CN104533679B - A kind of injector control valve and use the high pressure common rail fuel injection system of this injector control valve - Google Patents
A kind of injector control valve and use the high pressure common rail fuel injection system of this injector control valve Download PDFInfo
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- CN104533679B CN104533679B CN201410840430.4A CN201410840430A CN104533679B CN 104533679 B CN104533679 B CN 104533679B CN 201410840430 A CN201410840430 A CN 201410840430A CN 104533679 B CN104533679 B CN 104533679B
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Abstract
The present invention discloses a kind of injector control valve and uses the high pressure common rail fuel injection system of this injector control valve.Its injector control valve is made up of with relief valve parts valve body, Electromagnetic Control valve member.Change beginning of injection by the energising initial point of regulation magnet exciting coil and regulation its of length changes distributive value conduction time.The circulation area of its Electromagnetic Control valve member is more than the circulation area of relief valve, and makes relief valve parts unlatching pressure be slightly larger than injection pressure of injector, the injection characteristics of urgency after first delaying with acquisition, raising oil spout response speed.Its relief valve parts make fuel injector also be simultaneously in draining state latter stage in oil spout, make fuel injector oil-break rapider.The control spool of relief valve parts uses fuel pressure self-balancing form structure, can reduce the driving electric current of magnet exciting coil, improves the service life of magnetic valve.The high pressure common rail fuel injection system of the present invention uses injector control valve can realize beginning of injection, distributive value Flexible Control with the mode of positive injector combination.
Description
Technical field
The present invention relates to a kind of injector control valve that can control beginning of injection and distributive value, and use this
The high pressure common rail fuel injection system of injector control valve.
Background technology
Fuel oil at diesel engine supplies in system, and traditional mechanical type fuel injection system is owing to controlling certainly
By degree little, control accuracy is low, it is difficult to ensure that each fuel injection parameters is carried out according to corresponding engine operating condition
Excellent control.And common rail system changes the composition structure of traditional mechanical type injection pump system, its injection pressure
Generation be totally independent of rotating speed and the course of injection of engine, real achieve injection pressure, oil spout is begun
The independence of point, distributive value and multi-injection and Flexible Control, be greatly improved the dynamic property of diesel engine, economy
Combination property in terms of property, discharge and noise.Common rail system, meets state three, state four as Diesel engine
Or the optimal selection of more maximum discharge standard, the most extensively, should send out including road vehicle in each engine art
Group of motors, boats and ships, engineering machinery etc..
Common rail system is mainly by high-pressure fuel-feed pump, common rail chamber and high-pressure oil pipe, fuel injector, controller, all kinds of
Sensor and wire harness composition.Oil transfer pump delivers fuel to the oil input channel of high-pressure fuel-feed pump from fuel tank, by starting
The high-pressure fuel-feed pump that machine drives will be sent in common rail chamber after fuel pressurization, then is controlled each cylinder injector by magnetic valve
In corresponding moment oil spout.
Electric-controlled fuel injector is most critical and the most complicated parts in joint-track type fuel system.Its effect is: according to
The control signal that engine controller sends, by control electric-controlled fuel injector open and close, high pressure fuel with
Optimal injection timing, distributive value and injection rate spray into burning chamber of diesel engine.A series of in order to be able to realize this
Complex process, the design of fuel injector, process and the links such as use is the most particularly significant: pre-in order to realize
Fixed fuel injection characteristic, need to reasonably optimize design to fuel injector.The size of the volume of control room determines
Sensitivity when needle-valve opens and closes.The discharge characteristic of oil return metering-orifice and oil-feed metering-orifice and uniformity and control
The face area of piston determines injector valve and opens stability, the shortest injection process and stable minimum oil spout
Amount；The realization of these functions is required for the part of very high manufacturing accuracy.Due to electric-controlled fuel injector key components and parts
Difficulty of processing big, product percent of pass is low；It is extremely strict to oil product, product cleannes and use environmental requirement,
And maintenance cost is high.These high requests constrain the promotion and application of common rail system to a certain extent.
Summary of the invention
One of the technical problem to be solved is intended to the solenoid electric valve in electric-controlled fuel injector and oil spout
Mouth separates, a kind of injector control valve of design.
One of the technical problem to be solved is to be integrated in common rail system by described injector control valve,
Form a kind of novel Electrocontrolled high-pressure common rail fuel injection system.
The technical problem to be solved can be achieved through the following technical solutions:
Injector control valve, including:
Valve body, is provided with Electromagnetic Control valve member installation cavity on the top of described valve body, and both sides, middle part set respectively
Being equipped with common rail chamber interface and fuel injector interface, bottom is configured with relief valve parts installation cavity and oil return pipe interface；
Relief valve oil input channel, gate gurgle valve back oil road, oil back chamber, total back oil road, electromagnetism it is configured with in described valve body
Valve oil input channel, magnetic valve oil road；One end of described magnetic valve oil input channel and described common rail chamber orifice,
The other end of magnetic valve oil input channel connects with described Electromagnetic Control valve member installation cavity；The one of described total back oil road
End and described oil return pipe orifice, the other end of total back oil road connects with described oil back chamber；Described relief valve
One end of oil road connects with described oil back chamber, and the other end of relief valve oil road is pacified with described relief valve parts
It behave affectedly connection；One end of described relief valve oil input channel connects with described relief valve parts installation cavity, and relief valve enters
The other end of oil duct connects with described magnetic valve oil road, one end of described magnetic valve oil road and described oil spout
Device orifice, the other end connects with described Electromagnetic Control valve member installation cavity；
One is arranged on the gate gurgle valve parts in described relief valve parts installation cavity, during described gate gurgle valve component working,
To close with open-minded between described relief valve oil input channel and described relief valve oil road；
One is arranged on the Electromagnetic Control valve member in described Electromagnetic Control valve member installation cavity, described Electromagnetic Control
During valve member work, will close with open-minded between described magnetic valve oil input channel and magnetic valve oil road；
The circulation area of described relief valve parts is less than the circulation area of electromagnetic valve components.
In a preferred embodiment of the invention, described Electromagnetic Control valve member includes electromagnet, excitation wire
Circle, armature, locking swivel nut, control spool, valve pocket and valve seat；Described locking swivel nut and described Electromagnetic Control
Female thread portion in valve member installation cavity is threaded is arranged on described Electromagnetic Control by described valve pocket and valve seat
In valve member installation cavity, seal at the bottom of the bottom surface of described valve seat and the chamber of described Electromagnetic Control valve member installation cavity and connect
Touch, described valve pocket between the bottom surface and the end face of described valve seat of described locking screw seat, the bottom surface of valve pocket with
The end face of described valve seat is in sealing contact；
Magnetic valve fuel feed hole, magnetic valve oil outlet and valve base center hole it is configured with, described in described valve seat
The apical margin of valve base center hole is provided with inferior pyramidal sealing ring surface, the lower end of described magnetic valve fuel feed hole and described valve
The other end connection of internal magnetic valve oil input channel, the upper end of magnetic valve fuel feed hole is with described valve base center hole even
Logical；The lower end of described magnetic valve oil outlet connects with the described magnetic valve oil road in described valve body；Described valve
The bottom of seat centre bore connects with the oil back chamber in described valve body；
In the center of described valve pocket is configured with coaxial magnetic valve cushion block installation cavity, valve pocket the most successively
Central hole and center gap bridge oil pocket, described center gap bridge oil pocket connects with the upper end of described magnetic valve oil outlet；
Configure coaxial have necking down hole and magnetic valve spring the most successively to hold at the center of described locking swivel nut
Dress hole；
The periphery of described control spool is from top to bottom disposed with spring load section, valve pocket seal section,
Axial location limits section and valve base sealing section, is provided with an external diameter on described valve base sealing section top less than described
Axial location limits the external diameter of section and the annular groove of the external diameter of described valve base sealing section, at described annular groove
The transition position limiting section with described axial location is configured with a upper conical sealing ring surface；At described control spool
After spring load section set solenoid spring and magnetic valve cushion block, whole control spool is inserted into described locking
The necking down hole of swivel nut and magnetic valve spring take up hole, the valve pocket centre bore of described valve pocket, the valve seat of described valve seat
In centre bore, wherein said magnetic valve spring is positioned at the magnetic valve spring of described locking swivel nut and takes up hole,
The end face that the upper end of described magnetic valve spring takes up hole with described magnetic valve spring contacts, under magnetic valve spring
End contacts with described magnetic valve cushion block end face, the bottom surface of described magnetic valve cushion block and the top of described valve pocket seal section
Face contacts, and described magnetic valve cushion block is limited in the magnetic valve cushion block installation cavity of described valve pocket；In described control
When upper conical sealing ring surface on spool processed is in sealing contact with the inferior pyramidal sealing ring surface in described valve seat, described
The annular groove controlled on spool is positioned at described valve base center hole the magnetic valve fuel feed hole with described valve seat
Connection, the upper conical sealing ring surface on described control spool divides with the inferior pyramidal sealing ring surface in described valve seat
When opening, the magnetic valve fuel feed hole in described valve seat and center are passed a bridge oily by the annular groove on described control spool
Chamber connects, and and then is connected with described magnetic valve oil outlet by center gap bridge oil pocket, avris gap bridge oil pocket；
Described armature is arranged on the upper end of described control spool by securing member and is positioned at the upper of described locking swivel nut
Side；
Described electromagnet is arranged on the top of described valve body by the very tight cap of electromagnetism, and described magnet exciting coil configures
In described electromagnet；Adjustment pad it is configured with between described electromagnet and described valve body, described electromagnet
Leave magnetic valve air gap between bottom surface and described armature end face, adjusted the thickness of pad by regulation, the most adjustable
The size of economize on electricity magnet valve air gap.
In a preferred embodiment of the invention, it is configured with avris gap bridge oil pocket in the bottom surface of described valve pocket,
Described avris gap bridge oil pocket upper end with described center gap bridge oil pocket and described magnetic valve oil outlet respectively connects.
In a preferred embodiment of the invention, the internal diameter of described valve pocket centre bore is less than described electromagnetism valve pad
Internal diameter and the internal diameter of center gap bridge oil pocket of block installation cavity but equal to the internal diameter of described valve base center hole；Institute simultaneously
State the internal diameter internal diameter more than described valve base center hole of center gap bridge oil pocket.
In a preferred embodiment of the invention, necking down hole and the magnetic valve spring of described locking swivel nut takes up
Hole and the magnetic valve cushion block installation cavity of described valve pocket, valve pocket centre bore, center gap bridge oil pocket and described valve seat
Interior valve base center hole is coaxial；
In a preferred embodiment of the invention, described control spool is tubular structure.
In a preferred embodiment of the invention, the external diameter of described spring load section is less than described valve base sealing
The external diameter of section, described axial location limits the external diameter of section and is more than the external diameter of described valve pocket seal section and described valve seat
The external diameter of seal section.
In a preferred embodiment of the invention, shape between described valve pocket seal section and described valve pocket centre bore
Become closely spaced first couple secondary, formed closely spaced between described valve base sealing section and described valve base center hole
Second couple is secondary, the seal length that length sum is high pressure fuel that the first couple is secondary and the second couple is secondary.
In a preferred embodiment of the invention, the very tight cap of described electromagnetism uses engagement thread and described valve body
Connect, between the very tight cap of described electromagnetism and described valve body, be configured with sealing ring.
In a preferred embodiment of the invention, described relief valve parts include pressure releasing valve core, pressure release valve seat,
Relief valve cushion block, relief valve spring, adjustment pad, pressure relief valve body, have a pressure release in described pressure relief valve body
Valve spring installing hole, in this pressure relief valve body is arranged on described relief valve parts installation cavity and also by described relief valve
Seat is pressed in described relief valve parts installation cavity；Top side configuration at described pressure release valve seat has sealing bulge loop,
Described sealing bulge loop is in sealing contact with the chamber end face of described relief valve parts installation cavity；In described pressure release valve seat
Center by lower and under be disposed with coaxial pressure release oil pocket and pressure releasing valve core location hole, at described relief valve
It is additionally provided with a radial direction oil leak hole in Zuo and from top to bottom configures by draining section on the outer peripheral face of this pressure release valve seat
And positioning section, the outer peripheral face of described positioning section coordinates location with the inner peripheral surface of described relief valve parts installation cavity,
The outer peripheral face of described draining section and the inner peripheral surface of described relief valve parts installation cavity form certain gap and constitute one
Annular drain pan, the outer end of described radial direction oil leak hole connects with described annular drain pan, and radially oil leak hole is interior
End connects with described pressure release oil pocket；Apical margin at described pressure release oil pocket is configured with inferior pyramidal sealing ring surface；
Described pressure releasing valve core is the most successively by seal section, necking segment, pressure release valve seat seal section and relief valve
Cushion block linkage section is constituted；It is provided with and described pressure release oil pocket top in described seal section and necking segment transition junction
The inferior pyramidal sealing ring surface of edge seals the upper conical sealing ring surface coordinated；Described pressure releasing valve core is let out described in being arranged on
After the pressure release oil pocket of pressure valve seat and hole, pressure releasing valve core location, the described seal section in described pressure releasing valve core is positioned at institute
Stating the top of pressure release oil pocket, described necking segment is positioned at described pressure release oil pocket, described pressure release valve seat seal section with
It is secondary that hole, described pressure releasing valve core location complements each other to form closely spaced couple, and described relief valve cushion block linkage section prolongs
Stretch out the bottom surface of described pressure release valve seat and continue and extend in relief valve spring mounting hole；When described pressure releasing valve core
On the inferior pyramidal sealing ring surface of upper conical sealing ring surface and described pressure release oil pocket apical margin when being in sealing contact, described
It is disconnected between gate gurgle valve oil input channel in draining chamber and described valve body, and then by described relief valve oil-feed
Close between road and described relief valve oil road；When the upper conical sealing ring surface on described pressure releasing valve core is with described
When the inferior pyramidal sealing ring surface of pressure release oil pocket apical margin does not contacts, described draining chamber and the gate gurgle valve in described valve body
It is connection between oil input channel, and then will connect between described relief valve oil input channel with described relief valve oil input channel；
Described relief valve cushion block is arranged on described relief valve cushion block linkage section by securing member, described relief valve
The end face of cushion block contacts with the bottom surface of pressure release valve seat seal section；Described relief valve spring and adjustment pad are arranged in
In described relief valve spring mounting hole, the bottom surface of wherein said adjustment pad and described relief valve spring mounting hole
Hole at the bottom of contact, the upper end of described relief valve spring contacts with the bottom surface of described relief valve cushion block, relief valve bullet
The lower end of spring contacts with the end face of described adjustment pad.
In a preferred embodiment of the invention, the internal diameter of described pressure release oil pocket is fixed more than described pressure releasing valve core
The internal diameter in hole, position.
In a preferred embodiment of the invention, the external diameter of described positioning section is more than the external diameter of described draining section.
In a preferred embodiment of the invention, the external diameter of described seal section more than described necking segment external diameter,
The external diameter of described pressure release valve seat seal section and the external diameter of described relief valve cushion block linkage section, described pressure release valve seat is close
The external diameter of envelope section is more than external diameter and the external diameter of described relief valve cushion block linkage section of described necking segment.
A kind of high pressure common rail fuel injection system, including fuel tank, oil transfer pump, high-pressure fuel-feed pump, common rail chamber,
Fuel injector and controller, it is characterised in that also include that aforesaid injector control valve, described controller pass through line
Bundle connects the sensor in described common rail chamber and the magnetic valve in high-pressure fuel-feed pump, the electricity in injector control valve
Magnetic control valve member；Oil-in in described high-pressure fuel-feed pump connects described fuel tank by petroleum pipeline, described defeated
Oil pump is serially connected on described petroleum pipeline, and in described high-pressure fuel-feed pump, oil-out connects described common by high-pressure oil pipe
The high pressure oil-in in rail chamber, the high-pressure oil outlet in described common rail chamber is connected to described oil spout control by high-pressure oil pipe
Common rail chamber interface in valve processed, the oil return pipe interface in described injector control valve is connected to by the first oil return pipe
Second oil return pipe, one end of the second oil return pipe is connected to the oil return opening of described high-pressure fuel-feed pump, the second oil return pipe
The other end be connected to the 3rd oil return pipe, one end of the 3rd oil return pipe is connected to the oil return opening of described fuel injector,
The other end of the 3rd oil return pipe connects described fuel tank.
Owing to have employed technical scheme as above, the common rail system of the present invention is to use injector control valve and tradition
Positive injector combination substitute the function of electric-controlled fuel injector.Common rail system of the present invention to be realized
Function, will not the shortcoming such as, cost high, maintenance difficult big by electric-controlled fuel injector technology difficulty be restricted.
The mode using the combination of injector control valve and positive injector in the present invention can realize beginning of injection,
Distributive value Flexible Control.Use common rail system of the present invention, can be by magnet exciting coil in regulation injector control valve
Energising initial point obtain preferable engine injection timing, by regulate magnet exciting coil length conduction time
Per engine cycle distributive value can be changed.
Injector control valve of the present invention uses Electromagnetic Control valve member and relief valve component combined structure, designs electromagnetism
The circulation area of control valve parts is more than the circulation area of relief valve, and designs relief valve parts unlatching pressure slightly
More than injection pressure of injector, therefore can obtain first slow rear anxious fuel injection characteristic, engine can be significantly improved
Combustion characteristics.And come by the ratio of Reasonable adjustment solenoid electric valve circulation area with relief valve circulation area
Improve oil spout response speed.
Control spool in injector control valve of the present invention uses fuel pressure self-balancing form structure, the most only needs
Less electromagnetic force can make solenoid electric valve open, and can significantly improve oil spout response speed, but also permissible
Reduce the driving electric current of magnet exciting coil, the service life of magnetic valve can be improved.
In injector control valve of the present invention, the relief valve component function of design can make fuel injector go back simultaneously latter stage in oil spout
Be in draining state, therefore this common rail system oil spout latter stage oil-break than standard machinery formula fuel injector oil-break more
Add rapidly.So the common rail system of the application present invention, can obtain being more beneficial for the fuel injection characteristic of engine combustion.
Accompanying drawing explanation
Fig. 1 is injector control valve structural representation of the present invention.
Fig. 2 is the A enlarged diagram of Fig. 1.
Fig. 3 is the A enlarged diagram of Fig. 2.
Fig. 4 is the B enlarged diagram of Fig. 1.
Fig. 5 is the B enlarged diagram of Fig. 4.
Fig. 6 is that high pressure common rail fuel injection system of the present invention forms schematic diagram.
Detailed description of the invention
For the technological means making the present invention realize, creation characteristic, reach purpose and be easy to understand with effect,
Below in conjunction with being specifically illustrating, the present invention is expanded on further.
See Fig. 1 to Fig. 5, the injector control valve be given in figure include valve body 21, Electromagnetic Control valve member and
Relief valve parts.
Be provided with Electromagnetic Control valve member installation cavity 21b on the top of valve body 21, both sides, middle part are respectively arranged with
Common rail chamber interface Y and fuel injector interface M, bottom is configured with relief valve parts installation cavity 21c and oil return pipe interface
N；Relief valve oil input channel 21d, gate gurgle valve back oil road 21a, oil back chamber 21e, total it is configured with in valve body 21
Back oil road 21f, magnetic valve oil input channel 21g, magnetic valve oil road 21h.
Common rail chamber interface Y is designed as inner bolt hole shape, is connected with high-pressure oil pipe 6 (seeing Fig. 6) to facilitate, logical
Cross high-pressure oil pipe 6 to be connected with common rail chamber 5.
Fuel injector interface M is inner bolt hole shape, is connected, by height with high-pressure oil pipe 7 (seeing Fig. 4) to facilitate
Pressuring oil pipe 7 is connected with fuel injector 9.
Oil return pipe interface N is inner bolt hole shape, is connected with oil pipe 10 (seeing Fig. 4) to facilitate, passes through oil pipe
10 with being connected of oil return pipe 4.
One end of magnetic valve oil input channel 21g connects with common rail chamber interface Y, the other end and Electromagnetic Control valve member
Installation cavity 21b connects.
One end of total back oil road 21f connects with oil return pipe interface N, and the other end connects with oil back chamber 21e.
One end of relief valve oil road 21d connects with oil back chamber 21e, the other end and relief valve parts installation cavity
21c connects.
One end of relief valve oil input channel 21a connects with relief valve parts installation cavity 21c, the other end and magnetic valve
Oil road 21h connects.
Magnetic valve oil road 21h one end connects with Electromagnetic Control valve member installation cavity 21b, the other end and oil spout
Device interface M connects.
Electromagnetic Control valve member is arranged in Electromagnetic Control valve member installation cavity 21b, this Electromagnetic Control valve member
During work, will close with open-minded between magnetic valve oil input channel 21g and magnetic valve oil road 21h.
This Electromagnetic Control valve member specifically includes electromagnet 14, magnet exciting coil 15, armature 34, locking swivel nut
36, spool 32, valve pocket 20 and valve seat 31 are controlled；Locking swivel nut 36 and Electromagnetic Control valve member installation cavity 21b
Interior female thread portion is threaded is arranged on Electromagnetic Control valve member installation cavity 21b by valve pocket 20 and valve seat 31
In, the bottom surface of valve seat 31 is in sealing contact at the bottom of the chamber of Electromagnetic Control valve member installation cavity 21b, valve pocket 20
Between the end face of the bottom surface of locking screw seat 33 and valve seat 31, the bottom surface of valve pocket 20 and the end face of valve seat 31
It is in sealing contact.
Magnetic valve fuel feed hole 31a, magnetic valve oil outlet 31b and valve base center hole 31c it is configured with in valve seat 31,
Apical margin at valve base center hole 31c is provided with inferior pyramidal sealing ring surface 31d, the lower end of magnetic valve fuel feed hole 31a
Connect with the other end of the magnetic valve oil input channel 21g in valve body 21, the upper end of magnetic valve fuel feed hole 31a and valve
Seat centre bore 31c connection；The lower end of magnetic valve oil outlet 31b and the magnetic valve oil road 21h in valve body 21
One end connection；The bottom of valve base center hole 31c connects with the oil back chamber 21e in valve body 21.
Coaxial magnetic valve cushion block installation cavity 20a, valve pocket it is configured with the most successively at the center of valve pocket 20
Centre bore 20b and center gap bridge oil pocket 20c, is configured with avris gap bridge oil pocket 20d in the bottom surface of valve pocket 20,
Avris gap bridge oil pocket 20d upper end with center gap bridge oil pocket 20c and magnetic valve oil outlet 31b respectively connects；
The internal diameter of valve pocket centre bore 20b is less than internal diameter and the center gap bridge oil pocket 20c of magnetic valve cushion block installation cavity 20a
Internal diameter but equal to the internal diameter of valve base center hole 31c；The internal diameter of center gap bridge oil pocket 20c is more than valve seat simultaneously
The internal diameter of centre bore 31c.
It is configured with necking down hole 33a the most successively at the center of locking swivel nut 33 and magnetic valve spring takes up hole
33b；The necking down hole 33a of locking swivel nut 33 and magnetic valve spring take up the electromagnetism valve pad of hole 33b and valve pocket 20
Valve seat center in block installation cavity 20a, valve pocket centre bore 20b, center gap bridge oil pocket 20c and valve seat 31
Hole 31c is coaxial.
Controlling spool 32 is tubular structure, is from top to bottom disposed with bullet on the periphery controlling spool 32
Spring carrying section 32a, valve pocket seal section 32b, axial location limit section 32c and valve base sealing section 32d, spring
The external diameter of carrying section 32a is less than the external diameter of valve base sealing section 32b, and the external diameter that axial location limits section 32c is big
External diameter and the external diameter of valve base sealing section 32d in valve pocket seal section 32b.
It is provided with an external diameter on valve base sealing section 32d top and limits external diameter and the valve of section 32c less than axial location
The annular groove 32e of the external diameter of seat seal section 32d, limits section 32c at annular groove 32e with axial location
Transition position is configured with a upper conical sealing ring surface 32f.
After the spring load section set 32a solenoid spring 18 controlling spool 32 and magnetic valve cushion block 19,
Whole control spool 32 is inserted into the locking necking down hole 33a of swivel nut 33 and magnetic valve spring take up hole 33b,
The valve pocket centre bore 20b of valve pocket 20, valve seat 31 valve base center hole 31c in, wherein magnetic valve spring 18
The magnetic valve spring being positioned at locking swivel nut 33 takes up hole 33b, the upper end of magnetic valve spring 18 and magnetic valve
Spring takes up the end face contact of hole 33b, and lower end contacts with magnetic valve cushion block 19 end face, thus can make armature
34 trend being held away from electromagnet 14 and make the upper conical sealing ring surface 32e on control spool 32 and valve seat
Inferior pyramidal sealing ring surface 31d in 31 keeps being in sealing contact state.
The bottom surface of magnetic valve cushion block 19 contacts with the end face of valve pocket seal section 32b, and magnetic valve cushion block 19 is limited
Make in the magnetic valve cushion block installation cavity 20a of valve pocket 20.
Forming closely spaced first couple between valve pocket seal section 32b and valve pocket centre bore 20b secondary, valve seat is close
Forming closely spaced second couple between envelope section 32d and valve base center hole 31c secondary, the first couple is secondary with second
The seal length that length sum is high pressure fuel that couple is secondary.
Inferior pyramidal sealing ring surface 31d in the upper conical sealing ring surface 32e controlled on spool 32 with valve seat 31
When being in sealing contact, control the annular groove 32e on spool 32 be positioned at valve base center hole 32d and with valve seat 32
Interior magnetic valve fuel feed hole 31a connection, in the upper conical sealing ring surface 32e controlled on spool 32 with valve seat
Inferior pyramidal sealing ring surface 31d when separating, control the annular groove 32e on spool 32 by valve seat 31
Magnetic valve fuel feed hole 31a connects with center gap bridge oil pocket 20c, and and then by center gap bridge oil pocket 20c, limit
Side gap bridge oil pocket 20d connects with magnetic valve oil outlet 31b.
Armature 34 is arranged on the upper end controlling spool 32 top being positioned at locking swivel nut 33 by screw 16.
Electromagnet 14 is arranged on the top of valve body 21 by the very tight cap of electromagnetism 36, the very tight cap of electromagnetism 36 with
Valve body 21 is threaded.Magnet exciting coil 15 is arranged in electromagnet 14, and it is by being arranged on electromagnet 14
On a pairs of posts 37 draw, a pairs of posts 37 is by wire harness 13a and the driving electricity in controller 12
Road connects.O RunddichtringO 17, electromagnet 14 and valve body it is configured with between the very tight cap of electromagnetism 36 and valve body 21
It is configured with adjustment pad 35 between 21, between bottom surface and armature 34 end face of electromagnet 14, leaves magnetic valve gas
Gap L1, adjusts the size of magnetic valve air gap L1 by changing adjustment pad 35 gauge.
Control spool 32 and use fuel pressure self-balancing form structure, the most only need less electromagnetic force to overcome electricity
Control spool 32 just can be made to move for the pretightning force of magnet valve spring 18 so that solenoid electric valve is opened, and can significantly carry
High oil spout response speed, but also the size driving electric current can be reduced, Electromagnetic Control valve member can be improved
Service life.Control the upper conical sealing ring surface 32e on spool 32 and the inferior pyramidal sealing ring in valve seat 31
Face 31d keeps the effect being in sealing contact shape morphogenetic sealing surface E to be to block magnetic valve oil input channel 31a and electricity
Magnet valve oil road 31b is connected.When controlling spool 32 and moving to dotted line position, fuel flow communication area K1
Reach maximum.K1 is calculated as follows:
K1=π × (R1+R2) × S1 × sln (θ 1)
In formula:
K1: solenoid electric valve circulation area；
R1: the least radius of solenoid electric valve circulation area；
R2: the maximum radius of solenoid electric valve circulation area；
S1: control the stroke of spool 32；Can change by adjusting the gauge H1 of magnetic valve cushion block 19
Become the size of S1；
θ 1: the cone angle of sealing surface E.
Relief valve parts by pressure releasing valve core 22, pressure release valve seat 23, relief valve cushion block 24, relief valve spring 27,
Adjust pad 29, pressure relief valve body 30 forms.
Having a relief valve spring mounting hole 30a in pressure relief valve body 30, this pressure relief valve body 30 uses engagement thread
It is arranged in relief valve parts installation cavity 21c and also pressure release valve seat 23 is pressed on relief valve parts installation cavity
In 21c.O-ring seals 28 is used to seal between pressure relief valve body 30 and valve body 21.
Top side configuration at pressure release valve seat 23 has sealing bulge loop 23b, seals bulge loop 23b and pacifies with relief valve parts
The chamber end face of 21c of behaveing affectedly is in sealing contact；Center in pressure release valve seat 23 by lower and under be disposed with coaxial
Pressure release oil pocket 23c and pressure releasing valve core location hole 23d, the internal diameter of pressure release oil pocket 23c more than pressure releasing valve core position
The internal diameter of hole 23d.Radial direction oil leak hole 23a it is additionally provided with and at this pressure release valve seat 23 in pressure release valve seat 23
Outer peripheral face on from top to bottom configure by draining section 23e and positioning section 23f, the external diameter of positioning section 23f is more than letting out
The inner peripheral surface of the oil external diameter of section 23e and the outer peripheral face of this positioning section 23f and relief valve parts installation cavity 21c is joined
Close location, the outer peripheral face of draining section 23e and the inner peripheral surface of relief valve parts installation cavity 21c formed certain between
Gap constitutes an annular drain pan 23h.Radially the outer end of oil leak hole 23a connects with annular drain pan 23h, inner
Connecting with pressure release oil pocket 23c, annular drain pan 23h connects with relief valve oil input channel 21d；At pressure release oil pocket
The apical margin of pressure release oil pocket 23c is configured with inferior pyramidal sealing ring surface 23g.
Pressure releasing valve core 22 is the most successively by seal section 22a, necking segment 22b, pressure release valve seat seal section 22c
Constituting with relief valve cushion block linkage section 22d, the external diameter of seal section 22a is more than the external diameter of necking segment 22b, lets out
The external diameter of pressure valve seat seal section 22c and the external diameter of relief valve cushion block linkage section 22d, pressure release valve seat seal section 22c
External diameter more than the external diameter of necking segment 22b and the external diameter of relief valve cushion block linkage section 22d.
It is provided with and the lower cone of pressure release oil pocket 23c apical margin with necking segment 22b transition junction at seal section 22a
V-shaped ring face 23g seals the upper conical sealing ring surface 22e coordinated.
After pressure releasing valve core 22 is arranged on the pressure release oil pocket 23c and pressure releasing valve core location hole 23d of pressure release valve seat 23,
Seal section 22a in pressure releasing valve core 22 is positioned at the top of pressure release oil pocket 23c, and necking segment 22b is positioned at pressure release oil
In the 23c of chamber, pressure release valve seat seal section 22c complements each other to form closely spaced with pressure releasing valve core location hole 23d
Couple is secondary, and the length of fit of this couple pair is the seal section length of fuel oil.
Relief valve cushion block linkage section 22d extends the bottom surface of pressure release valve seat 22 and continues and extend to relief valve spring
In installing hole 30a；When the upper conical sealing ring surface 22e on pressure releasing valve core 22 and pressure release oil pocket 23c apical margin
When inferior pyramidal sealing ring surface 23g is in sealing contact, draining chamber 23c and the gate gurgle valve oil input channel 21a in valve body 21
Between be disconnected, and then will between relief valve oil road 21d and relief valve oil input channel 21a close；When
Upper conical sealing ring surface 22e on the pressure releasing valve core 22 and inferior pyramidal sealing ring surface 23g of pressure release oil pocket 23c apical margin
When not contacting, connect between draining chamber 23c and the gate gurgle valve oil input channel 21a in valve body 21, and then will
Connect between relief valve oil road 21d with relief valve oil input channel 21a；
Relief valve cushion block 24 is arranged on relief valve cushion block linkage section 22d by locking nut 26, spring shim 25
On, the end face of relief valve cushion block 24 contacts with the bottom surface of pressure relief valve body seal section 22d, with locking nut 26,
Relief valve cushion block 24 is axially positioned by spring shim 25 together.
Relief valve spring 27 and adjustment pad 29 are arranged in relief valve spring mounting hole 23a, wherein adjust
The bottom surface of pad 29 contacts at the bottom of the hole of relief valve spring mounting hole 30a.The upper end of relief valve spring 27 with
The bottom surface contact of relief valve cushion block 24, lower end contacts with the end face adjusting pad 29.Relief valve spring 27
Effect is to make relief valve cushion block 24 and pressure releasing valve core 22 keep principle to adjust the mobile trend of pad 29.
Upper conical sealing ring surface 22e on pressure releasing valve core 22 and the inferior pyramidal sealing ring of pressure release oil pocket 23c apical margin
Face 23g is in sealing contact formation sealing surface F, and the effect of sealing surface F is to block relief valve oil input channel 21a and pressure release
Valve oil road 21d is connected.External force suffered by pressure releasing valve core 22 is mainly from relief valve oil input channel 21a's
Fuel pressure and the initial tension of spring of relief valve spring 27；When the fuel oil acting on pressure releasing valve core 22 upper surface
When pressure is more than the initial tension of spring of pressure release spring 27, pressure releasing valve core 22 moves down, relief valve oil input channel 21a
It is not communicated with relief valve oil road 21a；When acting on the fuel pressure of pressure releasing valve core 22 upper surface less than pressure release
During the initial tension of spring of spring 27, pressure releasing valve core 22 moving, oil input channel 21a is fuel-displaced with relief valve for relief valve
Road 21d is connected, and is now the unlatching pressure P2 of relief valve.Can be by changing the thickness adjusting pad 29
Size T2 adjusts the unlatching pressure P2 of relief valve.When pressure releasing valve core 22 moves to dotted line position, fuel oil
Circulation area K2 reaches maximum.K2 is calculated as follows:
K2-π×(R3+R4)×S2×θin(θ2)
In formula:
K2: relief valve circulation area；
R3: the least radius of relief valve circulation area；
R4: the maximum radius of relief valve circulation area；
The stroke of S2: pressure releasing valve core 22；Can change by adjusting the gauge H2 of relief valve cushion block 24
Become the size of S2；
The cone angle of θ 2: pressure releasing valve core 22 sealing surface F；
For realizing the function of injector control valve, the gauge T2 that need to arrange adjustment pad 29 makes relief valve open
Open pressure P2 slightly larger than the unlatching pressure P1 of fuel injector 9, and by adjust S1, S2, R1, R2, R3,
R4, θ 1, the value of θ 2 make K1 be more than K2.
Seeing Fig. 6, a kind of high pressure common rail fuel injection system, including fuel tank 1, oil transfer pump 2, high-pressure oil feed
Pump 3, common rail chamber 5, fuel injector 9 and controller 12, it also includes aforesaid injector control valve 8, controller
The sensor in common rail chamber 5 and the electromagnetism in high-pressure fuel-feed pump 3 is connected by wire harness 13b, 13c, 13a
A pairs of posts 37 (seeing Fig. 1) in Electromagnetic Control valve member in valve, injector control valve 8；High pressure supplies
Oil-in 3a in oil pump 3 connects fuel tank 1 by petroleum pipeline 2a, and oil transfer pump 2 is serially connected on petroleum pipeline 2a,
In high-pressure fuel-feed pump 3, oil-out 3b connects the high pressure oil-in 5a in common rail chamber 5 by high-pressure oil pipe 3c, altogether
The common rail chamber interface Y that high-pressure oil outlet 5b in rail chamber 5 is connected in injector control valve 8 by high-pressure oil pipe 6
(seeing Fig. 1), the oil return pipe interface N in injector control valve 8 is connected to oil return pipe 4 by oil return pipe 10,
One end of oil return pipe 4 is connected to the oil return opening 3d of high-pressure fuel-feed pump 3, and the other end of oil return pipe 4 is connected to back
Oil pipe 11.One end of oil return pipe 11 is connected to the oil return opening of fuel injector 9, and the other end connects fuel tank 1.
Fuel from fuel tank 1 enters common rail chamber 5 through oil transfer pump 2, high-pressure fuel-feed pump 3, then by common rail chamber 5 through spray
Oil control valve 8 is sprayed by fuel injector 9, the combustion that high-pressure fuel-feed pump 3, injector control valve 8, fuel injector 9 are unnecessary
Oil is back in fuel tank 1 by oil return pipe 4,10,11 respectively, and in figure, in each pipeline, the direction of arrow is combustion
The flow direction of oil.
In conjunction with Fig. 1 to Fig. 4, during common rail system of the present invention (seeing Fig. 6) work, the valve of injector control valve 8
It is full of and common rail chamber 5 in magnetic valve oil input channel 21g in body 21, the magnetic valve fuel feed hole 31a in valve seat 31
The high pressure fuel that pressure is equal.When controller 12 sends oil spout instruction, the magnet exciting coil 15 of injector control valve 8
After energising, electromagnet 14 produces electromagnetic force and overcomes the initial tension of spring of magnetic valve spring 18, make armature 34 with
Controlling spool 32 together to move, the sealing surface E controlled between spool 32 and valve seat 31 opens, Electromagnetic Control
Valve oil input channel 21g is connected with magnetic valve oil road 21h, and fuel oil enters spray by magnetic valve oil road 21g
Oil device interface M and relief valve oil input channel 21a.When fuel pressure is less than the unlatching pressure P1 of fuel injector 9,
Fuel oil from magnetic valve oil road 21g only can flow to relief valve oil input channel 21a, due to injector control valve 8
Relief valve parts open pressure P2 slightly larger than the unlatching pressure P1 of fuel injector 9, now the letting out of injector control valve 8
Sealing surface F in pressure valve parts opens, and fuel oil enters relief valve through the sealing surface F that relief valve parts are opened and goes out
Oil duct 21d, is back to fuel tank 1 subsequently into oil return pipe 10,4.Circulation area K2 due to relief valve parts
Less than circulation area K1 of Electromagnetic Control valve member, fuel-displaced hence into relief valve oil input channel 21a, magnetic valve
The fuel oil of the volume space (hereinafter referred to as adapter cavity) that road 21h and fuel injector interface M is constituted is many, fuel-displaced few；
So the fuel pressure in adapter cavity can persistently raise.Pressure P1 is opened when fuel pressure is increased to fuel injector 9
Time, fuel injection beginning.Owing to the oil spout Initial Injection Rate of fuel injector 9 is low, so fuel pressure still can be fast
Speed rises；Simultaneously as pressure release valve opening pressure P2 is slightly larger than the unlatching pressure P1 of fuel injector 9, so fuel oil
Pressure can quickly rise to the unlatching pressure P2 more than relief valve parts, and now pressure releasing valve core 22 moves down, pressure release
Valve member is closed, and sealing surface F Guan Bi blocks relief valve oil input channel 21a and is connected with relief valve oil road 21d,
Adapter cavity pressure rises rapidly, and therefore fuel injector 9 injection rate increases rapidly, so can obtain first slow rear anxious
Fuel injection characteristic, the combustion characteristics of engine can be significantly improved.
When controller 12 sends oil-break instruction, and after magnet exciting coil 15 power-off, electromagnetic force disappears, armature 34 with
Controlling spool 32 to move down under the spring-force driven dual of magnetic valve spring 18, sealing surface E closes, and blocks
High pressure fuel enters adapter cavity from magnetic valve oil input channel 21g.Owing to there is no persistently supplementing of fuel oil, along with spray
The oil spout of oil device 9 is carried out, and the fuel pressure in adapter cavity can be gradually lowered, and opens when fuel oil is reduced to relief valve
When opening pressure P2, pressure releasing valve core 22 moving, adapter cavity is connected with relief valve oil road 21d, and draining is opened
Begin, adapter cavity rapid pressure drop, when transition cavity pressure drops to the unlatching pressure P1 of fuel injector 9, spray
Oil device 9 stops oil spout.Unlatching pressure P2 due to relief valve parts is slightly larger than the unlatching pressure P1 of fuel injector 9,
During so the pressure of adapter cavity is in P2 to P1 scope, while fuel injector 9 oil spout, relief valve parts are also
Being in draining state, therefore fuel injector 9 can be than common tradition mechanical governor high pressure at the oil-break in oil spout latter stage
The fuel injector oil-break of oil pump systems is rapider.So using the common rail system of the present invention, can obtain more favourable
Injection characteristics in engine combustion.
The Diesel engine applying common rail system of the present invention can be by regulating the energising initial point of magnet exciting coil 15
Obtain preferable beginning of injection, engine can be changed by length conduction time of regulation magnet exciting coil 15 every
Circulating fuel injection quantity.
By adjusting the ratio W of electromagnetic valve components circulation area K1 and relief valve parts circulation area K2, permissible
Adjust the oil spout response time of common rail system of the present invention.Analyzing theoretically, ratio W is the biggest, and oil spout responds
The fastest.But, owing to circulation area K2 of relief valve parts is restricted by manufacturing capacity, it is impossible to design
Obtaining the least, electromagnetic valve components stroke S1 is also impossible to be designed to too greatly by the restriction of electromagnet 14 performance,
Therefore ratio W can not be designed to the biggest.So appropriate design solenoid electric valve circulation area K1 and relief valve
The ratio of circulation area K2, can improve oil spout response speed.
Under normal operation, stablizing the fuel pressure in common rail chamber 5 under the closed-loop control of controller 12 is
Certain value.According to the demand of engine operating condition, controller 12 sends oil spout instruction, and injector control valve 8 is energized,
Fuel oil enters fuel injector 9 through injector control valve 8, when fuel pressure opens pressure higher than fuel injector 9, and spray
Oil starts, and the size of distributive value is determined by length conduction time of injector control valve 8.
The general principle of the present invention, principal character and advantages of the present invention have more than been shown and described.The industry
Skilled person will appreciate that, the present invention is not restricted to the described embodiments, in above-described embodiment and specification
The principle that the present invention is simply described described, without departing from the spirit and scope of the present invention, the present invention
Also having various changes and modifications, these changes and improvements both fall within scope of the claimed invention.This
The claimed scope of invention has appending claims and equivalent thereof to define.
Claims (14)
1. injector control valve, it is characterised in that including:
Valve body, is provided with Electromagnetic Control valve member installation cavity on the top of described valve body, and both sides, middle part are respectively
Being provided with common rail chamber interface and fuel injector interface, bottom is configured with relief valve parts installation cavity and oil return pipe connects
Mouthful；Be configured with in described valve body relief valve oil input channel, gate gurgle valve back oil road, oil back chamber, total back oil road,
Magnetic valve oil input channel, magnetic valve oil road；One end of described magnetic valve oil input channel and described common rail chamber interface
Connection, the other end of magnetic valve oil input channel connects with described Electromagnetic Control valve member installation cavity；Described total time
One end of oil duct and described oil return pipe orifice, the other end of total back oil road connects with described oil back chamber；
One end of described relief valve oil road connects with described oil back chamber, and the other end of relief valve oil road is with described
Relief valve parts installation cavity connects；One end of described relief valve oil input channel and described relief valve parts installation cavity
Connection, the other end of relief valve oil input channel connects with described magnetic valve oil road, described magnetic valve oil road
One end and described fuel injector orifice, the other end connects with described Electromagnetic Control valve member installation cavity；
One is arranged on the gate gurgle valve parts in described relief valve parts installation cavity, described gate gurgle valve component working
Time, will close with open-minded between described relief valve oil input channel and described relief valve oil road；
One is arranged on the Electromagnetic Control valve member in described Electromagnetic Control valve member installation cavity, described electromagnetism control
During valve member processed work, will close with open-minded between described magnetic valve oil input channel and magnetic valve oil road；
The circulation area of described relief valve parts is less than the circulation area of electromagnetic valve components.
2. injector control valve as claimed in claim 1, it is characterised in that described Electromagnetic Control valve member
Including electromagnet, magnet exciting coil, armature, locking swivel nut, control spool, valve pocket and valve seat；Described lock
Tight swivel nut threaded described valve pocket with the female thread portion in described Electromagnetic Control valve member installation cavity and
Valve seat is arranged in described Electromagnetic Control valve member installation cavity, the bottom surface of described valve seat and described Electromagnetic Control
Being in sealing contact at the bottom of the chamber of valve member installation cavity, described valve pocket is positioned at the bottom surface of described locking screw seat and described valve
Between the end face of seat, the bottom surface of valve pocket is in sealing contact with the end face of described valve seat；
Magnetic valve fuel feed hole, magnetic valve oil outlet and valve base center hole it is configured with, in institute in described valve seat
The apical margin stating valve base center hole is provided with inferior pyramidal sealing ring surface, the lower end of described magnetic valve fuel feed hole and institute
The other end stating the magnetic valve oil input channel in valve body connects, in the upper end of magnetic valve fuel feed hole and described valve seat
Central hole connects；The lower end of described magnetic valve oil outlet connects with the described magnetic valve oil road in described valve body；
The bottom of described valve base center hole connects with the oil back chamber in described valve body；
Coaxial magnetic valve cushion block installation cavity, valve pocket it is configured with the most successively at the center of described valve pocket
Centre bore and center gap bridge oil pocket, described center gap bridge oil pocket connects with the upper end of described magnetic valve oil outlet；
Configuring the most successively at the center of described locking swivel nut coaxial has necking down hole and magnetic valve spring
Take up hole；
The periphery of described control spool is from top to bottom disposed with spring load section, valve pocket seal section,
Axial location limits section and valve base sealing section, is provided with an external diameter on described valve base sealing section top less than institute
State axial location and limit the external diameter of section and the annular groove of the external diameter of described valve base sealing section, in described annular
The transition position that groove limits section with described axial location is configured with a upper conical sealing ring surface；In described control
After the spring load section set solenoid spring of spool and magnetic valve cushion block, whole control spool is inserted into
The necking down hole of described locking swivel nut and magnetic valve spring take up hole, the valve pocket centre bore of described valve pocket, described
In the valve base center hole of valve seat, wherein said magnetic valve spring is positioned at the magnetic valve bullet of described locking swivel nut
Spring takes up in hole, and the end face that the upper end of described magnetic valve spring takes up hole with described magnetic valve spring contacts,
The lower end of magnetic valve spring contacts with described magnetic valve cushion block end face, the bottom surface of described magnetic valve cushion block and institute
Stating the end face contact of valve pocket seal section, described magnetic valve cushion block is limited in the magnetic valve cushion block of described valve pocket
In installation cavity；Upper conical sealing ring surface on described control spool seals with the inferior pyramidal in described valve seat
Face seal contact time, the annular groove on described control spool be positioned at described valve base center hole and with institute
Stating the magnetic valve fuel feed hole connection in valve seat, the upper conical sealing ring surface on described control spool is with described
When inferior pyramidal sealing ring surface in valve seat separates, the annular groove on described control spool is by described valve seat
Magnetic valve fuel feed hole connect with center gap bridge oil pocket, and and then by center gap bridge oil pocket, avris pass a bridge
Oil pocket connects with described magnetic valve oil outlet；
Described armature is arranged on the upper end of described control spool by securing member and is positioned at described locking swivel nut
Top；
Described electromagnet is arranged on the top of described valve body by the very tight cap of electromagnetism, and described magnet exciting coil is joined
Put in described electromagnet；Adjustment pad, described electromagnetism it is configured with between described electromagnet and described valve body
Leave magnetic valve air gap between bottom surface and the described armature end face of iron, adjusted the thickness of pad by regulation,
Get final product the size of electromagnetic valve for adjusting air gap.
3. injector control valve as claimed in claim 2, it is characterised in that join in the bottom surface of described valve pocket
Be equipped with avris gap bridge oil pocket, described avris gap bridge oil pocket respectively with described center gap bridge oil pocket and described electromagnetism
The upper end connection of valve oil outlet.
4. injector control valve as claimed in claim 2, it is characterised in that described valve pocket centre bore interior
Footpath is less than the internal diameter of described magnetic valve cushion block installation cavity and the internal diameter of center gap bridge oil pocket but equal to described valve seat
The internal diameter of centre bore；The internal diameter of the most described center gap bridge oil pocket is more than the internal diameter of described valve base center hole.
5. injector control valve as claimed in claim 2, it is characterised in that the necking down of described locking swivel nut
Hole and magnetic valve spring take up hole and the magnetic valve cushion block installation cavity of described valve pocket, valve pocket centre bore, center
Valve base center hole in gap bridge oil pocket and described valve seat is coaxial.
6. injector control valve as claimed in claim 2, it is characterised in that described control spool is tubulose
Structure.
7. injector control valve as claimed in claim 2, it is characterised in that outside described spring load section
Footpath is less than the external diameter of described valve base sealing section, and the external diameter that described axial location limits section is close more than described valve pocket
The external diameter of envelope section and the external diameter of described valve base sealing section.
8. injector control valve as claimed in claim 2, it is characterised in that described valve pocket seal section and institute
State and between valve pocket centre bore, form closely spaced first couple pair, in described valve base sealing section and described valve seat
Forming closely spaced second couple between central hole secondary, the length sum that the first couple is secondary and the second couple is secondary is
The seal length of high pressure fuel.
9. injector control valve as claimed in claim 2, it is characterised in that the very tight cap of described electromagnetism uses
Engagement thread is connected with described valve body, is configured with sealing ring between the very tight cap of described electromagnetism and described valve body.
10. injector control valve as claimed in claim 2, it is characterised in that described relief valve parts include
Pressure releasing valve core, pressure release valve seat, relief valve cushion block, relief valve spring, adjustment pad, pressure relief valve body, institute
Having a relief valve spring mounting hole in stating pressure relief valve body, this pressure relief valve body is arranged on described relief valve parts
In installation cavity and also described pressure release valve seat is pressed in described relief valve parts installation cavity；In described pressure release
The top side configuration of valve seat has sealing bulge loop, described sealing bulge loop to push up with the chamber of described relief valve parts installation cavity
Face is in sealing contact；Center in described pressure release valve seat by lower and under be disposed with coaxial pressure release oil pocket
Position hole with pressure releasing valve core, in described pressure release valve seat, be additionally provided with a radial direction oil leak hole and at this relief valve
From top to bottom configuring by draining section and positioning section on the outer peripheral face of seat, the outer peripheral face of described positioning section is with described
The inner peripheral surface of relief valve parts installation cavity coordinates location, the outer peripheral face of described draining section and described relief valve portion
The inner peripheral surface of part installation cavity forms certain gap and constitutes an annular drain pan, outside described radial direction oil leak hole
Holding and connect with described annular drain pan, radially inner the and described pressure release oil pocket of oil leak hole connects；Described
The apical margin of pressure release oil pocket is configured with inferior pyramidal sealing ring surface；
Described pressure releasing valve core is the most successively by seal section, necking segment, pressure release valve seat seal section and pressure release
Valve pad block linkage section is constituted；It is provided with in described seal section and necking segment transition junction and described pressure release oil
The inferior pyramidal sealing ring surface of chamber apical margin seals the upper conical sealing ring surface coordinated；Described pressure releasing valve core is arranged on
After the pressure release oil pocket of described pressure release valve seat and hole, pressure releasing valve core location, the described sealing in described pressure releasing valve core
Section is positioned at the top of described pressure release oil pocket, and described necking segment is positioned at described pressure release oil pocket, described relief valve
It is secondary that seat seal section and hole, described pressure releasing valve core location complement each other to form closely spaced couple, described relief valve
Cushion block linkage section extends the bottom surface of described pressure release valve seat and continues and extend in relief valve spring mounting hole；
Inferior pyramidal sealing ring surface when the upper conical sealing ring surface on described pressure releasing valve core Yu described pressure release oil pocket apical margin
When being in sealing contact, it is disconnected between the gate gurgle valve oil input channel in described draining chamber and described valve body, enters
And will close between described relief valve oil input channel and described relief valve oil road；When on described pressure releasing valve core
When upper conical sealing ring surface does not contacts with the inferior pyramidal sealing ring surface of described pressure release oil pocket apical margin, described draining
Connect between chamber and the gate gurgle valve oil input channel in described valve body, so by described relief valve oil input channel with
Connect between described relief valve oil input channel；
Described relief valve cushion block is arranged on described relief valve cushion block linkage section by securing member, described pressure release
The end face of valve pad block contacts with the bottom surface of pressure release valve seat seal section；Described relief valve spring and adjustment pad are joined
Put in described relief valve spring mounting hole, the bottom surface of wherein said adjustment pad and described relief valve spring
Contacting at the bottom of the hole of installing hole, the upper end of described relief valve spring contacts with the bottom surface of described relief valve cushion block,
The lower end of relief valve spring contacts with the end face of described adjustment pad.
11. injector control valves as claimed in claim 10, it is characterised in that described pressure release oil pocket interior
Footpath is more than the internal diameter in hole, described pressure releasing valve core location.
12. injector control valves as claimed in claim 10, it is characterised in that the external diameter of described positioning section
External diameter more than described draining section.
13. injector control valves as claimed in claim 10, it is characterised in that the external diameter of described seal section
Connect more than the external diameter of described necking segment, the external diameter of described pressure release valve seat seal section and described relief valve cushion block
The external diameter of section, the external diameter of described pressure release valve seat seal section is more than the external diameter of described necking segment and described relief valve
The external diameter of cushion block linkage section.
14. 1 kinds of high pressure common rail fuel injection systems, including fuel tank, oil transfer pump, high-pressure fuel-feed pump, common rail
Chamber, fuel injector and controller, it is characterised in that also include claim 1 to 13 any one claim
Described injector control valve, described controller connects the sensor in described common rail chamber and height by wire harness
Magnetic valve in pressure oil feed pump, the Electromagnetic Control valve member in injector control valve；In described high-pressure fuel-feed pump
Oil-in connect described fuel tank by petroleum pipeline, described oil transfer pump is serially connected on described petroleum pipeline, described
In high-pressure fuel-feed pump, oil-out connects the high pressure oil-in in described common rail chamber, described common rail by high-pressure oil pipe
The common rail chamber interface that the high-pressure oil outlet in chamber is connected in described injector control valve by high-pressure oil pipe, described
Oil return pipe interface in injector control valve is connected to the second oil return pipe, the second oil return pipe by the first oil return pipe
One end be connected to the oil return opening of described high-pressure fuel-feed pump, the other end of the second oil return pipe is connected to the 3rd time
Oil pipe, one end of the 3rd oil return pipe is connected to the oil return opening of described fuel injector, the other end of the 3rd oil return pipe
Connect described fuel tank.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410840430.4A CN104533679B (en) | 2014-12-30 | 2014-12-30 | A kind of injector control valve and use the high pressure common rail fuel injection system of this injector control valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410840430.4A CN104533679B (en) | 2014-12-30 | 2014-12-30 | A kind of injector control valve and use the high pressure common rail fuel injection system of this injector control valve |
Publications (2)
| Publication Number | Publication Date |
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| CN104533679A CN104533679A (en) | 2015-04-22 |
| CN104533679B true CN104533679B (en) | 2016-09-07 |
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| CN201410840430.4A Active CN104533679B (en) | 2014-12-30 | 2014-12-30 | A kind of injector control valve and use the high pressure common rail fuel injection system of this injector control valve |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN106050500B (en) * | 2016-05-31 | 2017-05-24 | 清华大学 | Electronic control high-pressure oil atomizer with improved armature device |
| CN106368874A (en) * | 2016-09-12 | 2017-02-01 | 上海中船三井造船柴油机有限公司 | Oil sprayer of low-speed diesel engine |
| CN114439662B (en) * | 2022-02-22 | 2023-04-18 | 一汽解放汽车有限公司 | Switching valve and common rail system |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10100422A1 (en) * | 2001-01-08 | 2002-07-11 | Bosch Gmbh Robert | Solenoid valve for controlling an injection valve of an internal combustion engine |
| DE102004058803A1 (en) * | 2004-12-07 | 2006-06-08 | Robert Bosch Gmbh | Injector |
| DE102007025614A1 (en) * | 2007-06-01 | 2008-12-04 | Robert Bosch Gmbh | Armature stroke adjustment for solenoid valve |
| DE102008061400A1 (en) * | 2008-12-10 | 2010-06-17 | Man Diesel Se | Fuel injection valve for an internal combustion engine |
| CN204627824U (en) * | 2014-12-30 | 2015-09-09 | 南岳电控(衡阳)工业技术有限公司 | A kind of injector control valve and use the high pressure common rail fuel injection system of this injector control valve |
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