CN114635818A - High-speed electromagnetic valve for realizing stable injection of common rail fuel injector by utilizing flexible hydraulic damping - Google Patents
High-speed electromagnetic valve for realizing stable injection of common rail fuel injector by utilizing flexible hydraulic damping Download PDFInfo
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- CN114635818A CN114635818A CN202210225059.5A CN202210225059A CN114635818A CN 114635818 A CN114635818 A CN 114635818A CN 202210225059 A CN202210225059 A CN 202210225059A CN 114635818 A CN114635818 A CN 114635818A
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- armature
- iron core
- stage buffering
- electromagnetic valve
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/0012—Valves
- F02M63/0014—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
- F02M63/0021—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means characterised by the arrangement of mobile armatures
- F02M63/0022—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means characterised by the arrangement of mobile armatures the armature and the valve being allowed to move relatively to each other
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M51/00—Fuel-injection apparatus characterised by being operated electrically
- F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
- F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means
- F02M51/0625—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/0012—Valves
- F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
- F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Magnetically Actuated Valves (AREA)
Abstract
The invention aims to provide a high-speed electromagnetic valve for realizing stable injection of a common rail oil injector by utilizing flexible hydraulic damping, which comprises a shell, an iron core and an armature, wherein a coil is arranged in a groove of the iron core, an electromagnetic valve reset spring is arranged in a middle through hole, one end of the electromagnetic valve reset spring is fixed on an electromagnetic valve reset spring seat, the other end of the electromagnetic valve reset spring is sleeved on a boss at the upper end of the armature, a through hole is formed in a valve seat, a buffer groove is formed in the lower end of the iron core, a through hole is formed in the middle of the iron core, the upper end of the through hole is a straight hole, the lower end of the through hole is a horn-shaped expanded hole, a buffer circular platform is arranged on the armature, the upper end face of the valve seat is provided with the buffer groove and a valve seat buffer ring belt, the lower end of a valve rod is provided with two-stage buffer steps, four vertical tangent planes are arranged at the outer edges of the two-stage buffer steps, and a two-stage buffer adjusting ring belt is arranged below the valve seat. The invention utilizes multi-stage flexible damping hydraulic to realize the stable opening and closing of the high-speed electromagnetic valve, thereby improving the injection stability of the common rail oil injector.
Description
Technical Field
The invention relates to a diesel engine, in particular to a high-pressure common rail device of the diesel engine.
Background
The high-speed electromagnetic valve with high dynamic response characteristic is a core component of an electric control high-pressure common rail fuel injection system, and the control system realizes flexible control on the starting moment and the fuel injection quantity of fuel injection through opening and closing of the high-speed electromagnetic valve, so that the modern diesel engine is optimal in economy and emission.
In order to realize controllability of oil injection characteristics of the high-pressure common rail oil injector, the high-speed electromagnetic valve needs to be opened and closed more quickly, however, in the process of quick action, quick lifting and descending of the armature inevitably cause large impact force to be formed between the armature and the iron core and between the armature and the valve seat, the armature often cannot be opened completely at one time due to the large impact force and is vibrated for many times, and the armature is not seated thoroughly or crisp, so that seating rebound occurs. Therefore, for a high-speed electromagnetic valve with high response characteristic, how to realize stable opening and seating of the high-speed electromagnetic valve on the premise of ensuring high response is a technical problem that needs to be solved urgently for the high-speed electromagnetic valve of the high-pressure common rail injector.
Disclosure of Invention
The invention aims to provide a high-speed electromagnetic valve which can solve the problem that the electromagnetic valve is not thoroughly opened and closed due to the impact rebound of an armature iron and an iron core or a valve seat at present, realize the stable injection and the quick oil cut-off of a high-pressure common rail oil injector, and further improve the oil injection consistency of a common rail system.
The purpose of the invention is realized as follows:
the invention relates to a high-speed electromagnetic valve for realizing stable injection of a common rail oil sprayer by utilizing flexible hydraulic damping, which is characterized in that: the electromagnetic valve comprises a housing, the iron core, armature, the disk seat, fastening nut is installed to the casing top, fastening nut middle part sets up the solenoid valve reset spring seat, the iron core is installed in the casing, the iron core sets up recess and winding coil, the middle part of iron core sets up middle through-hole, install solenoid valve reset spring in the middle through-hole, the iron core below sets gradually armature, the disk seat, two-stage buffering regulation clitellum, the armature upper end sets up abrupt platform and buffering round platform, solenoid valve reset spring's both ends overlap respectively in solenoid valve reset spring seat and abrupt bench, the armature lower extreme sets up the valve rod, the valve rod passes the disk seat, the bottom of valve rod sets up two-stage buffering ladder and is located two-stage buffering regulation clitellum, armature upper end place shell inner wall sets up fixing gasket.
The present invention may further comprise:
1. the upper end of the through hole in the middle of the iron core is a straight hole, and the lower end of the through hole is a horn-shaped hole.
2. The armature buffering round platform is provided with an inclined plane which is parallel to the iron core reaming inclined plane, the diameter of the upper end face of the armature buffering round platform is equal to that of a straight hole of the iron core, and the diameter of the lower end face of the armature buffering round platform is equal to that of a large hole of the iron core reaming.
3. The height of the armature buffering circular truncated cone is 30% of the total lifting stroke of the armature.
4. The lower end of the iron core is provided with an iron core buffer slot.
5. The iron core buffer grooves are distributed in a petal shape, and an ascending throttling damping gap of 0.004-0.005mm is formed between the iron core buffer grooves and the lower end face of the coil.
6. The upper end face of the valve seat is provided with a valve seat buffer strip and a valve seat buffer groove.
7. The two-stage buffering ladder comprises a valve rod one-stage buffering ladder, the two-stage buffering adjusting girdle comprises a one-stage buffering adjusting girdle and a second-stage buffering adjusting girdle, the diameter of the valve rod one-stage buffering ladder is smaller than the inner diameter of the one-stage buffering adjusting girdle, the valve rod one-stage buffering ladder and the second-stage buffering adjusting girdle form an ascending throttling damping gap of 0.006-0.007mm, the valve rod one-stage buffering ladder and the second-stage buffering adjusting girdle form a sitting throttling damping gap of 0.004-0.005mm, and the upper end surface height of the one-stage buffering adjusting girdle is positioned at 80% of the total armature sitting stroke.
8. The two-stage buffering ladder comprises a valve rod two-stage buffering ladder, the two-stage buffering adjusting girdle comprises a first-stage buffering adjusting girdle and a second-stage buffering adjusting girdle, the diameter of the valve rod two-stage buffering ladder is smaller than the inner diameter of the second-stage buffering adjusting girdle and larger than the inner diameter of the first-stage buffering adjusting girdle, the valve rod two-stage buffering ladder and the second-stage buffering adjusting girdle form a sitting throttling damping gap of 0.004-0.005mm, and the height of the upper end surface of the first-stage buffering adjusting girdle is positioned at 70% of the total armature sitting stroke.
9. Four vertical tangent planes are arranged at the outer edge of the two-stage buffer ladder.
The invention has the advantages that:
1. in the process of ascending the armature, the first buffering is realized through a buffer groove at the lower end of the iron core, the armature buffers the throttling damping effect formed by the outer edge of the circular truncated cone and the inner wall of the hole expansion of the iron core, the flexible buffering is realized, the impact force between the armature and the iron core is reduced, and the stable opening of the electromagnetic valve and the stable injection of the common rail oil injector are realized;
2. in the descending process of the armature, pre-buffering is realized through a throttling damping gap at the upper end of the armature and the valve seat buffering ring belt, and step-by-step damping buffering is formed through the outer edges of the first-stage buffering step and the second-stage buffering step of the valve rod and the buffering adjusting ring, so that the impact force between the valve rod and the valve seat is reduced, the stable closing of the electromagnetic valve is realized, and the stability of oil injection of the common rail oil injector is improved.
Drawings
FIG. 1 is a schematic structural view of the present invention;
fig. 2 is a bottom view of the core;
FIG. 3 is a top view of the valve seat;
FIG. 4 is a schematic view of the throttle damping gap between the valve rod and the damping adjusting ring.
Detailed Description
The invention will now be described in more detail by way of example with reference to the accompanying drawings in which:
with reference to fig. 1-4, fig. 1 is a schematic structural diagram of the present invention, which includes a housing 1, a fastening nut 2, a solenoid valve return spring seat 3, a solenoid valve return spring 4, an iron core 5, a coil 6, a fixing gasket 7, an armature 8, an armature valve rod 9, a valve seat 10, and a buffer adjusting ring 11, wherein the coil 6 is installed in a groove of the iron core 5, the solenoid valve return spring 4 is installed in a middle through hole, one end of the solenoid valve return spring 4 is fixed on the solenoid valve return spring seat 3, the other end is sleeved on a boss at the upper end of the armature 8, the valve seat 10 is provided with a through hole, the lower end of the iron core 5 is provided with a buffer groove 12, the middle of the iron core is provided with a through hole 13, the upper end of the through hole is a straight hole, the lower end of the through hole is a trumpet-shaped enlarged hole, the armature is provided with a buffer round boss 14, the upper end surface of the valve seat is provided with a buffer groove 15 and a valve seat buffer ring 16, the lower end of the valve rod 9 is provided with two- stage buffer steps 17, 18, 17, 18, 17, Four vertical sections are arranged at the outer edge of the valve seat 18, and a two-stage buffer adjusting ring belt 11 is arranged below the valve seat 10. The buffer groove 12 at the lower end of the iron core 5 is distributed in a petal shape, the lower end face of the buffer groove 12 is flush with the lower end face of the iron core 5, the height of the upper end face is higher than that of the lower end face of the coil 6, and the iron core buffer groove 12 and the lower end face of the coil 6 form a rising throttling damping gap of 0.004-0.005 mm. The diameter of the upper end face of the armature buffering circular truncated cone 14 is equal to that of a straight hole of the iron core 5, the diameter of the lower end face of the armature buffering circular truncated cone 14 is equal to that of the large diameter of the iron core reaming hole 13, the inclined plane of the armature buffering circular truncated cone 14 is parallel to that of the iron core reaming hole 13, and the height of the armature buffering circular truncated cone 14 is 30% of the total ascending stroke of the armature 5. The upper end buffer groove 15 of the valve seat 10 is distributed in a petal shape, the upper end surface of the valve seat buffer ring belt 16 is flush with the lower end surface of the armature 5, and a seating throttling damping gap of 0.004-0.005mm is formed between the valve seat buffer groove 15 and the valve seat buffer ring belt 16. The diameter of the first-stage buffering step 17 of the valve rod is smaller than the inner diameter of the first-stage buffering adjusting ring belt, the first-stage buffering step 18 of the valve rod and the second-stage buffering adjusting ring belt form a rising throttling damping gap of 0.006-0.007mm, the first-stage buffering step and the second-stage buffering adjusting ring belt form a sitting throttling damping gap of 0.004-0.005mm, and the upper end surface height of the first-stage buffering adjusting ring belt is positioned at 80% of the total armature sitting stroke. The diameter of the second-stage buffering step 18 of the valve rod is smaller than the inner diameter of the second-stage buffering adjusting ring band and larger than the inner diameter of the first-stage buffering adjusting ring band, a seating throttling damping gap of 0.004-0.005mm is formed between the second-stage buffering step 18 of the valve rod and the second-stage buffering adjusting ring band, and the height of the upper end face of the first-stage buffering adjusting ring band is 70% of the total armature seating stroke.
With reference to fig. 2-4, the operating principle of the present invention is that when the coil 6 of the solenoid valve is not energized, the solenoid valve return spring 4 is in a compressed state, which generates a downward spring force on the armature 8, pressing the armature 8 and the valve stem 9 against the seat cushion adjustment ring 16, so that the armature 8 remains stationary at an initial position. When the coil 6 of the electromagnetic valve is electrified, a magnetic loop is formed with the iron core 5 and the armature 8, electromagnetic force is generated on the armature 8, the armature 8 drives the armature valve rod 9 to move upwards together, the oil return path is opened, and low-pressure fuel oil leaks away through the outer side of the armature valve rod 9. Along with the continuous rising of the armature 8, fuel oil between the armature 8 and the iron core 5 is extruded, the fuel oil is also stored in a buffer groove 12 at the lower end of the iron core 5, and because the height of the lower end surface of the coil 6 is lower than that of the buffer groove 12, the fuel oil in the buffer groove 12 flows outwards and passes through a throttling damping gap at the lower end of the coil 6, so that the first buffering is realized, the pressure of the fuel oil in the buffer groove 12 at the inner side is increased, resistance is generated when the armature 8 rises, the rising speed of the armature 8 is reduced, the collision between the armature 8 and the iron core 5 is reduced, and the rebound after the armature 8 collides is weakened;
when the armature 8 continues to move upwards until the height of the armature buffering circular truncated cone 14 is flush with the lower end of the iron core 5, the outer edge of the armature buffering circular truncated cone 14 and the inner wall of a reaming hole 13 of the iron core generate a throttling damping effect, along with the rising of the armature, the fuel oil flow area of the upper part and the lower part of the armature 8 is gradually reduced, fuel oil cannot rapidly pass through and is extruded, the fuel oil pressure of the part is rapidly increased, resistance is generated on the rising of the armature 8, the rising speed of the armature 8 is reduced, the collision between the armature 8 and the iron core 5 is reduced, flexible buffering is realized, the rebound after the collision of the armature 8 is weakened, and the stable opening of the electromagnetic valve and the stable injection of the common rail fuel injector are realized;
when the coil 6 of the electromagnetic valve is powered off, the electromagnetic force generated by the magnetic circuit disappears, the armature 8 and the armature valve rod 9 start to move downwards under the pressure effect of the electromagnetic valve return spring 4, along with the continuous descending of the armature 8, fuel oil between the armature 8 and the valve seat 10 is extruded, fuel oil can also be stored in the buffer groove 15 at the upper end of the valve seat 10, and the height of the upper end surface of the valve seat buffer ring belt 16 is higher than that of the buffer groove 15, so that the fuel oil can pass through the throttling damping gap at the upper end of the valve seat buffer ring belt 16 when flowing outwards in the inner side of the buffer groove 15, pre-buffering is realized, the pressure of the fuel oil in the inner side buffer groove 15 is increased, resistance is generated on the downward movement of the armature 8, the seating speed of the armature 8 is reduced, the collision between the armature 8 and the valve seat 5 is reduced, and the rebound after the collision of the armature 8 is weakened;
when the armature 8 moves downwards until the outer edge of the primary buffer step 17 of the armature valve rod is flush with the upper end of the secondary buffer adjusting ring belt, the outer edge of the primary buffer step 17 of the armature valve rod and the secondary buffer adjusting ring belt generate a throttling damping effect to realize primary buffering, and a throttling damping gap 19 is shown in fig. 4, so that the fuel oil circulation areas of the upper part and the lower part of the valve rod 9 are rapidly reduced, the fuel oil cannot rapidly pass through and is extruded, the fuel oil pressure of the part is rapidly increased to generate resistance to the seating of the armature 8, the movement speed of the armature 8 is reduced, the collision between the valve rod 9 and the valve seat 10 is reduced, and the rebound after the valve rod 9 collides is weakened;
when the armature 8 moves downwards until the outer edge of the secondary buffer step 18 of the armature valve rod is flush with the upper end of the buffer adjusting ring belt in height, the outer edge of the secondary buffer step 18 of the armature valve rod and the buffer adjusting ring belt generate a throttling damping effect to realize secondary buffering, and throttling damping gaps 19 and 20 are shown in figure 4, so that the fuel flow areas of the upper part and the lower part of the valve rod 9 are rapidly reduced, fuel cannot rapidly pass through and is extruded, the fuel pressure of the part is rapidly increased to generate resistance on the seating of the armature 8, the movement speed of the armature 8 is reduced, the collision between the valve rod 9 and the valve seat 10 is reduced, the rebound after the collision of the valve rod 9 is weakened, and the stable closing of the electromagnetic valve and the rapid oil cut-off of the common rail oil injector are realized.
On the basis of this, by adjusting and changing the height of the buffer groove, the degree of buffering during the raising and seating of the armature 8 can be adjusted.
Claims (10)
1. A high-speed electromagnetic valve for realizing stable injection of a common rail oil sprayer by utilizing flexible hydraulic damping is characterized in that: the electromagnetic valve comprises a housing, the iron core, armature, the disk seat, fastening nut is installed to the casing top, fastening nut middle part sets up the solenoid valve reset spring seat, the iron core is installed in the casing, the iron core sets up recess and winding coil, the middle part of iron core sets up middle through-hole, install solenoid valve reset spring in the middle through-hole, the iron core below sets gradually armature, the disk seat, two-stage buffering regulation clitellum, the armature upper end sets up abrupt platform and buffering round platform, solenoid valve reset spring's both ends overlap respectively in solenoid valve reset spring seat and abrupt bench, the armature lower extreme sets up the valve rod, the valve rod passes the disk seat, the bottom of valve rod sets up two-stage buffering ladder and is located two-stage buffering regulation clitellum, armature upper end place shell inner wall sets up fixing gasket.
2. The high-speed electromagnetic valve for realizing stable injection of the common rail injector by utilizing flexible hydraulic damping as claimed in claim 1 is characterized in that: the upper end of the through hole in the middle of the iron core is a straight hole, and the lower end of the through hole is a horn-shaped hole.
3. The high-speed electromagnetic valve for realizing stable injection of the common rail injector by utilizing flexible hydraulic damping as claimed in claim 2 is characterized in that: the armature buffering round platform is provided with an inclined plane which is parallel to the iron core reaming inclined plane, the diameter of the upper end face of the armature buffering round platform is equal to that of a straight hole of the iron core, and the diameter of the lower end face of the armature buffering round platform is equal to that of a large hole of the iron core reaming.
4. The high-speed electromagnetic valve for realizing stable injection of the common rail injector by utilizing flexible hydraulic damping as claimed in claim 1 is characterized in that: the height of the armature buffering circular truncated cone is 30% of the total lifting stroke of the armature.
5. The high-speed electromagnetic valve for realizing stable injection of the common rail injector by utilizing flexible hydraulic damping as claimed in claim 1 is characterized in that: the lower end of the iron core is provided with an iron core buffer slot.
6. The high-speed electromagnetic valve for realizing stable injection of the common rail injector by utilizing flexible hydraulic damping as claimed in claim 5 is characterized in that: the iron core buffer slots are distributed in a petal shape, and an ascending throttling damping gap of 0.004-0.005mm is formed between the iron core buffer slots and the lower end face of the coil.
7. The high-speed electromagnetic valve for realizing stable injection of the common rail injector by utilizing flexible hydraulic damping as claimed in claim 1 is characterized in that: the upper end face of the valve seat is provided with a valve seat buffer strip and a valve seat buffer groove.
8. The high-speed electromagnetic valve for realizing stable injection of the common rail injector by utilizing flexible hydraulic damping as claimed in claim 1 is characterized in that: the two-stage buffering ladder comprises a valve rod one-stage buffering ladder, the two-stage buffering adjusting girdle comprises a one-stage buffering adjusting girdle and a second-stage buffering adjusting girdle, the diameter of the valve rod one-stage buffering ladder is smaller than the inner diameter of the one-stage buffering adjusting girdle, the valve rod one-stage buffering ladder and the second-stage buffering adjusting girdle form an ascending throttling damping gap of 0.006-0.007mm, the valve rod one-stage buffering ladder and the second-stage buffering adjusting girdle form a sitting throttling damping gap of 0.004-0.005mm, and the upper end surface height of the one-stage buffering adjusting girdle is positioned at 80% of the total armature sitting stroke.
9. The high-speed electromagnetic valve for realizing stable injection of the common rail injector by utilizing flexible hydraulic damping as claimed in claim 1 is characterized in that: the two-stage buffering ladder comprises a valve rod two-stage buffering ladder, the two-stage buffering adjusting girdle comprises a first-stage buffering adjusting girdle and a second-stage buffering adjusting girdle, the diameter of the valve rod two-stage buffering ladder is smaller than the inner diameter of the second-stage buffering adjusting girdle and larger than the inner diameter of the first-stage buffering adjusting girdle, the valve rod two-stage buffering ladder and the second-stage buffering adjusting girdle form a sitting throttling damping gap of 0.004-0.005mm, and the height of the upper end surface of the first-stage buffering adjusting girdle is positioned at 70% of the total armature sitting stroke.
10. The high-speed electromagnetic valve for realizing the stable injection of the common rail oil injector by utilizing the flexible hydraulic damping as claimed in claim 1 is characterized in that: four vertical tangent planes are arranged at the outer edge of the two-stage buffer ladder.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210225059.5A CN114635818A (en) | 2022-03-09 | 2022-03-09 | High-speed electromagnetic valve for realizing stable injection of common rail fuel injector by utilizing flexible hydraulic damping |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210225059.5A CN114635818A (en) | 2022-03-09 | 2022-03-09 | High-speed electromagnetic valve for realizing stable injection of common rail fuel injector by utilizing flexible hydraulic damping |
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| Publication Number | Publication Date |
|---|---|
| CN114635818A true CN114635818A (en) | 2022-06-17 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202210225059.5A Pending CN114635818A (en) | 2022-03-09 | 2022-03-09 | High-speed electromagnetic valve for realizing stable injection of common rail fuel injector by utilizing flexible hydraulic damping |
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| CN (1) | CN114635818A (en) |
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| WO2021110307A1 (en) * | 2019-12-03 | 2021-06-10 | Robert Bosch Gmbh | Solenoid valve for a fluid-conveying device and method for operating a solenoid valve |
| CN113790116A (en) * | 2021-09-14 | 2021-12-14 | 哈尔滨工程大学 | Electric control high-pressure common rail oil injector capable of realizing variable oil injection rule |
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2022
- 2022-03-09 CN CN202210225059.5A patent/CN114635818A/en active Pending
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|---|---|---|---|---|
| DE4421714A1 (en) * | 1994-06-21 | 1996-01-04 | Bosch Gmbh Robert | Fuel injection system |
| JPH09273457A (en) * | 1996-04-04 | 1997-10-21 | Hitachi Ltd | Injector for high-pressure fuel injection device |
| US20020125343A1 (en) * | 1999-12-16 | 2002-09-12 | Fevzi Yildirim | Fuel injector valve |
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| CN1726341A (en) * | 2002-12-13 | 2006-01-25 | 罗伯特·博世有限公司 | The vibrationless electromagnetic regulator that is used for injection valve |
| JP2005351203A (en) * | 2004-06-11 | 2005-12-22 | Denso Corp | Fuel injection valve |
| US20060027682A1 (en) * | 2004-07-08 | 2006-02-09 | Aisan Kogyo Kabushiki Kaisha | Fuel injectors |
| JP2010185468A (en) * | 2009-02-10 | 2010-08-26 | Rinnai Corp | Motor safety valve |
| CN103437928A (en) * | 2013-09-06 | 2013-12-11 | 中国第一汽车股份有限公司无锡油泵油嘴研究所 | Control valve assembly for electromagnetic valve type oil sprayer |
| CN104100425A (en) * | 2014-07-23 | 2014-10-15 | 哈尔滨工程大学 | Electronically-controlled common-rail oil injector of heavy-oil diesel for ship |
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| CN113790116A (en) * | 2021-09-14 | 2021-12-14 | 哈尔滨工程大学 | Electric control high-pressure common rail oil injector capable of realizing variable oil injection rule |
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