CN108443040A - 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
- Publication number
- CN108443040A CN108443040A CN201810526193.2A CN201810526193A CN108443040A CN 108443040 A CN108443040 A CN 108443040A CN 201810526193 A CN201810526193 A CN 201810526193A CN 108443040 A CN108443040 A CN 108443040A
- Authority
- CN
- China
- Prior art keywords
- valve
- ball valve
- high pressure
- mandril
- needle
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 239000000178 monomer Substances 0.000 title claims abstract description 16
- 239000000446 fuel Substances 0.000 claims abstract description 55
- NJPPVKZQTLUDBO-UHFFFAOYSA-N novaluron Chemical compound C1=C(Cl)C(OC(F)(F)C(OC(F)(F)F)F)=CC=C1NC(=O)NC(=O)C1=C(F)C=CC=C1F NJPPVKZQTLUDBO-UHFFFAOYSA-N 0.000 claims abstract description 31
- 238000007789 sealing Methods 0.000 claims abstract description 30
- 230000000694 effects Effects 0.000 claims abstract description 13
- 238000009434 installation Methods 0.000 claims abstract description 10
- 230000006835 compression Effects 0.000 claims description 7
- 238000007906 compression Methods 0.000 claims description 7
- 230000033001 locomotion Effects 0.000 claims description 3
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 claims 2
- 229910052742 iron Inorganic materials 0.000 claims 1
- 238000002347 injection Methods 0.000 abstract description 38
- 239000007924 injection Substances 0.000 abstract description 38
- 239000007921 spray Substances 0.000 abstract description 11
- 239000002283 diesel fuel Substances 0.000 abstract description 3
- 238000005457 optimization Methods 0.000 abstract description 3
- 230000007423 decrease Effects 0.000 abstract 1
- 239000003921 oil Substances 0.000 description 55
- 235000019198 oils Nutrition 0.000 description 55
- 239000011162 core material Substances 0.000 description 22
- 239000000295 fuel oil Substances 0.000 description 15
- 238000003860 storage Methods 0.000 description 6
- 230000008878 coupling Effects 0.000 description 5
- 238000010168 coupling process Methods 0.000 description 5
- 238000005859 coupling reaction Methods 0.000 description 5
- 238000000889 atomisation Methods 0.000 description 4
- 239000000567 combustion gas Substances 0.000 description 4
- 230000035882 stress Effects 0.000 description 4
- 230000008859 change Effects 0.000 description 3
- MWUXSHHQAYIFBG-UHFFFAOYSA-N nitrogen oxide Inorganic materials O=[N] MWUXSHHQAYIFBG-UHFFFAOYSA-N 0.000 description 3
- 239000000443 aerosol Substances 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000009977 dual effect Effects 0.000 description 2
- 239000002828 fuel tank Substances 0.000 description 2
- 239000007789 gas Substances 0.000 description 2
- 238000003754 machining Methods 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 239000000243 solution Substances 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 229910017052 cobalt Inorganic materials 0.000 description 1
- 239000010941 cobalt Substances 0.000 description 1
- GUTLYIVDDKVIGB-UHFFFAOYSA-N cobalt atom Chemical compound [Co] GUTLYIVDDKVIGB-UHFFFAOYSA-N 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 230000001934 delay Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 230000006353 environmental stress Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000004907 flux Effects 0.000 description 1
- 239000002737 fuel gas Substances 0.000 description 1
- 230000006870 function Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 230000014759 maintenance of location Effects 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 239000003595 mist Substances 0.000 description 1
- 230000008450 motivation Effects 0.000 description 1
- 235000019488 nut oil Nutrition 0.000 description 1
- 239000010466 nut oil Substances 0.000 description 1
- 238000012856 packing Methods 0.000 description 1
- 230000000505 pernicious effect Effects 0.000 description 1
- 239000010970 precious metal Substances 0.000 description 1
- 230000000284 resting effect Effects 0.000 description 1
- 238000012163 sequencing technique Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
- F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
-
- 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
- F02M51/00—Fuel-injection apparatus characterised by being operated electrically
- F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
- F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means
-
- 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
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
- F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
- F02M61/1893—Details of valve member ends not covered by groups F02M61/1866 - F02M61/188
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Fuel-Injection Apparatus (AREA)
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 settings of needle intracavitary is connected with needle control-rod, the oil nozzle needle for controlling two atomizers respectively.In addition, ball valve mandril further decreases required electromagnetic force with high pressure sealing ball valve split settings by the way that ball valve mandril is designed as enlarged diameter section and reduced diameter section.The function of the high pressure common rail injector more adapts to the characteristics of diesel spray diesel oil relative to conventional fuel injector, under conditions of not improving fuel system pressure, can further improve the atomizing effect of high-pressure diesel injection, improve engine original machine emission level；Advantageous optimization injection rate rule simultaneously, it is horizontal further to excavate diesel powered.
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 technology
For the fuel economy for improving diesel engine and the discharge capacity for improving the original pernicious gas of engine, and optimization diesel oil
Machine noise and vibration need the effect for improving air and 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 carry high injection pressure to enhance fuel atomization effect, for example, from before compared with
It is even higher it to be increased to 1800bar, 2200bar for universal 1600bar；And utilize the pre- of multiple minimum oil mass (0.5~1mg)
Injection makes injection rate to realize that the rate of heat release being intended under ideal conditions first delays rear anxious jeting effect；Even same
Identical pressure carries out the injection of front portion period with high pressure oil rail for secondary course of injection mid-early stage use, in the latter portion of oil spout
Relying on the fluid power enlarger inside oil injector body to further increase at times, oil injector body is interior 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, the side such as material selection, accessory size, technique can be caused
In face of the higher requirement of processing and manufacturing aspect.In addition in current diesel injector only there are one atomizer when, due to one
The spray orifice aperture of a atomizer and nozzle hole number first have to meet the injection rate requirement needed for normal fuel delivery, it is therefore desirable to
Certain enough fuel oils spray sectional area；But the 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 fully opening not yet, thus the pilot injection of minimum oil mass be all often
Far below being carried out under the mouth end injection pressure of system fuel pressure, 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 are 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 pattern；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 makes gas nozzle chamber come full of the big pressurized fuel gas of pressure ratio valve opening pressure to open intake valve
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, fuel injector of the fuel injector relative to the existing application of traditional scheme
It can so that fuel injection mode is more flexible, steadily obtain the smaller small oil mass injection of quality, can not greatly improve
Realized in the case of oily rail pressure power closer to needed for diesel engine ideal burning injection rate control and good air and fuel oil
Mixed aerosol effect.
Invention content
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 design one kind having good high pressure (meeting or exceeding 1600 bars) fuel sealing function
New-type seal ball-valve control mechanism, design a kind of compact only there are one oil injector body but have two components on this basis
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 floor installation nut, ball valve ejector rod base, needle control-rod pedestal, oil nozzle installation nut and oil nozzle valve body；It is characterized in that：
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 endoporus cylindrical surface precision-fit of reduced diameter section and ball valve ejector rod base, greatly
Diameter segment and ball valve mandril seal sleeve endoporus 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 settings of needle intracavitary 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, is arranged 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 larger initial tension of spring is not needed to be compressed 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 number of degrees 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, total orifice number can than traditional scheme only there are one oil nozzle when it is more, in single injection diameter phase
When or it is smaller in the case of can but obtain 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 of institute of identical fuel oil
Oil injection duration is needed to lengthen, to make pilot injection be carried out in the case of higher mouth end pressure, pilot injection atomization quality is more preferable, from
And help to improve the particulate emissions level of engine original machine.
Description of the drawings
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 vertical view of twin-jet nozzle.
Fig. 4 is the sectional view of twin-jet nozzle.
Fig. 1 part names：
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 implementation mode
As shown in Figure 1, the monomer crosspointer valve twin-jet nozzle high pressure common rail injector of the present invention includes magnetic core valve seat 3, ball valve top
Bar floor installation nut 12, ball valve ejector rod base 13, ball valve pedestal 16, needle control-rod pedestal 18,20 and of oil nozzle installation 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 number of degrees 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 is carried out to high pressure sealing ball valve
The bellmouth of limit, 53 mesohigh of annulus control noticeable degree oil groove that high pressure sealing ball valve 17 is formed with bellmouth taper-face contact
The break-make 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 in post rod hydraulic pressure balancing channel 51 declines, 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 change, i.e. ball valve mandril exists
There is enlarged diameter section and reduced diameter section, a diameter of R1 of reduced diameter section, a diameter of R2 of enlarged diameter section in ball valve tip-lever support.It is small straight
The endoporus 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 endoporus cylindrical surface precision-fit forms high pressure sealing.14 lower face 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 one ball valve mandrils of individual part respectively
Pedestal 13 and ball valve mandril seal sleeve 14 are conducive to after Finishing Parts Machining so that the clearance fit of two sections of seal requests is 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 seal ball-valve with Internal Spherical Surface shape in specific processing
It touches.Either 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, needle control low-pressure tank 53, high pressure oil storages 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 is used to control the oil nozzle needle 23 of two atomizers respectively there are two being connected with needle control-rod 19.
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, and part needle control-rod bottom is still in by dead 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 ensure 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, each group of electromagnetic valve coil corresponds to 2 stitch, totally 4
Stitch.
Fuel injector course of work explanation：
After engine start rotates, 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 maintain actual internal area between low pressure drainback passage 52 and fuel tank
Larger 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 taper 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 stage casing of ball valve mandril, and lower end
In the low-pressure state of low pressure drainback passage 52, ball valve mandril 15 is more 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 the lower section of valve armature 1, 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 of needle control-rod, 54,53 etc. pressure and the comparable high pressure conditions of system rail pressure, hydraulic pressure
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 suffered hydraulic pressure area and the relationship of hydraulic coupling size, oil nozzle needle 23 are 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 stage casing diameter difference it is downward
With joint efforts>Upwards with joint efforts, seal ball-valve 17 will be in ball for both 11 pretightning forces of armature preloading spring+seal ball-valve, 17 hydraulic compression power
The down thrust effect of 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 hydraulic pressure
Balance channel 51 is communicated with low pressure drainback passage 52.The mobile upper end limited by seal ball-valve pedestal 16 directed downwardly of ball valve mandril 15
Face provides.Needle controls low-pressure tank 53 and the fuel pressure in ball valve post rod hydraulic pressure balancing channel 51 will settle to and low pressure oil return
52 comparable low voltage level of channel, fuel oil return to fuel tank.High pressure oil storage tank 54 is kept and the comparable high pressure water of external system rail pressure
It is flat.
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 is lifted, injection hole on injection nozzle upwards upwards suffered by final atomizer needle 23
High pressure fuel injection will be generated at 59.
The monomer crosspointer valve twin-jet nozzle high pressure common rail injector oil nozzle valve body outer diameter of the present invention, can be than one group of spray of traditional scheme
7.2 millimeters of the oil nozzle valve diameter in hole increases to 12.5 to 13.5 millimeters or so, is 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 than transmission scheme smaller, it is possible to reduce to 15 public affairs
Point or so, installation such as oil injector body top and top parts such as camshaft etc. can be reduced in certain applications
Interference so that the layout of parts is freer above engine cylinder cover.
The present invention is to reduce solenoid valve power and being controlled to seal ball-valve using seal ball-valve control-rod 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
Floor installation nut, ball valve ejector rod base, needle control-rod pedestal, oil nozzle installation nut and oil nozzle valve body；
It is characterized in that：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 endoporus 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 endoporus 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 settings of needle intracavitary 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, and the bellmouth to match with high pressure sealing ball valve, high pressure sealing ball valve control is arranged in ball valve pedestal
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 for the 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. the monomer crosspointer valve twin-jet nozzle high pressure common rail injector as described in claim 1-5, which is characterized in that utilize armature pressure
The frictional force that the interference fit of tight ring and ball valve mandrel ends generates, solenoid valve armature is fixed on ball valve mandril.
7. the monomer crosspointer valve twin-jet nozzle high pressure common rail injector as described in claim 1-6, which is characterized in that magnetic core fixes pressure
Tight ring is not 360 degree of complete rings, has certain number of degrees notch, using the interference fit of itself and the hole on magnetic core valve seat, is generated
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 and high pressure fuel suffered by the sealing valve of seal ball-valve or other number of other, non-spherical shapes
Resultant direction is opposite.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810526193.2A CN108443040A (en) | 2018-05-25 | 2018-05-25 | Medium and heavy-duty engines monomer crosspointer valve twin-jet nozzle high pressure common rail injector |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810526193.2A CN108443040A (en) | 2018-05-25 | 2018-05-25 | Medium and heavy-duty engines monomer crosspointer valve twin-jet nozzle high pressure common rail injector |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN108443040A true CN108443040A (en) | 2018-08-24 |
Family
ID=63204764
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810526193.2A Pending CN108443040A (en) | 2018-05-25 | 2018-05-25 | Medium and heavy-duty engines monomer crosspointer valve twin-jet nozzle high pressure common rail injector |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN108443040A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111594108A (en) * | 2020-07-08 | 2020-08-28 | 江苏普盛石化机械有限公司 | Succinct formula glib talker device of adjusting soon |
| CN112796916A (en) * | 2021-03-08 | 2021-05-14 | 上海钧风电控科技有限公司 | Valve rod assembly and high-pressure fuel injection valve |
Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10008554A1 (en) * | 2000-02-24 | 2001-08-30 | Bosch Gmbh Robert | Fuel injection valve for internal combustion engines |
| CN102220924A (en) * | 2010-04-15 | 2011-10-19 | 曼柴油机欧洲股份公司曼柴油机德国分公司 | A fuel valve for large stroke diesel engines |
| CN103670851A (en) * | 2013-11-28 | 2014-03-26 | 上海交通大学 | Oil injector which is provided with double high-pressure oil pipes and is applicable to dimethyl ether fuel |
| CN104500297A (en) * | 2014-11-28 | 2015-04-08 | 重庆红江机械有限责任公司 | Energy-saving high-pressure common-rail electronic-control oil injector |
| CN105464865A (en) * | 2016-01-13 | 2016-04-06 | 吉林大学 | Diesel fuel injector with double fuel injection nozzles |
| CN105756821A (en) * | 2016-04-21 | 2016-07-13 | 哈尔滨工程大学 | Combined non-pressurized fuel oil and pressurized fuel gas dual piezoelectric mixed fuel injection device |
| CN205478036U (en) * | 2016-01-13 | 2016-08-17 | 吉林大学 | Two fuel sprayer sprayers of diesel engine |
| CN106762286A (en) * | 2017-01-18 | 2017-05-31 | 哈尔滨工程大学 | A kind of On Fluctuations oil return bypass type electric-controlled fuel injector with hydraulic feedback |
| CN208534664U (en) * | 2018-05-25 | 2019-02-22 | 李玉龙 | Medium and heavy-duty engines monomer crosspointer valve twin-jet nozzle high pressure common rail injector |
-
2018
- 2018-05-25 CN CN201810526193.2A patent/CN108443040A/en active Pending
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10008554A1 (en) * | 2000-02-24 | 2001-08-30 | Bosch Gmbh Robert | Fuel injection valve for internal combustion engines |
| CN102220924A (en) * | 2010-04-15 | 2011-10-19 | 曼柴油机欧洲股份公司曼柴油机德国分公司 | A fuel valve for large stroke diesel engines |
| CN103670851A (en) * | 2013-11-28 | 2014-03-26 | 上海交通大学 | Oil injector which is provided with double high-pressure oil pipes and is applicable to dimethyl ether fuel |
| CN104500297A (en) * | 2014-11-28 | 2015-04-08 | 重庆红江机械有限责任公司 | Energy-saving high-pressure common-rail electronic-control oil injector |
| CN105464865A (en) * | 2016-01-13 | 2016-04-06 | 吉林大学 | Diesel fuel injector with double fuel injection nozzles |
| CN205478036U (en) * | 2016-01-13 | 2016-08-17 | 吉林大学 | Two fuel sprayer sprayers of diesel engine |
| CN105756821A (en) * | 2016-04-21 | 2016-07-13 | 哈尔滨工程大学 | Combined non-pressurized fuel oil and pressurized fuel gas dual piezoelectric mixed fuel injection device |
| CN106762286A (en) * | 2017-01-18 | 2017-05-31 | 哈尔滨工程大学 | A kind of On Fluctuations oil return bypass type electric-controlled fuel injector with hydraulic feedback |
| CN208534664U (en) * | 2018-05-25 | 2019-02-22 | 李玉龙 | Medium and heavy-duty engines monomer crosspointer valve twin-jet nozzle high pressure common rail injector |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111594108A (en) * | 2020-07-08 | 2020-08-28 | 江苏普盛石化机械有限公司 | Succinct formula glib talker device of adjusting soon |
| CN111594108B (en) * | 2020-07-08 | 2024-06-11 | 江苏普盛石化机械有限公司 | Succinct regulation glib device that revolves |
| CN112796916A (en) * | 2021-03-08 | 2021-05-14 | 上海钧风电控科技有限公司 | Valve rod assembly and high-pressure fuel injection valve |
| CN112796916B (en) * | 2021-03-08 | 2024-03-19 | 钧风电控科技(泰州)有限责任公司 | Valve rod assembly and high-pressure fuel injection valve |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN101680413B (en) | Control valve for a fuel injection valve | |
| CN101535625B (en) | Injector for injecting fuel | |
| CN105756824B (en) | Combined type piezoelectric fuel injection is pressurized electromagnetism jet hybrid fuel jet device | |
| CN115387943B (en) | Multi-injection mode electric control fuel injector suitable for high-power diesel engine | |
| CN115387944B (en) | Low oil return variable needle valve opening speed electric control oil sprayer | |
| CN111336048A (en) | Fuel injector for realizing diesel/natural gas dual-fuel injection | |
| CN105626316A (en) | Combined type pressurizing double-electromagnetic-valve gas injection device | |
| CN108443040A (en) | Medium and heavy-duty engines monomer crosspointer valve twin-jet nozzle high pressure common rail injector | |
| CN208534664U (en) | Medium and heavy-duty engines monomer crosspointer valve twin-jet nozzle high pressure common rail injector | |
| CN105756811B (en) | Combined type piezoelectricity and supercharging electromagnetism fuel gas ejecting device | |
| CN114151250A (en) | Diesel oil pressurization-liquid ammonia direct injection dual-fuel injector | |
| CN105756830B (en) | Combined mechanical oil spout-supercharging electromagnetism jet hybrid fuel jet device | |
| CN101395365A (en) | Fuel injector having recessed check top | |
| GB2367330A (en) | Common-rail fuel injector | |
| CN103925136A (en) | Fuel injector with solenoid valve mounted on side | |
| CN105756821A (en) | Combined non-pressurized fuel oil and pressurized fuel gas dual piezoelectric mixed fuel injection device | |
| CN105351115A (en) | Non-leakage piezoelectric control gas injection device | |
| CN105756829B (en) | Combined mechanical oil spout is pressurized piezoelectricity jet hybrid fuel jet device | |
| CN105756825B (en) | Combined electromagnetic oil spout is pressurized piezoelectricity jet hybrid fuel jet device | |
| CN109184987A (en) | The variable pressure accumulation type heavy oil electric-controlled fuel injector of fuel injection characteristic | |
| CN105822477B (en) | A kind of no static leakage transformation cavate low inertia component of oil sprayer and fuel injector | |
| CN104358645A (en) | Electromagnetic assisted heating type GDI (Gasoline Direct Injector) tar injection device | |
| JP2001207935A (en) | Fuel injection device assembly having improved solenoid operating type check valve | |
| CN105257362A (en) | Common rail type air cylinder oil injection lubricating system | |
| CN105781797B (en) | Electromagnetism and piezoelectricity combination gas gas spraying device |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination |