CN114165370B - Two-position three-way control valve of high-pressure common-rail oil injector - Google Patents
Two-position three-way control valve of high-pressure common-rail oil injector Download PDFInfo
- Publication number
- CN114165370B CN114165370B CN202111409735.6A CN202111409735A CN114165370B CN 114165370 B CN114165370 B CN 114165370B CN 202111409735 A CN202111409735 A CN 202111409735A CN 114165370 B CN114165370 B CN 114165370B
- Authority
- CN
- China
- Prior art keywords
- hole
- oil
- valve
- new control
- groove
- 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.)
- Active
Links
Images
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
- F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
- F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
- F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/0012—Valves
- F02M63/0014—Valves characterised by the valve actuating means
- F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
- F02M63/0017—Valves characterised by the valve actuating means electrical, e.g. using solenoid 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
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/0012—Valves
- F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
- F02M63/0045—Three-way valves
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)
- Fluid Mechanics (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
The invention relates to a two-position three-way control valve of a high-pressure common rail oil sprayer, wherein the high-pressure common rail oil sprayer comprises an electromagnet, an oil storage chamber, a control chamber and a low-pressure oil area, and the two-position three-way control valve comprises a new control rod, a valve seat and a new control sleeve; the valve seat is hollow, and a new control rod is inserted into the hollow hole of the valve seat; the outer circle surface of the upper part of the new control rod is attached to the hole wall surface of the upper part of the hollow hole of the valve seat to form sealing; the lower end surface of the valve seat is attached to the upper end surface of the new control sleeve to form sealing; a groove is arranged on the new control rod, an oil groove is arranged on the valve seat, and a central oil drainage hole is arranged on the new control sleeve; the groove is communicated with the oil storage chamber, the oil groove is communicated with the control chamber, and the central oil drainage hole is communicated with the low-pressure oil area; the electromagnet is switched on and off to electrically drive the new control rod to move at an upper sealing position and a lower sealing position, so that the communication of fuel oil in three areas of the groove, the oil groove and the central oil drainage hole is formed, and the novel control rod is a two-position three-way valve. The invention reduces the requirement on electromagnetic force, improves the opening and closing response of the needle valve and reduces the oil return quantity of the oil injector.
Description
Technical Field
The invention belongs to the field of fuel injection systems of internal combustion engines, and particularly relates to a two-position three-way control valve of a pressure balance valve of a high-pressure common rail fuel injector.
Background
The prior high-pressure common rail oil sprayer adopts a two-position two-way control valve, such as a ball valve, as shown in figure 1, and consists of a high-speed electromagnet 1, a control rod 2, a steel ball 3, a control sleeve 4, a long valve rod 5, an oil sprayer body 6, an oil sprayer matching part 7, a compression nut 9, an armature 11 and other parts. The clamping nut 9 presses the control sleeve 4 against a shoulder 61 of the injector body 6.
High-pressure fuel enters from a high-pressure fuel inlet hole 62 on the fuel injector body 6, passes through an oil inlet passage 63 upwards, enters the high-pressure oil storage chamber 8, and reaches the control chamber 45 through the fuel inlet throttle hole 14. The high pressure fuel entering the fuel inlet channel 63 flows down to the oil groove 71 of the fuel injection nozzle matching part 7 and then gathers at the conical surface 72 of the fuel injection nozzle.
When the electromagnet 1 is powered off, the electromagnet return spring 13 tightly presses the control rod 2 and the steel ball 3 on the conical surface of the control sleeve 4 to seal an oil leakage path of the oil outlet throttle hole 15, so that high-pressure fuel oil entering the control chamber 45 from the oil inlet throttle hole 14 stays in the control chamber 45, the pressure of the high-pressure fuel oil presses the conical surfaces of the long valve rod 5 and the oil injector needle valve on the conical surface of the oil injection nozzle valve seat, the oil path of the high-pressure fuel oil leading to the oil injection hole 73 is cut off, and the oil injection nozzle does not inject oil.
When the electromagnet 1 is electrified, the electromagnet 1 attracts the armature 11, so that the control rod 2 ascends, the steel ball 3 is separated from the conical surface on the control sleeve 4, and high-pressure fuel in the control chamber 45 flows to a low-pressure area outside the steel ball 3 through the fuel outlet orifice 15 and returns to the oil tank through the oil return channel 64. Since the orifice 15 is slightly larger in diameter than the intake orifice 14, the fuel pressure in the control chamber 45 decreases because more high-pressure fuel flows out from the control chamber 45 through the outlet orifice 15 than high-pressure fuel flows in from the reservoir chamber 8 through the intake orifice 14. When the resultant force of the hydraulic pressure of the fuel acting on the long valve rod 5 and the return spring is lower than the upward hydraulic pressure of the high-pressure fuel acting on the long valve rod 5 in the oil containing groove 71 of the fuel injection nozzle, the long valve rod 5 rises, the conical surface of the needle valve of the fuel injection nozzle is separated from the conical surface of the valve seat, and the high-pressure fuel passes through the fuel injection hole 73 from the gap between the two conical surfaces and is injected into a combustion chamber of the diesel engine.
The electromagnet 1 is continuously switched off and on, and the above process is repeated. Because the high-pressure fuel oil flows to the low-pressure area from the oil outlet throttling hole 15 all the time when the fuel is supplied, the pressure of the high-pressure fuel oil is up to 160-250 MPa, and the pressure of the low-pressure fuel oil is less than 0.1MPa. Therefore, in the prior common rail oil sprayer, the fuel oil at the oil drainage hole of the control valve is continuously discharged to a low-pressure fuel oil area to form return oil in the injection process, so that the high-pressure potential energy converted from mechanical energy is lost; on the other hand, the loss of potential energy from high pressure fuel leaking into the low pressure region generates a large amount of heat energy, which raises the temperature of the fuel in the injector and the injector body above 100 degrees. Further, as is known from the bernoulli principle, the pressure at the orifice decreases and the flow velocity increases, but when the pressure of the fuel at the orifice where it contacts the solid surface is lower than its vapor pressure, bubbles are formed near the solid surface, and the gas dissolved in the fuel may be separated out to form bubbles. Then, when the bubbles flow to a place where the fuel pressure exceeds the bubble pressure, the bubbles collapse, and a great impact force and a high temperature are generated at the moment of collapse. The solid surface is subjected to repeated action of the impact force for many times, and the material is subjected to fatigue and falls off to form cavitation to cause fatigue failure, so that the service life of the fuel injector is shortened. Meanwhile, the hole diameters of the oil inlet throttling hole and the oil outlet throttling hole are small, and a certain time is needed for pressure difference formation, so that the opening and closing speed of the needle valve is reduced, and the oil injection rate is influenced.
Disclosure of Invention
In order to solve the problems in the prior art, the invention provides a two-position three-way control valve of a high-pressure common-rail oil injector. Because the common rail oil atomizer in the prior art is usually provided with the two-position two-way valve, and high-pressure fuel oil always flows from the oil outlet throttle hole to the low-pressure area during oil supply, so that energy loss is caused.
In order to achieve the purpose, the invention adopts the following scheme:
the high-pressure common rail oil sprayer two-position three-way control valve comprises an electromagnet, an oil storage chamber, a control chamber and a low-pressure oil area, and comprises a new control rod, a valve seat and a new control sleeve; the valve seat is hollow, and a new control rod is inserted into the hollow hole of the valve seat; the outer circle surface of the upper part of the new control rod is mutually attached to the hole wall surface of the upper part of the hollow hole of the valve seat to form sealing; the lower end surface of the valve seat is mutually attached to the upper end surface of the new control sleeve to form sealing;
a groove is arranged on the rod wall of the upper part of the new control rod and is positioned below the outer circular surface; an oil groove is formed in the valve seat, and a notch of the oil groove is coplanar with the lower end face of the valve seat; the groove is positioned above the oil groove, the groove is communicated with the oil storage chamber, and the oil groove is communicated with the control chamber; a central oil drainage hole is formed in the new control sleeve and communicated with the low-pressure oil area;
the rod wall of the lower part of the new control rod is provided with a conical surface a, the hole wall of the lower part of the hollow hole of the valve seat is provided with a conical surface b, the conical surface a and the conical surface b are matched with each other to form a conical valve, and the conical valve is a two-way valve and is positioned on an oil path for communicating the groove and the oil groove; after assembly, a new control rod 16 is checked, the conical surface a and the conical surface b are attached when the new control rod moves upwards, and the distance from the lower end face of the new control rod to the lower end face of the valve seat is H, namely the working stroke of the electromagnet;
the lower end face of the new control rod and the upper end face of the new control sleeve are matched with each other to form a plane valve, and the plane valve is a two-way valve and is positioned on an oil way for communicating the oil groove with the central oil drainage hole; the sealing surface of the plane valve is round;
when the electromagnet is powered off, the cone valve is opened, and the plane valve is closed; when the electromagnet is electrified, the cone valve is closed, and the plane valve is opened; the electromagnet is switched on and off to electrically drive the new control rod to move at an upper sealing position and a lower sealing position, so that the communication of fuel oil in three areas of a groove, an oil groove and a central oil drainage hole is formed, and the three areas are two-position three-way valves;
the diameter A1 of the outer circular surface of the upper part of the new control rod, the diameter B of the sealing surface of the planar valve and the diameter A of the hole wall surface of the upper part of the hollow hole of the valve seat are equal, so that when the valve works, the pressures of liquid acting on the new control rod in the vertical direction are balanced, and the resultant force is zero.
As a preferred technical scheme:
in the two-position three-way control valve of the high-pressure common rail injector, the conical angle D of the conical surface b of the valve seat is 0.5-10 degrees larger than the conical angle D1 of the conical surface a of the new control rod.
According to the two-position three-way control valve of the high-pressure common-rail oil sprayer, the new control rod comprises a cylinder I, a cylinder II, a circular truncated cone I, a cylinder III and a reverse circular truncated cone which are coaxial and sequentially connected from top to bottom; the diameter of the cylinder II is smaller than the diameter A1 of the cylinder I; the small end of the circular truncated cone I is arranged at the upper part and the large end of the circular truncated cone I is arranged at the lower part, the diameter of the small end is larger than that of the cylinder II, and the diameter of the large end is equal to that of the cylinder III; the large end of the inverted round table is arranged at the upper part and the small end is arranged at the lower part, and the diameter of the large end is equal to that of the cylinder III;
the outer circular surface of the upper part of the new control rod is the circumferential surface of the cylinder I; the groove is defined by the lower bottom surface of the cylinder I, the side surface of the cylinder II and the small end surface of the circular truncated cone I; the conical surface a of the new control rod is the side surface of the circular truncated cone I.
The diameter A2 of the cylinder III of the two-position three-way control valve of the high-pressure common rail oil sprayer is 0.5-1 mm larger than the diameter A1.
According to the two-position three-way control valve of the high-pressure common rail oil sprayer, the whole formed by the cylinder III and the inverted round table is provided with the hollow round table coaxial with the cylinder III, the small end of the hollow round table is arranged above the upper large end of the hollow round table, and the diameter of the large end of the hollow round table is equal to that of the inverted round table; the diameter B of an edge line (as a sealing line a contacted with the upper end surface of the new control sleeve) of the large end of the hollow circular truncated cone is equal to A1 (the angle of an included angle between the side surface of the hollow circular truncated cone and the side surface of the inverted circular truncated cone can be increased); in order to improve the sealing performance and the reliability of the sealing edge, the taper angle C1 of the side surface of the inverted circular truncated cone is 10-30 degrees, and the taper angle C2 of the side surface of the hollow circular truncated cone is 5-15 degrees; the lower end face of the new control rod is the large end face of the hollow circular truncated cone.
According to the two-position three-way control valve of the high-pressure common rail oil sprayer, the hollow hole of the valve seat comprises the cylindrical hole a, the circular table hole, the cylindrical hole b and the cylindrical hole c which are coaxial and sequentially arranged from top to bottom; the small end of the circular table hole is arranged above the cylindrical hole a, and the large end of the circular table hole is arranged below the cylindrical hole a; the diameter of the cylindrical hole b is smaller than that of the cylindrical hole c; the diameter of the cylindrical hole c is larger than A2;
the hole wall surface of the upper part of the hollow hole of the valve seat is the hole wall surface of the cylindrical hole a; the central axis of the cylindrical hole a is vertical to the lower end surface (high-precision sealing plane) of the valve seat; the conical surface b of the valve seat is the hole wall of the circular truncated cone hole; the diameter of a sealing line b formed after the conical surface b of the valve seat is contacted with the conical surface a of the new control rod is equal to A1; and the wall of the oil groove is the wall of the cylindrical hole c.
According to the two-position three-way control valve of the high-pressure common rail oil injector, the valve seat is provided with the inclined oil inlet hole, and the upper end of the inclined oil inlet hole is connected with the groove.
The new control sleeve is of a T-shaped structure and consists of a cylinder IV (the cylinder can be a standard cylinder or a nonstandard cylinder) and a cylinder V (the cylinder can be a standard cylinder or a nonstandard cylinder) which are coaxially and sequentially arranged from top to bottom, and the diameter of the cylinder IV is larger than that of the cylinder V;
the central axis of the cylinder IV is vertical to the upper end surface (high-precision sealing plane) of the new control sleeve; the cylinder IV is provided with a ring groove, an oil inlet hole, a central oil drainage hole and a transverse oil drainage hole; the central axis of the central oil drainage hole is superposed with the central axis of the cylinder IV, the upper end of the central oil drainage hole is open, and the lower end of the central oil drainage hole is closed; the central oil drainage hole is coaxial with the hollow circular truncated cone, and the diameter of the central oil drainage hole is smaller than A1, so that the central oil drainage hole and the oil groove can be sealed by the planar valve; the central axis of the oil inlet is parallel to the central axis of the cylinder IV, the two ends of the oil inlet are open, the upper end of the oil inlet is connected with the ring groove, and the lower end of the oil inlet is connected with the oil storage chamber; the ring groove surrounds the central oil drainage hole; the lower end of the inclined oil inlet is connected with the annular groove; the central axis of the transverse oil drainage hole is vertical to the central axis of the cylinder IV, the two ends of the transverse oil drainage hole are open, one end of the transverse oil drainage hole is connected with the central oil drainage hole, and the other end of the transverse oil drainage hole is connected with the low-pressure oil area;
the control chamber is positioned in the cylinder V, an inner hole is arranged below the control chamber, and the cylinder V, the control chamber and the inner hole are coaxial; the inner hole is used for installing the long valve rod;
the new control sleeve is provided with an inclined hole, two ends of the inclined hole are opened, the lower end of the inclined hole is connected with the control chamber, the upper end of the inclined hole is connected with the oil groove, and the distance between the end and the central shaft of the new control sleeve is more than half of A1, so that the inclined hole cannot be sealed by the planar valve;
the oil passage for communicating the oil storage chamber with the control chamber is formed by sequentially connecting an oil inlet hole, a ring groove, an inclined oil inlet hole, a groove, a cylindrical hole c and an inclined hole;
the oil passage for communicating the control chamber with the low-pressure oil area is formed by sequentially connecting an inclined hole, a cylindrical hole c, a central oil drainage hole and a transverse oil drainage hole.
According to the two-position three-way control valve of the high-pressure common rail oil sprayer, the new control rod is provided with the clamping ring groove for placing the clamping ring, the armature is sleeved on the clamping ring when the two-position three-way control valve is used, and the new control rod can move up and down through the clamping ring when the electromagnet sucks the armature; the air gap between the armature and the electromagnet can be adjusted by adjusting the thickness of an air gap adjusting gasket to reach a required value.
Has the advantages that:
(1) Because the sealing diameter A1 of the new control rod is 3-5 times larger than the oil outlet section of the steel ball in the prior art, the working stroke of the electromagnet can be reduced to 0.02-0.03 mm (the working stroke of the steel ball in the prior art is 0.05 mm), thereby improving the ascending and descending speed of the new control rod, improving the oil supply rate of an oil nozzle and improving the combustion of a diesel engine;
(2) Because the new control rod plays a role of a hydraulic pressure balance valve during working, the return spring of the electromagnet can adopt very small force, so that the requirement of electromagnetic force can be reduced, and the opening and closing response of the needle valve is improved;
(3) Because the communication between the high-pressure fuel oil and the low-pressure oil duct is cut off in the oil injection state, the dynamic oil return amount can be reduced, the temperature rise of the oil injector is reduced, and the reliability is improved.
Drawings
FIG. 1 is a high pressure common rail injector including a two-position, two-way control valve according to the prior art;
FIG. 2 is a block diagram of the two-position, three-way control valve of the present invention;
FIG. 3 is a structural diagram of a new control rod of the two-position three-way control valve of the high pressure common rail injector of the present invention;
FIG. 4 is a structural diagram of a valve seat of a two-position three-way control valve of the high-pressure common rail oil sprayer;
FIG. 5 is a structural diagram of a new control sleeve of the two-position three-way control valve of the high pressure common rail injector according to the present invention;
FIG. 6 is a part position diagram of the two-position three-way control valve of the high-pressure common rail oil injector when the electromagnet is powered off;
FIG. 7 is a part position diagram of the two-position three-way control valve of the high-pressure common rail oil injector when the electromagnet is electrified;
wherein, 1-high speed electromagnet, 2-control rod, 3-steel ball, 4-control sleeve, 5-long valve rod, 6-injector body, 7-injector matching part, 8-oil storage chamber, 9-gland nut, 10-air gap adjusting shim, 11-armature, 12-snap ring, 13-electromagnet return spring, 14-oil inlet orifice, 15-oil outlet orifice, 16-new control rod, 17-valve seat, 18-new control sleeve, 45-control chamber, 61-shoulder, 62-high pressure oil inlet hole, 63-oil inlet channel, 64-oil return channel, 71-oil containing groove, 72-injector cone, 73-oil injection hole, 161-outer cone, 162-groove, 163-cone a, 164-side of hollow circular truncated cone, 165-side of inverted circular truncated cone, 166-edge line of large end of hollow circular truncated cone, 167-lower end of new control rod, 168-snap ring groove, 172-oblique oil inlet hole, 173-lower end of valve seat, 174-cone, 175-sealing line, 176-182-177-oil discharge hole, 183-central hole, 183-oil discharge hole, 183-transverse hole, 183-150-transverse hole, and 183-transverse hole.
Detailed Description
The invention will be further illustrated with reference to specific embodiments. It should be understood that these examples are for illustrative purposes only and are not intended to limit the scope of the present invention. Further, it should be understood that various changes or modifications of the present invention can be made by those skilled in the art after reading the teaching of the present invention, and these equivalents also fall within the scope of the claims appended to the present application.
As shown in fig. 2, the high-pressure common rail injector includes an electromagnet, an oil storage chamber 8, a control chamber 45, and a low-pressure oil region;
the two-position three-way control valve of the high-pressure common rail injector is shown in FIG. 2 and comprises a new control rod 16, a valve seat 17 and a new control sleeve 18;
the complete structure of the new control rod 16 is shown in fig. 3, and the new control rod 16 comprises a cylinder I, a cylinder II, a circular truncated cone I, a cylinder III and an inverted circular truncated cone which are coaxial and sequentially connected from top to bottom; the diameter of the cylinder II is smaller than the diameter A1 of the cylinder I; the small end of the circular truncated cone I is arranged at the upper part and the large end is arranged at the lower part, the diameter of the small end is larger than that of the cylinder II, the diameter of the large end is equal to the diameter A2 of the cylinder III, and the diameter A2 is 0.5-1 mm larger than that of A1; the large end of the inverted round table is arranged at the upper part and the small end is arranged at the lower part, and the diameter of the large end is equal to that of the cylinder III; the whole formed by the cylinder III and the inverted round table is provided with a hollow round table coaxial with the cylinder III, the small end of the hollow round table is arranged above the upper end and the large end of the hollow round table is arranged below the lower end, and the diameter of the large end is equal to that of the small end of the inverted round table; the diameter B of the edge line 166 of the large end of the hollow circular truncated cone is equal to A1; the taper angle C1 of the side 165 of the truncated cone is 10 to 30 degrees, and the taper angle C2 of the side 164 of the hollow truncated cone is 5 to 15 degrees; the lower end surface 167 of the new control rod is a large end surface of the hollow round table;
the complete structure of the valve seat 17 is shown in fig. 4, the interior of the valve seat 17 is hollow and is a hollow hole 176, the hollow hole 176 of the valve seat 17 comprises a cylindrical hole a, a circular truncated cone hole, a cylindrical hole b and a cylindrical hole c which are coaxial and sequentially arranged from top to bottom, and the central axis of the cylindrical hole a is perpendicular to the lower end surface 173 of the valve seat; the small end of the circular table hole is arranged above the cylindrical hole a, and the large end of the circular table hole is arranged below the cylindrical hole a; the diameter of the cylindrical hole b is smaller than that of the cylindrical hole c;
the complete structure of the new control sleeve 18 is shown in fig. 5, the new control sleeve 18 is a T-shaped structure and is composed of a cylinder IV and a cylinder V which are coaxially and sequentially arranged from top to bottom, the diameter of the cylinder IV is larger than that of the cylinder V, and the area of the lower surface of the cylinder IV, which is connected with the cylinder V, is a shoulder surface 186; the central axis of the cylinder IV is vertical to the upper end surface 181 of the new control sleeve 18; the cylinder IV is provided with a ring groove 182 (namely an annular groove), an oil inlet hole 183, a central oil drainage hole 188 and a transverse oil drainage hole 187; the central axis of the central oil drainage hole 188 is superposed with the central axis of the cylinder IV, the upper end of the central oil drainage hole is open, and the lower end of the central oil drainage hole is closed; the central oil drainage hole 188 is coaxial with the hollow circular truncated cone, and the diameter of the central oil drainage hole 188 is smaller than A1; the central axis of the oil inlet 183 is parallel to the central axis of the cylinder IV, the two ends of the oil inlet are open, the upper end of the oil inlet is connected with the annular groove 182, and the lower end of the oil inlet is connected with the oil storage chamber 8; an annular groove 182 surrounds the central drain hole 188; the central axis of the transverse oil drainage hole 187 is vertical to the central axis of the cylinder IV, the two ends of the transverse oil drainage hole are open, one end of the transverse oil drainage hole is connected with the central oil drainage hole 188, and the other end of the transverse oil drainage hole is connected with the low-pressure oil area;
the control chamber 45 is positioned in the cylinder V, an inner hole 189 is arranged below the control chamber 45, and the cylinder V, the control chamber 45 and the inner hole 189 are coaxial; the inner hole 189 is a hole for mounting the long stem 5;
the new control rod 16 is inserted into the hollow bore 176 of the valve seat 17; the peripheral surface of the cylinder I of the new control rod 16 is an external circular surface 161, and is mutually attached to the hole wall surface of the cylindrical hole a in the hollow hole 176 of the valve seat 17 to form sealing; the lower end surface 173 of the valve seat is mutually attached to the upper end surface 181 of the new control sleeve 18 to form a seal;
the new control rod 16 is provided with a groove 162, the groove 162 is surrounded by the lower bottom surface of the cylinder I, the side surface of the cylinder II and the small end surface of the circular truncated cone I, and the groove 162 is positioned below the outer circular surface 161; an oil groove 177 and an inclined oil inlet 172 are arranged on the valve seat 17, the wall of the oil groove 177 is the wall of the cylindrical hole c, and the notch of the oil groove 177 is coplanar with the lower end surface 173 of the valve seat; the new control sleeve 18 is provided with an inclined hole 184, and two ends of the inclined hole 184 are opened; the groove 162 is positioned above the oil groove 177, the upper end of the inclined oil inlet 172 is connected with the groove 162, and the lower end of the inclined oil inlet 172 is connected with the annular groove 182; the lower end of the inclined hole 184 is connected with the control chamber 45, the upper end is connected with the oil groove 177, and the distance between the upper end and the central shaft of the new control sleeve 18 is more than half of A1;
the new control rod 16 is provided with a conical surface a 163, and the conical surface a 163 is the side surface of the circular truncated cone I; the hollow hole 176 of the valve seat 17 is provided with a conical surface b 174, and the conical surface b 174 is the hole wall of a circular table hole in the hollow hole 176; the taper angle D of the taper surface b 174 of the valve seat 17 is 0.5-10 degrees larger than the taper angle D1 of the taper surface a 163 of the new control rod 16, the taper surfaces a 163 and b 174 are mutually matched to form a taper valve, the taper valve is a two-way valve, and the diameter of a sealing line b formed after the taper surface b 174 of the valve seat 17 is contacted with the taper surface a 163 of the new control rod 16 is equal to A1; the cone valve is positioned on an oil path for communicating the groove 162 with the oil groove 177;
the lower end surface 167 of the new control rod and the upper end surface 181 of the new control sleeve 18 are mutually matched to form a plane valve, and the plane valve is a two-way valve and is positioned on an oil path for communicating the oil groove 177 and the central oil drainage hole 188; the sealing surface of the plane valve is round;
a snap ring groove 168 for placing a snap ring is processed on the new control rod 16, when the novel control rod is used, the armature 11 is sleeved on the snap ring, the armature 11 is attracted by the electromagnet, the new control rod 16 can move up and down through the snap ring, an air gap between the armature 11 and the high-speed electromagnet 1 can be adjusted, and the thickness of an air gap adjusting gasket 10 can be optionally adjusted to reach a required value; when the electromagnet is powered off, the cone valve is opened, and the plane valve is closed; when the electromagnet is electrified, the cone valve is closed, and the plane valve is opened; the electromagnet is switched on and off to drive the new control rod 16 to move at two sealing positions, so that the communication of fuel oil in three areas, namely the groove 162, the oil groove 177 and the central oil drainage hole 188 is formed, and the two-position three-way valve is formed;
the diameter A1 of the outer circular surface 161 of the upper portion of the new control rod 16, the diameter B of the sealing surface of the flat valve, and the diameter a of the hole wall surface of the cylindrical hole a of the hollow hole 176 of the valve seat 17 are equal, so that in operation, the pressures of the liquid acting on the new control rod 16 in the up-down direction are balanced, and the resultant force is zero.
The working principle of the method is further explained in conjunction with fig. 6 and 7.
FIG. 6 is a diagram of the positions of the components of the two-position three-way control valve of the high-pressure common rail injector when the electromagnet is powered off, at this time, the new control rod 16 is pressed on the upper end surface 181 of the new control sleeve 18 by the electromagnet return spring 13, the edge line 166 of the large end of the hollow circular truncated cone on the lower end surface 167 of the new control rod is attached to the upper end surface 181 of the new control sleeve 18, the high-pressure fuel enters the oil storage chamber 8 from the high-pressure fuel inlet hole 62 through the oil inlet channel 63, and then sequentially passes through the oil inlet hole 183 and the annular groove 182 on the new control sleeve 18, the oblique oil inlet hole 172 on the valve seat 17, and enters the groove 162 on the new control rod 16, because the lower end surface 167 of the new control rod is pressed on the upper end surface 181 of the new control sleeve 18, the conical surface a 163 on the new control rod 16 is separated from the conical surface b 174 on the valve seat 17, and the high-pressure fuel in the groove 162 enters the oil groove 177 on the valve seat 17 from the gap between the conical surface a 163 and the conical surface b 174;
because the diameter B of the edge line 166 of the large end of the hollow circular truncated cone on the lower end surface 167 of the new control rod is equal to the diameter A1 of the outer circular surface 161 on the new control rod 16, and the resultant force of hydraulic pressure acting on the new control rod 16 is zero, the high-pressure fuel is sealed in the oil groove 177, meanwhile, the high-pressure fuel in the oil groove 177 enters the control chamber 45 through the inclined hole 184 on the new control sleeve 18, the pressure of the high-pressure fuel presses the long valve rod 5 and the oil nozzle needle valve on the conical surface of the oil nozzle valve seat, the high-pressure fuel is gathered at the oil nozzle conical surface 72 and cannot reach the oil injection hole 73, and the oil nozzle does not inject oil at the moment.
Fig. 7 is a part position diagram of the two-position three-way control valve of the high-pressure common rail injector when the electromagnet is powered on, at this time, the attraction force of the electromagnet overcomes the pressure of the electromagnet return spring 13 acting on the armature 11 to move upwards, the new control rod 16 moves upwards, the conical surface a 163 on the new control rod 16 presses on the conical surface b 174 on the valve seat 17, the high-pressure fuel entering from the inclined fuel inlet 172 on the valve seat 17 is sealed in the groove 162, at this time, because the diameter A1 of the outer circular surface 161 of the new control rod 16 is equal to the diameter of the sealing line b 175, the resultant force of the hydraulic pressure acting on the new control rod 16 is zero, the new control rod 16 seals the high-pressure fuel in the groove 162 under the action of the electromagnetic force, at this time, the lower end face 167 of the new control rod leaves the upper end face 181 of the new control sleeve 18, a gap is formed between the edge line 166 of the large end of the hollow circular truncated cone and the upper end face 181 of the new control sleeve 18, the seal is released, so that the high-pressure fuel in the control chamber 45 enters the oil groove 177 through the inclined hole 184, then the fuel breaks through an annular gap formed between the edge line 166 of the large end of the hollow circular truncated cone and the upper end face 181, flows into a low-pressure oil area through the central oil drain hole 188 and the transverse oil drain hole 187, the pressure of the oil in the control chamber 45 is reduced, the high-pressure fuel in the oil nozzle oil containing groove 71 moves the long valve rod 5 upwards, the conical surface of the oil nozzle needle valve leaves the conical surface of the oil nozzle valve seat, and the high-pressure fuel is sprayed into the combustion chamber through the oil nozzle oil spray hole 73.
The above processes are repeated to ensure that the diesel engine works normally.
The invention relates to a high pressure common rail pressure balance two-position three-way control valve, which comprises a new control rod 16, a valve seat 17 and a new control sleeve 18, wherein the new control rod, the valve seat 17 and the new control sleeve are tightly pressed on a shoulder 61 of an oil injector body 6 by a compression nut 9, other parts adopt the original oil injector parts, the leakage can be reduced, the response capability is improved, and meanwhile, the original production equipment can be utilized to rapidly put into mass production.
Claims (9)
1. The high-pressure common rail oil sprayer two-position three-way control valve is characterized by comprising a new control rod (16), a valve seat (17) and a new control sleeve (18); the valve seat (17) is hollow, and a new control rod (16) is inserted into a hollow hole (176) of the valve seat (17); the outer circular surface (161) of the upper part of the new control rod (16) is mutually attached to the hole wall surface of the upper part of the hollow hole (176) of the valve seat (17) to form sealing; the lower end surface (173) of the valve seat (17) is mutually attached with the upper end surface (181) of the new control sleeve (18) to form sealing;
a groove (162) is arranged on the rod wall of the upper part of the new control rod (16), and the groove (162) is positioned below the outer circular surface (161); an oil groove (177) is formed in the valve seat (17), and a notch of the oil groove (177) is coplanar with the lower end face (173) of the valve seat (17); the groove (162) is positioned above the oil groove (177), the groove (162) is communicated with the oil storage chamber (8), and the oil groove (177) is communicated with the control chamber (45); a central oil drainage hole (188) is formed in the new control sleeve (18), and the central oil drainage hole (188) is communicated with the low-pressure oil area;
a conical surface a (163) is arranged on the rod wall of the lower part of the new control rod (16), a conical surface b (174) is arranged on the hole wall of the lower part of a hollow hole (176) of the valve seat (17), the conical surface a (163) and the conical surface b (174) are matched with each other to form a conical valve, and the conical valve is a two-way valve and is positioned on an oil path for communicating the groove (162) and the oil groove (177);
the lower end face (167) of the new control rod (16) is matched with the upper end face (181) of the new control sleeve (18) to form a plane valve, the plane valve is a two-way valve and is positioned on an oil path for communicating the oil groove (177) with the central oil drainage hole (188); the sealing surface of the plane valve is round;
when the electromagnet is powered off, the cone valve is opened, and the plane valve is closed; when the electromagnet is electrified, the cone valve is closed, and the plane valve is opened; the electromagnet is switched on and off to electrically drive the new control rod (16) to move at an upper sealing position and a lower sealing position, so that the communication of fuel oil in three areas, namely a groove (162), an oil groove (177) and a central oil drainage hole (188), is formed, and is a two-position three-way valve;
the diameter A1 of the outer circular surface (161) of the upper part of the new control rod (16), the diameter B of the sealing surface of the planar valve and the diameter A of the hole wall surface of the upper part of the hollow hole (176) of the valve seat (17) are equal, so that in operation, the pressures of liquid acting on the new control rod (16) in the up-and-down direction are balanced, and the resultant force is zero;
the new control rod (16) comprises a cylinder I, a cylinder II, a circular truncated cone I, a cylinder III and a reversed circular truncated cone which are coaxial and sequentially connected from top to bottom; the diameter of the cylinder II is smaller than the diameter A1 of the cylinder I; the small end of the circular truncated cone I is arranged at the upper part and the large end of the circular truncated cone I is arranged at the lower part, the diameter of the small end is larger than that of the cylinder II, and the diameter of the large end is equal to that of the cylinder III; the large end of the inverted round table is arranged at the upper part and the small end is arranged at the lower part, and the diameter of the large end is equal to that of the cylinder III;
the new control sleeve (18) is of a T-shaped structure and is composed of a cylinder IV and a cylinder V which are coaxial and sequentially arranged from top to bottom, and the diameter of the cylinder IV is larger than that of the cylinder V;
the central axis of the cylinder IV is vertical to the upper end surface (181) of the new control sleeve (18); the cylinder IV is provided with a ring groove (182), an oil inlet hole (183), a central oil drainage hole (188) and a transverse oil drainage hole (187); the central axis of the central oil drainage hole (188) is superposed with the central axis of the cylinder IV, the upper end of the central oil drainage hole is open, and the lower end of the central oil drainage hole is closed; the central oil drainage hole (188) is coaxial with the hollow circular truncated cone, and the diameter of the central oil drainage hole (188) is smaller than A1; the central axis of the oil inlet hole (183) is parallel to the central axis of the cylinder IV, the two ends of the oil inlet hole are opened, the upper end of the oil inlet hole is connected with the ring groove (182), and the lower end of the oil inlet hole is connected with the oil storage chamber (8); an annular groove (182) surrounds the central drain hole (188); the lower end of the inclined oil inlet hole (172) is connected with the annular groove (182); the central axis of the transverse oil drainage hole (187) is vertical to the central axis of the cylinder IV, the two ends of the transverse oil drainage hole are open, one end of the transverse oil drainage hole is connected with the central oil drainage hole (188), and the other end of the transverse oil drainage hole is connected with the low-pressure oil area.
2. The two-position three-way control valve of the high-pressure common rail injector according to claim 1, characterized in that the conical angle D of the conical surface b (174) of the valve seat (17) is 0.5-10 degrees larger than the conical angle D1 of the conical surface a (163) of the new control rod (16).
3. The two-position three-way control valve of the high-pressure common rail injector according to claim 2, characterized in that an outer circular surface (161) of the upper part of the new control rod (16) is the peripheral surface of the cylinder I; the groove (162) is defined by the lower bottom surface of the cylinder I, the side surface of the cylinder II and the small end surface of the circular truncated cone I; the conical surface a (163) of the new control rod (16) is the side surface of the circular truncated cone I.
4. The two-position three-way control valve of the high-pressure common rail injector according to claim 3, characterized in that the diameter A2 of the cylinder III is 0.5-1mm larger than the diameter A1.
5. The two-position three-way control valve of the high-pressure common rail injector according to claim 4, characterized in that the whole body formed by the cylinder III and the inverted circular truncated cone is provided with a hollow circular truncated cone coaxial with the cylinder III, the small end of the hollow circular truncated cone is arranged above the large end of the hollow circular truncated cone, and the diameter of the large end of the hollow circular truncated cone is equal to that of the small end of the inverted circular truncated cone; the diameter B of an edge line (166) of the large end of the hollow circular truncated cone is equal to A1; the taper angle C1 of the side surface (165) of the inverted round table is 10-30 degrees, and the taper angle C2 of the side surface (164) of the hollow round table is 5-15 degrees; the lower end face (167) of the new control rod (16) is the large end face of the hollow circular truncated cone.
6. The two-position three-way control valve of the high-pressure common rail injector according to claim 5, characterized in that the hollow hole (176) of the valve seat (17) comprises a cylindrical hole a, a circular table hole, a cylindrical hole b and a cylindrical hole c which are coaxial and are sequentially arranged from top to bottom; the small end of the circular table hole is arranged above the circular table hole, the large end of the circular table hole is arranged below the circular table hole, the diameter of the small end is equal to the diameter A of the cylindrical hole a, and the diameter of the large end of the circular table hole is smaller than the diameter of the cylindrical hole b; the diameter of the cylindrical hole b is smaller than that of the cylindrical hole c; the diameter of the cylindrical hole c is larger than A2;
the hole wall surface of the upper part of the hollow hole (176) of the valve seat (17) is the hole wall surface of the cylindrical hole a; the central axis of the cylindrical hole a is vertical to the lower end surface (173) of the valve seat (17); the conical surface b (174) of the valve seat (17) is the hole wall of the circular truncated cone hole; the diameter of a sealing line b (175) formed after the conical surface b (174) of the valve seat (17) is contacted with the conical surface a (163) of the new control rod (16) is equal to A1; and the groove wall of the oil groove (177) is the hole wall of the cylindrical hole c.
7. The two-position three-way control valve of the high-pressure common rail injector according to claim 6, characterized in that an inclined oil inlet hole (172) is formed in the valve seat (17), and the upper end of the inclined oil inlet hole (172) is connected with the groove (162).
8. The two-position three-way control valve of the high-pressure common rail injector according to claim 7, characterized in that the control chamber (45) is positioned in a cylinder V, an inner hole (189) is formed below the control chamber, and the cylinder V, the control chamber (45) and the inner hole (189) are coaxial; the inner hole (189) is used for installing the long valve rod (5);
the new control sleeve (18) is provided with an inclined hole (184), two ends of the inclined hole (184) are opened, the lower end of the inclined hole is connected with the control chamber (45), the upper end of the inclined hole is connected with the oil groove (177), and the distance between the end and the central shaft of the new control sleeve (18) is more than half of A1.
9. The two-position three-way control valve of the high-pressure common rail injector according to claim 1, characterized in that a clamping ring groove (168) for placing a clamping ring is machined in the new control rod (16).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111409735.6A CN114165370B (en) | 2021-11-25 | 2021-11-25 | Two-position three-way control valve of high-pressure common-rail oil injector |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111409735.6A CN114165370B (en) | 2021-11-25 | 2021-11-25 | Two-position three-way control valve of high-pressure common-rail oil injector |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN114165370A CN114165370A (en) | 2022-03-11 |
| CN114165370B true CN114165370B (en) | 2022-12-23 |
Family
ID=80480725
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202111409735.6A Active CN114165370B (en) | 2021-11-25 | 2021-11-25 | Two-position three-way control valve of high-pressure common-rail oil injector |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN114165370B (en) |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB556140A (en) * | 1942-02-17 | 1943-09-21 | George Amery | Improvements in or relating to fuel-injection apparatus for internal-combustion engines and like purposes |
| JP2005344630A (en) * | 2004-06-03 | 2005-12-15 | Denso Corp | Fuel injection valve of internal combustion engine |
| JP4325589B2 (en) * | 2004-07-06 | 2009-09-02 | 株式会社デンソー | Common rail injector |
| CN102852684B (en) * | 2012-10-12 | 2014-09-17 | 福建省莆田市中涵机动力有限公司 | Pressure balancing type external sealing plane control valve of common-rail oil sprayer |
| CN102877994B (en) * | 2012-10-12 | 2014-12-24 | 福建省莆田市中涵机动力有限公司 | Pressure balance type inner sealing planar control valve of common-rail oil atomizer |
| US9228550B2 (en) * | 2013-03-11 | 2016-01-05 | Stanadyne Llc | Common rail injector with regulated pressure chamber |
| CN110242460B (en) * | 2019-06-13 | 2021-06-22 | 一汽解放汽车有限公司 | Balanced two-position three-way fuel injection valve |
| CN111207016A (en) * | 2020-03-17 | 2020-05-29 | 莆田市宏业精密机械有限公司 | Direct-control high-pressure common rail oil sprayer |
-
2021
- 2021-11-25 CN CN202111409735.6A patent/CN114165370B/en active Active
Also Published As
| Publication number | Publication date |
|---|---|
| CN114165370A (en) | 2022-03-11 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN101680413B (en) | Control valve for a fuel injection valve | |
| CN101529078B (en) | Injector for injecting fuel | |
| CN101251068B (en) | Valve core type high pressure co-rail electric-controlled oil ejector | |
| CN101382110A (en) | Disk spring type high pressure common rail electric-controlled fuel injector | |
| CN114151254B (en) | Piezoelectric direct-drive-pilot double-acting double-needle-valve oil sprayer | |
| CN104018964A (en) | Pressure accumulation flow-limiting type piezoelectric control oil sprayer | |
| CN104018965A (en) | Electromagnetic control pressure-storage and pressure-stabilizing oil sprayer | |
| CN109488501B (en) | Servo oil driven common rail oil sprayer for heavy oil | |
| CN101498263B (en) | High pressure common rail injector of direct control nozzle switch | |
| CN101251067B (en) | Tappet rod type high pressure co-rail electric-controlled oil ejector | |
| CN111120171B (en) | Fuel injection valve assembly | |
| CN115387943A (en) | Multi-injection-mode electric control oil injector suitable for high-power diesel engine | |
| CN114165370B (en) | Two-position three-way control valve of high-pressure common-rail oil injector | |
| CN203892092U (en) | Pressure accumulating and flow limiting electromagnetic control oil atomizer | |
| GB2367330A (en) | Common-rail fuel injector | |
| CN110017230A (en) | A kind of electro-hydraulic joint control rapid response type high pressure common rail injector | |
| CN111237108A (en) | High-pressure common rail oil sprayer for directly controlling opening and closing of oil nozzle | |
| CN115450811A (en) | Variable oil injection rule electric control oil injector based on needle valve lift adjustment | |
| CN213063810U (en) | Electric control common rail oil injector with dynamic leakage flow control | |
| CN111207016A (en) | Direct-control high-pressure common rail oil sprayer | |
| JP2001207935A (en) | Fuel injection device assembly having improved solenoid operating type check valve | |
| CN109736988B (en) | Electric control single body fuel injection pump for single cylinder diesel engine | |
| CN212508611U (en) | High-pressure common rail oil sprayer for directly controlling opening and closing of oil nozzle | |
| CN208534664U (en) | Medium and heavy-duty engines monomer crosspointer valve twin-jet nozzle high pressure common rail injector | |
| CN212250296U (en) | Direct-control high-pressure common rail oil sprayer |
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 | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |