional area of reduced diameter section.Therefore the effect of high pressure fuel sealing
Additional biggish initial tension of spring is not needed to compress to seal ball-valve, so as to farthest reduce solenoid valve
The pretightning force of armature preloading spring in suction and Current protocols, makes it that need to only meet major moving parts solenoid valve armature and sealing
Ball valve mandril speed responsive and resting position limit, and solenoid valve size is effectively reduced.
Further, two groups of nozzle hole numbers of the restriction of the spray orifice of two nozzles, two nozzles are respectively 3 to 6, total spray orifice
Number increases to 10 even 11,12 by 8 to 9 of common solution.
Further, two solenoid valves mutually stagger in the height direction, from vertical direction on see in the presence of partly overlapping, can
To reduce fuel injector integral diameter.
Further, the frictional force generated using the interference fit of armature compression ring and ball valve mandrel ends, solenoid valve
Armature is fixed on ball valve mandril.
Further, the magnetic core ring that is fixed and clamped is not 360 degree of complete rings, has certain degree notch, utilizes itself and magnetic
The interference fit in the hole on core valve seat generates frictional force, Motionless electromagnetic valve magnetic core.
Further, when control electromagnetic valve work is powered, high pressure suffered by the direction of motion and seal ball-valve after armature stress
The pressure direction of fuel oil is opposite.
Compared with prior art, because there are two groups of independent control atomizers, common rail system stress level is not being improved
In the case of, an oil nozzle elder generation oil spout so latter two oil nozzle oil spout simultaneously can be obtained preferably and be leveled off to needed for diesel engine
The oily stage oil spout heat release of main jet first delay after anxious jet mode.Two oil nozzles respectively flexibly arrange in pairs or groups by nozzle hole number, two groups of spray orifices
Diameter is set separately on demand, and total orifice number is more when can be than only one oil nozzle of traditional scheme, in single injection diameter phase
When or smaller situation under available higher maximum comprehensive injection rate, this helps to further increase engine peak
Value torque reduces the generation of nitrogen oxides simultaneously, and it is horizontal further to improve vibrating noise.
Meanwhile ball valve mandril is designed as enlarged diameter section and reduced diameter section, it, can be into one using the hydraulic coupling of high pressure fuel
Step reduces required electromagnetic force.Similarly, when reaching an equal amount of electromagnetic force, some solenoid valve magnetic core knots can suitably be increased
Structure selects saturation magnetic flux lower but the lower core material of cost, reduces the dependence to rare precious metals material cobalt etc., from
And part manufacturing cost is saved in this respect.
When one of hole in nozzle number is significantly reduced than the hole in nozzle number of traditional scheme, can more stably obtain
The pilot injection of smaller quality.Spray orifice means that fuel oil injection actual internal area is small less, in the pre- discharge rate in the case where institute of identical fuel oil
Oil injection duration is needed to lengthen, so that pilot injection be made to carry out in the case where Geng Gaozui end pressure, pilot injection atomization quality is more preferable, from
And help to improve the particulate emissions level of engine original machine.
Detailed description of the invention
Fig. 1 is the overall structure diagram of fuel injector of the present invention.
Fig. 2 is the schematic diagram of ball valve partial structurtes.
Fig. 3 is the top view of twin-jet nozzle.
Fig. 4 is the sectional view of twin-jet nozzle.
Fig. 1 part name:
1, solenoid valve wiring stitch；2, fuel injector end cap；3, magnetic core valve seat；4, armature compression ring；5, solenoid valve armature；6,
Magnetic core is fixed and clamped ring；7, magnetism-isolating loop；8, electromagnetic valve coil；9, solenoid valve magnetic core；10, air gap adjustment ring；11, armature pre-tightens bullet
Spring；12, ball valve ejector rod base installs nut；13, ball valve ejector rod base；14, ball valve mandril seal sleeve；15, ball valve mandril；
16, ball valve pedestal；17, high pressure sealing ball valve；18, needle control-rod pedestal；19, needle control-rod；20, oil nozzle installs nut；
21, oil nozzle needle preloading spring；22, oil nozzle valve body；23, oil nozzle needle
Specific embodiment
As shown in Figure 1, monomer crosspointer valve twin-jet nozzle high pressure common rail injector of the invention includes magnetic core valve seat 3, ball valve top
Bar pedestal installs nut 12, ball valve ejector rod base 13, ball valve pedestal 16, needle control-rod pedestal 18, oil nozzle and installs 20 and of nut
Oil nozzle valve body 22.
There are two solenoid valves, each solenoid valve to all have armature compression ring 4, solenoid valve armature 5, magnetic for setting in magnetic core valve seat
Core is fixed and clamped ring 6, magnetism-isolating loop 7, electromagnetic valve coil 8, solenoid valve magnetic core 9, air gap adjustment ring 10, armature preloading spring 11 and ball
Valve mandril 15.The frictional force generated using the interference fit of armature compression ring 4 and 15 end of ball valve mandril, solenoid valve armature 5
It is fixed on ball valve mandril 15；The magnetic core ring 6 that is fixed and clamped not is 360 degree of complete rings, and has been designed to certain degree and has lacked
Mouthful, using the interference fit of itself and the hole on magnetic core valve seat 3, generate frictional force, Motionless electromagnetic valve magnetic core 9.Ball valve mandril 15
Lower part is threaded through in ball valve ejector rod base 13.Two solenoid valves mutually stagger in the height direction, from vertical direction on see presence
It partly overlaps, to reduce fuel injector integral diameter.
13 lower end of ball valve ejector rod base is provided with ball valve pedestal 16, is provided in ball valve pedestal and carries out to high pressure sealing ball valve
The annulus that the bellmouth of limit, high pressure sealing ball valve 17 and bellmouth taper-face contact are formed controls 53 mesohigh of noticeable degree oil groove
The on-off of fuel oil and low pressure drainback passage 52.When high pressure sealing ball valve 17 is pushed away ball valve pedestal by ball valve mandril 15, sealing ring
Pressure release effect, the connection of noticeable degree oil groove 53 and low pressure drainback passage 52, noticeable degree oil groove 53 and ball valve are generated at band
Fuel pressure decline in post rod hydraulic pressure balancing channel 51, the pressure to level off in low pressure drainback passage 52.
Such as Fig. 2,15 two sections of diameters of the ball valve mandril being placed in 13 range of ball valve ejector rod base are changed, i.e. ball valve mandril exists
There is enlarged diameter section and reduced diameter section, the diameter of reduced diameter section is R1, and the diameter of enlarged diameter section is R2 in ball valve tip-lever support.It is small straight
The inner hole cylindrical surface precision-fit of diameter section and ball valve ejector rod base forms high pressure sealing, enlarged diameter section and ball valve mandril seal sleeve
14 inner hole cylindrical surface precision-fit forms high pressure sealing.14 lower end surface of ball valve mandril seal sleeve and 16 end face of ball valve pedestal essence
Close fit forms high pressure sealing.Two sections of sealings of ball valve mandril diameter change are fixed against two individual parts-ball valve mandril respectively
Pedestal 13 and ball valve mandril seal sleeve 14 are conducive to make after Finishing Parts Machining the clearance fit of two sections of seal requests logical
The mode for crossing apolegamy is realized, to reduce the requirement of device to hole, axis machining accuracy.
15 end face of ball valve mandril can be processed into and be connect with Internal Spherical Surface shape with seal ball-valve in specific processing
Touching.Perhaps increase by one section of part one end between ball valve mandril 15 and seal ball-valve 17 and be processed into Internal Spherical Surface or the conical surface, separately
It is processed into plane and is contacted with ball valve mandril end face in one end.
There are two needle control-rod 19, needles to control low-pressure tank 53, high pressure oil storage for setting in needle control-rod pedestal 18
Slot 54, needle control chamber 55, control chamber meter in hole 56, control chamber fuel-displaced throttle orifice 57.
Oil nozzle valve body 22 is internally provided with two needle chambers, and there are two two groups of nozzle openings of atomizer for lower end setting.Needle chamber
Interior setting with needle control-rod 19 there are two being connected, for controlling the oil nozzle needle 23 of two atomizers respectively.
Ball valve mandril 15, high pressure sealing ball valve 17, needle control-rod 19, oil nozzle needle 23 are main moving parts.It is sending out
Motivation shutdown status, i.e. fuel system pressure are not set up when leveling off to natural environmental stress, because of the elastic force of preloading spring 21,
Needle control-rod 19 is urged on control-rod pedestal 18, oil nozzle needle 23 is urged to the lower end of oil nozzle valve body 22.Armature pre-tightens
Spring 11 oppresses solenoid valve armature 5 and ball valve mandril 15 toward top, by air gap adjustment ring 10 or the nose end of magnetic core valve seat 3
It is limited in face of ball valve mandril 15.Seal ball-valve 17 is free state at this time, is still in part needle control-rod bottom by self weight
On seat 18.
From bottom to top, oil nozzle valve body 22, needle control-rod pedestal 18, ball valve pedestal 16, ball valve ejector rod base 13, magnetic core valve
It needs to guarantee good coaxial position between seat 3, cooperation limitation is carried out by mutual positioning pin in assembly.
It is provided with electromagnetic valve coil stitch 1 outside fuel injector end cap 2, corresponding 2 stitch of each group of electromagnetic valve coil, totally 4
Stitch.
Fuel injector course of work explanation:
After engine start rotation, high-pressure oil pump first with rotation, oil nozzle high pressure oil storage tank 58 and 57,56,
55,54,53,51 signified fuel pressures everywhere rise.And actual internal area is maintained between low pressure drainback passage 52 and fuel tank
Biggish channel, therefore fuel pressure is suitable with environmental pressure at this.Engine startup operation initial stage, at noticeable degree oil groove 53
Fuel oil flows at 52, and seal ball-valve 17 will be driven to move upwards, finally will fit closely shape with 16 tapered surface of seal ball-valve pedestal
At high pressure sealing, entire fuel system establishes preliminary high pressure.
When not needing oil spout, electromagnetic valve coil 8 is in off-position, and solenoid valve armature 5 will be by solenoid valve magnetic core 9
Attraction.Around the high pressure fuel in ball valve post rod hydraulic pressure balancing channel 51 around 15 middle section of ball valve mandril, and lower end
In the low-pressure state of low pressure drainback passage 52, ball valve mandril 15 is greater than electromagnetism because of the downward hydraulic coupling that diameter difference generates at this time
The upward initial tension of spring of the armature preloading spring of 1 lower section of valve armature, and have downward movement tendency.Ball valve mandril 15 and sealing
Ball valve 17 will be in close contact state.
19 top each position i.e. 55,54,53 of needle control-rod etc. pressure and the comparable high pressure conditions of system rail pressure, it is hydraulic
Downward, atomizer needle 23 is oppressed in contact to power.Around 23 middle and lower sections of atomizer needle at high pressure oil storage tank 58 with system rail pressure phase
Work as state, hydraulic coupling is upward.Because of suffered hydraulic area and the relationship of hydraulic coupling size, oil nozzle needle 23 is close to oil spout mouth downward
Portion forms high pressure sealing, will not have fuel oil injection at injection hole on injection nozzle 11.
When needing oil spout, each part time job is described as follows: electromagnetic valve coil 8 is powered, and solenoid valve armature 5 is by downward
Suction, so that both hydraulic couplings that electromagnetic force suffered by solenoid valve armature 5+ball valve mandril 15 is generated by middle section diameter difference is downward
Resultant force, seal ball-valve 17 will be upwards for both 11 pretightning forces of resultant force > armature preloading spring+17 hydraulic compression power of seal ball-valve
The down thrust effect of ball valve mandril 15 is lower to be detached from 16 sealing cone of ball sealer valve seat, and needle controls oil groove 53 and ball valve mandril liquid
Pressure balance channel 51 is communicated with low pressure drainback passage 52.The mobile limit directed downwardly of ball valve mandril 15 is by the upper of seal ball-valve pedestal 16
End face provides.Needle control low-pressure tank 53 and the fuel pressure in ball valve post rod hydraulic pressure balancing channel 51 will settle to and return with low pressure
The comparable low voltage level in oily channel 52, fuel oil return to fuel tank.High pressure oil storage tank 54 is kept and the comparable high pressure of external system rail pressure
It is horizontal.
Because two restriction effects it is comparable into fuel-displaced throttle orifice 56 and 57 under the action of, ceaselessly there is high pressure fuel to pass through
Throttle orifice 56 enters control chamber 55, control chamber is flowed out further through throttle orifice 57, in the needle control chamber 55 above noticeable degree bar
Fuel oil will eventually be reduced to some stress level between high pressure oil storage tank 54 and low-pressure tank 53.Needle control at this time
Downward hydraulic force suffered by bar 19 processed reduces, and the pressure of 23 surrounding high pressure oil storage tank 58 of atomizer needle is also always maintained at and outside
The comparable high-pressure horizontal of system rail pressure.Resultant direction suffered by final atomizer needle 23 is lifted, injection hole on injection nozzle upwards upwards
High pressure fuel injection will be generated at 59.
Monomer crosspointer valve twin-jet nozzle high pressure common rail injector oil nozzle valve body outer diameter of the invention, can be than one group of spray of traditional scheme
7.2 millimeters of oil nozzle valve diameter of hole increase to 12.5 to 13.5 millimeters or so, are suitble in the middle weight for reaching certain cylinder diameter
It is applied on the larger diesel engine such as type truck, engineering machinery.Its total height is smaller than transmission scheme, it is possible to reduce to 15 public affairs
Point or so, in terms ofs oil injector body top and top components such as camshaft etc. can be reduced in certain applications
Interference so that engine cylinder cover above components layout it is freer.
Of the invention is to reduce solenoid valve power and controlling using seal ball-valve control-rod to seal ball-valve for specially designing
New departure of system can be controlled by the liquid packing of other field and be used for reference, and be not limited in using in diesel fuel system.
Claims (8)
1. a kind of medium and heavy-duty engines monomer crosspointer valve twin-jet nozzle high pressure common rail injector, including magnetic core valve seat, ball valve mandril
Pedestal installs nut, ball valve ejector rod base, needle control-rod pedestal, oil nozzle installation nut and oil nozzle valve body；
It is characterized by: there are two solenoid valve, each solenoid valve all has armature compression ring, solenoid valve rank for setting in magnetic core valve seat
Iron, magnetic core are fixed and clamped ring, magnetism-isolating loop, electromagnetic valve coil, solenoid valve magnetic core, air gap adjustment ring, armature preloading spring and ball valve
Mandril；
Ball valve mandril is threaded through in ball valve ejector rod base, and ball valve mandril seal sleeve is provided in the recess of ball valve ejector rod base；
Ball valve mandril has enlarged diameter section and reduced diameter section, the inner hole of reduced diameter section and ball valve ejector rod base in ball valve tip-lever support
Cylindrical surface precision-fit, enlarged diameter section and ball valve mandril seal sleeve inner hole cylindrical surface precision-fit；
There are two needle control-rods for setting in needle control-rod pedestal；There are two needle chambers for the setting of oil nozzle valve inner, and lower end is set
Atomizer there are two setting；
There are two the intracavitary settings of needle is connected with needle control-rod, the oil nozzle needle for controlling two atomizers respectively.
2. monomer crosspointer valve twin-jet nozzle high pressure common rail injector as described in claim 1, which is characterized in that ball valve ejector rod base
Lower end is provided with ball valve pedestal, the bellmouth that setting matches with high pressure sealing ball valve in ball valve pedestal, high pressure sealing ball valve control
The connection of high pressure fuel processed and low pressure drainback passage；High pressure sealing ball valve body is mostly within high pressure fuel, high pressure
Seal ball-valve contacts to form a seal band with the bellmouth of ball valve pedestal, and high pressure sealing ball valve is pushed away ball valve by ball valve mandril
When pedestal, pressure release effect is generated at seal band.
3. monomer crosspointer valve twin-jet nozzle high pressure common rail injector as claimed in claim 2, which is characterized in that high pressure sealing ball valve
The enlarged diameter section and reduced diameter section of sectional area and ball valve mandril that the seal band formed with the bellmouth of ball valve pedestal is surrounded
Sectional area difference it is equal or suitable.
4. monomer crosspointer valve twin-jet nozzle high pressure common rail injector as described in claim 1, which is characterized in that two groups of two nozzles
Nozzle hole number is respectively 3 to 6, and total orifice number is 9 to 12.
5. monomer crosspointer valve twin-jet nozzle high pressure common rail injector as described in claim 1, which is characterized in that two solenoid valves exist
Mutually staggered in short transverse, and from vertical direction on see in the presence of partly overlapping.
6. monomer crosspointer valve twin-jet nozzle high pressure common rail injector as described in any one in claim 1-5, which is characterized in that utilize
The frictional force that the interference fit of armature compression ring and ball valve mandrel ends generates, solenoid valve armature is fixed on ball valve mandril.
7. monomer crosspointer valve twin-jet nozzle high pressure common rail injector as described in any one in claim 1-5, which is characterized in that magnetic core
The ring that is fixed and clamped is not 360 degree of complete rings, has certain degree notch, is matched using the interference in itself and the hole on magnetic core valve seat
It closes, generates frictional force, Motionless electromagnetic valve magnetic core.
8. monomer crosspointer valve twin-jet nozzle high pressure common rail injector as described in claim 1, which is characterized in that control electromagnetic valve work
When energization, the direction of motion after armature stress is opposite with the resultant direction of high pressure fuel suffered by seal ball-valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201820796050.9U CN208534664U (en) | 2018-05-25 | 2018-05-25 | Medium and heavy-duty engines monomer crosspointer valve twin-jet nozzle high pressure common rail injector |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201820796050.9U CN208534664U (en) | 2018-05-25 | 2018-05-25 | Medium and heavy-duty engines monomer crosspointer valve twin-jet nozzle high pressure common rail injector |
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| Publication Number | Publication Date |
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| CN208534664U true CN208534664U (en) | 2019-02-22 |
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| CN201820796050.9U Expired - Fee Related CN208534664U (en) | 2018-05-25 | 2018-05-25 | Medium and heavy-duty engines monomer crosspointer valve twin-jet nozzle high pressure common rail injector |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108443040A (en) * | 2018-05-25 | 2018-08-24 | 李玉龙 | Medium and heavy-duty engines monomer crosspointer valve twin-jet nozzle high pressure common rail injector |
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2018
- 2018-05-25 CN CN201820796050.9U patent/CN208534664U/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108443040A (en) * | 2018-05-25 | 2018-08-24 | 李玉龙 | Medium and heavy-duty engines monomer crosspointer valve twin-jet nozzle high pressure common rail injector |
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| CF01 | Termination of patent right due to non-payment of annual fee |