CN106523225B - Resonant type electric control oil injector with hydraulic feedback - Google Patents
Resonant type electric control oil injector with hydraulic feedback Download PDFInfo
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- CN106523225B CN106523225B CN201710034986.8A CN201710034986A CN106523225B CN 106523225 B CN106523225 B CN 106523225B CN 201710034986 A CN201710034986 A CN 201710034986A CN 106523225 B CN106523225 B CN 106523225B
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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
- 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
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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
- F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
- F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
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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
- F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
- F02M61/1893—Details of valve member ends not covered by groups F02M61/1866 - F02M61/188
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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
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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
- F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
- F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
- F02M63/0035—Poppet valves, i.e. having a mushroom-shaped valve member that moves perpendicularly to the plane of the valve seat
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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
- F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
- F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
- F02M63/0036—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat with spherical or partly spherical shaped valve member ends
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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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- 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 aims to provide a resonant electric control oil injector with hydraulic feedback, which comprises an oil injector head, an oil injector body, a flow limiting valve component, an electromagnetic valve component, a tightening cap, a needle valve limiting sleeve, a nozzle, a needle valve body and the like. The pressure storage cavity is arranged in the oil sprayer body and communicated with the main oil inlet hole and the flow limiting valve assembly, so that the stability of the oil spraying process of each cylinder can be ensured when oil is sprayed with large pulse width. The flow-limiting valve assembly is arranged below the pressure accumulation cavity, so that abnormal continuous oil injection is avoided. The bottom of the flow limiting valve assembly is provided with a resonance through hole and a resonance throttling hole, and the fluctuation of fuel oil passing through the flow limiting valve assembly is effectively reduced by utilizing the wave superposition principle. The existence of the feedback oil path slows down the opening speed of the needle valve, enables the system to build pressure quickly, improves the seating speed of the needle valve, and can control the oil injector to finish oil injection quickly. The internal hydraulic pressure of the oil sprayer is balanced, and no static pressure difference exists, so that the function of no static leakage of the oil sprayer is realized.
Description
Technical Field
The invention relates to an oil injection device of an engine, in particular to a high-pressure common rail oil injection device.
Background
With increasing demands on the fuel economy and emission characteristics of engines, emissions are limited primarily in terms of both nitrogen oxides and particulate matter. In order to reduce the emission of nitrogen oxides, it is required to control the instantaneous injection rate during the injection process and to reduce the injection rate at the initial stage of the injection. At the end of the injection event, the injector must be shut off quickly, i.e., the needle seating response is fast, to reduce the amount of particulate matter formed. Therefore, the requirement of the diesel engine emission on the oil injector is that the oil injection process can form an oil injection rate form with slow opening at the initial stage and fast closing at the end.
In addition, the accurate control of the multiple injection oil injection rule is the most advantage and key technology of the high-pressure common rail electronic control oil injection system of the diesel engine. In the multiple injection of the high-pressure common rail system, the water hammer pressure fluctuation caused by the injection directly influences the realization of the ideal oil injection rule of the multiple injection, thereby influencing the performance of the diesel engine.
Disclosure of Invention
The invention aims to provide a resonant electric control oil injector with hydraulic feedback, which can ensure small fuel pressure fluctuation, quick response and no static leakage function during multiple injections.
The purpose of the invention is realized as follows:
the invention relates to a resonant electric control oil injector with hydraulic feedback, which is characterized in that: the oil sprayer comprises an oil sprayer head, an oil sprayer body, a flow limiting valve assembly, a solenoid valve assembly, a needle valve assembly and a downlink high-pressure oil way, wherein the oil sprayer head is arranged above the oil sprayer body, a main oil inlet hole is formed in the oil sprayer head, a pressure storage cavity is formed in the oil sprayer body, the main oil inlet hole is communicated with the pressure storage cavity, the flow limiting valve assembly is arranged in the pressure storage cavity, the solenoid valve assembly and the needle valve assembly are sequentially arranged at the lower end of the oil sprayer body, a tightening cap is positioned outside the solenoid valve assembly and the needle valve assembly, and the upper end of the tightening cap is connected with the lower end of the oil sprayer body in a threaded connection mode;
the flow limiting valve assembly comprises a limiting spring seat, a flow limiting piston, a ball valve reset spring seat and a supporting control slider, wherein the limiting spring seat, the flow limiting piston and the ball valve reset spring seat are arranged from top to bottom, a damping spring is arranged between the limiting spring seat and the flow limiting piston, the supporting control slider is arranged in the ball valve reset spring seat, a ball valve is arranged between the upper end of the supporting control slider and the flow limiting piston, a ball valve reset spring is arranged between the lower end of the supporting control slider and the ball valve reset spring seat below the supporting control slider, a piston blind hole and a flow limiting hole are formed in the flow limiting piston, an axial central through hole is formed in the supporting control slider, a resonance through hole and a resonance orifice are formed in the ball valve reset spring seat, a transition oil cavity is formed between the ball valve reset spring seat and an oil sprayer body below the ball valve reset spring seat, the piston blind hole is communicated with a pressure storage cavity and the flow limiting hole, and the flow limiting hole are communicated or disconnected with the axial central through hole under the control of the ball valve, the resonance through hole and the resonance throttling hole are communicated with the axial central through hole and the transition oil cavity;
the electromagnetic valve component comprises an electromagnet, a coil, an armature, a balance valve rod, a valve seat and an intermediate block, wherein the coil is wound on the electromagnet, an electromagnetic valve reset spring seat is arranged above the electromagnet, the armature is arranged below the electromagnet, an electromagnetic valve reset spring is arranged between the armature and the electromagnetic valve reset spring seat, the balance valve rod is positioned in the valve seat, the upper end part of the balance valve rod is fixedly connected with the armature, the intermediate block is arranged below the valve seat, a balance valve rod cavity is formed among the lower end part of the balance valve rod, the valve seat and the intermediate block, an oil return hole, an intermediate oil way, a lower oil inlet hole and a feedback oil way are arranged in the intermediate block, the intermediate oil way and the feedback oil way are respectively communicated with the balance valve rod cavity, and the oil return hole is communicated with or disconnected with the intermediate oil way and an oil tank under the control of the balance valve rod;
the needle valve assembly comprises a needle valve limiting sleeve, a nozzle and a needle valve body, the needle valve limiting sleeve is positioned in the nozzle, the upper part of the needle valve body is positioned in the needle valve limiting sleeve, the lower part of the needle valve body is positioned in the nozzle, a control cavity is formed between the upper part of the needle valve body and the needle valve limiting sleeve, a needle valve cavity is formed between the needle valve limiting sleeve and the nozzle, a bulge is arranged on the needle valve limiting sleeve and positioned at the control cavity, a needle valve reset spring is arranged between the needle valve body and the bulge, the control cavity is respectively communicated with a middle oil path and a lower oil inlet, an oil containing groove is formed between the needle valve body and the nozzle, and the end part of the nozzle is provided with a spray hole;
the upper end of the descending high-pressure oil way is communicated with a transition oil cavity and is communicated with an oil containing groove through an oil injector body, a valve seat, a middle block, a needle valve cavity and a nozzle, and the feedback oil way and the descending oil inlet hole are respectively communicated with the descending high-pressure oil way.
The present invention may further comprise:
1. when the spray hole sprays oil, the fuel pressure of the transition oil cavity is reduced, the whole of the flow-limiting piston, the ball valve and the supporting control slide block moves downwards, the ball valve is not seated on the ball valve reset spring seat, and the flow-limiting hole is communicated with the axial central through hole; when the mass of the fuel flowing out of the spray hole exceeds a threshold value, the flow limiting piston compresses the ball valve and enables the ball valve to be seated on a ball valve reset spring seat, and the flow limiting hole is disconnected with the axial central through hole; when the spray hole stops spraying oil, the flow-limiting piston, the ball valve and the supporting control slide block are integrally restored to the initial positions under the action of the ball valve return spring.
2. When the coil is electrified, the balance valve rod moves upwards, the oil return hole is communicated with the oil tank, fuel oil in the control cavity returns to the oil tank through the middle oil way and the oil return hole, the needle valve body is lifted upwards, and the spray hole opens for oil injection; after the coil is powered off, the balance valve rod moves downwards under the action of the electromagnetic valve reset spring and is pressed on the upper end face of the middle block, the oil return hole is disconnected with the oil tank, and meanwhile, fuel in the downlink high-pressure oil way enters the control cavity through the feedback oil way, the balance valve rod cavity and the middle oil way and enters the control cavity through the downlink oil inlet hole.
3. The diameter of the middle part of the resonance throttling hole is smaller than the diameters of the two ends of the resonance throttling hole and smaller than the diameter of the resonance through hole, and the total axial length of the resonance throttling hole and the resonance through hole is consistent.
The invention has the advantages that: the invention adopts the pressure accumulation cavity structure, can greatly improve the pressure fluctuation of the whole oil injection system, and particularly can reduce the mutual interference of each oil injector during oil injection. The invention adopts the flow limiting valve component in structure, effectively avoids abnormal conditions such as abnormal oil injection and the like, and adds the resonance structure in the flow limiting valve component, thereby reducing the pressure fluctuation of fuel oil, ensuring the normal and stable oil injection process and simultaneously improving the fuel economy and the working reliability of the oil injector. The invention adopts the electromagnetic valve to control the balance valve rod to adjust the switch of the oil return way, is beneficial to improving the response speed and the control precision of the needle valve, provides a flexible oil injection rule and effectively improves the discharge stability and the economical efficiency of the diesel engine. A hydraulic feedback oil circuit is added in the middle block of the electromagnetic valve component and is communicated with a high-pressure oil circuit and a middle oil circuit, so that the needle valve can be opened slowly, the pressure of the system can be built quickly, the seating speed of the needle valve is improved, and the oil injector can be controlled to finish oil injection quickly. The internal hydraulic pressure of the nozzle part is balanced, and no static pressure difference exists, so that the function of no static leakage of the oil sprayer is realized.
Drawings
FIG. 1 is a schematic structural view of the present invention;
FIG. 2 is a schematic view of a constrictor valve assembly;
FIG. 3 is a schematic view of a solenoid valve assembly;
fig. 4 is a view a-a.
Detailed Description
The invention will now be described in more detail by way of example with reference to the accompanying drawings in which:
referring to fig. 1-4, the invention comprises an oil injector head 1, a flow limiting valve assembly 3, an electromagnetic valve assembly 5, a nozzle 7, a needle valve body 8, a needle valve limiting sleeve 11, a tightening cap 14 and an oil injector body 15. The injector head 1 is mounted on the injector body 15 by screw-fitting and sealed by a seal ring 2 placed on the injector body 15. The injector head 1 is provided with a main inlet port 17 and communicates with a pressure accumulation chamber 16 in the injector body 15. A flow limiting valve assembly 3 is arranged below the pressure accumulation cavity 16. The flow limiting valve component 3 is arranged in the oil injector body 15, and the main structure of the flow limiting valve component comprises a retainer ring 18, a damping spring 19, a ball valve 21, a supporting control slider 22, a ball valve return spring 27, a ball valve return spring seat 28, a flow limiting piston 29 and a limiting spring seat 31. The flow-limiting hole 20 and the piston blind hole 30 are processed on the flow-limiting piston 29, and the axial central through hole 23 is processed on the supporting control slider 22, so that the fuel can smoothly flow to a lower oil path. Two resonance holes, namely a resonance through hole 24 and a resonance throttling hole 26, are machined at the bottom of the ball valve reset spring seat 27. The electromagnetic valve component 5, the nozzle 7 and the needle valve body 8 are sequentially arranged below the oil injector body 15 and are assembled and connected through a tightening cap 14. The solenoid valve assembly 5 mainly comprises a solenoid valve return spring seat 32, a coil 33, an armature 34, a valve seat 35, an intermediate block 40, a balance valve rod 41, an electromagnet 42 and a solenoid valve return spring 43. The armature 34 and the balance stem 41 are mounted in combination inside the valve seat 35. The feedback oil path 36, the oil return hole 37, the descending oil inlet hole 38, the middle oil path 39 and the like are processed in a middle block 40, and the middle block 40, the needle valve limiting sleeve 11 and the needle valve body 8 form a control cavity 13. A needle valve cavity 12 is formed between the needle valve limiting sleeve 11 and the nozzle 7. The needle valve body 8 is arranged in the nozzle 7, the upper end part of the needle valve body 8 sleeved with the needle valve return spring 6 is arranged in the needle valve cavity 12, and an oil containing groove 10 is arranged between the needle valve body 8 and the nozzle 7.
Fig. 1 is a schematic diagram of the overall structure of a resonant electronic control fuel injector with hydraulic feedback according to the present invention, a fuel injector body 15 is provided with a pressure accumulation cavity 16, and the pressure accumulation cavity 16 is communicated with a main fuel inlet 17 on a fuel injector head 1. The oil chamber in the restrictor piston 29 is connected to the pressure accumulation chamber 16 via the blind piston bore 30 and the restrictor orifice 20 formed therein. The injector head 1 and the injector body 15 are assembled through threads, and the sealing ring 2 seals the injector head and the injector body. When high pressure fuel is delivered into the injector through the main inlet port 17, the fuel passing through the accumulator chamber 16 passes down through the restrictor valve assembly 3. After flowing out of the flow limiting valve assembly 3, the fuel flows through the descending high-pressure oil way 4 to enter the control cavity 13 and the oil containing groove 10. An electromagnetic valve assembly 5 is arranged between the lower part of the flow limiting valve assembly 3 and the upper part of the nozzle 7. Within the solenoid valve assembly 5, the lifting and seating of the armature 34 and the balance valve rod 41 are controlled by electromagnetic force. When the coil 33 is energized, the balance valve rod 41 is lifted upward, the oil return hole 37 is opened, and the fuel in the control chamber 13 flows through the intermediate oil passage 39 and is drained through the oil return hole 37. Therefore, the fuel pressure in the control chamber 13 is reduced to form a fuel pressure difference with the oil containing groove 10, so that the needle valve body 8 is lifted, and the oil injection starts. In this process, the needle valve stop collar 11 functions to limit the displacement of the needle valve body 8. When the coil 33 is de-energized and the balance valve rod 41 is seated downward, the oil return hole 37 is closed, part of the fuel directly enters the control chamber 13 through the downward oil inlet hole 38, and part of the fuel also passes through the intermediate oil passage through the feedback oil passage 36 and then enters the control chamber 6. The needle valve body 8 is mounted inside the nozzle and is compressed by the needle valve return spring 6. The nozzle 7 and the solenoid valve assembly 5 are mounted inside the tightening cap 14 and are secured by the injector body 15 and the thread. The internal hydraulic pressure of the nozzle 7 is balanced, and no static pressure difference exists, so that the function of no static leakage of the oil injector is realized.
Fig. 2 is a schematic view of a portion of a constrictor valve assembly of the present invention. The ball valve consists of a retainer ring 18, a damping spring 19, a ball valve 21, a support control slider 22, a ball valve reset spring seat 28, a flow limiting piston 29, a limiting spring seat 31 and the like. The restrictor valve assembly 3 is arranged inside the injector body 15 via a pressure accumulation chamber 16. The retainer ring 18 not only limits the overall restrictor valve assembly 3, but also cooperates with a limiting spring seat 31, which acts as a spring seat for the damping spring 19 on the one hand, and limits the maximum displacement of the restrictor piston 29 on the other hand. Under the action of the spring preload of the damping spring 19 and the ball valve return spring 27, the ball valve 21 cooperates with the lower end face of the flow-limiting piston 29 and the upper end face of the support control slider 22. The ball return spring seat 28 is pressed against the bottom by the spring force of the ball return spring 27, and the seat surface of the ball 21 is formed at the upper variable cross section thereof. High-pressure fuel enters the blind piston bore 30 in the restrictor piston 29 via the pressure accumulation chamber 16, flows through the restrictor bore 20 and into the axially central through bore 23 of the support control slide 22. The fuel flowing out of the axial center through hole 23 passes through the resonance through hole 24 and the resonance orifice 26 into the transition oil chamber 25. By providing the machined resonant through holes 24 and the resonant orifice 26, the amplitude of the fuel pressure wave through the two holes is reduced. In addition, there is one section aperture in the resonance orifice 26 of processing to be littleer than resonance through-hole 24, so the throttle effect is stronger, has resulted in the fuel velocity of flow that flows through from two holes different for the fuel pressure wave of original looks phase difference has been produced, and two strands of fuel pressure waves offset each other after the stack, and then make the pressure oscillation reduce greatly. The fuel flowing out of the excessive oil chamber 25 is led to the lower oil passage through the lower high-pressure oil passage 4. When the fuel injector works normally, the fuel is sprayed out from the spray holes 9, so that the pressure of the fuel in the transition oil cavity 25 is reduced. Due to the throttling effect of the throttling hole 20 on the fuel, the pressure of the fuel in the piston blind hole 30 in the flow limiting piston 29 and the pressure accumulation cavity 16 is increased, and a pressure difference is formed between the pressure of the fuel in the transition oil cavity 25, so that the flow limiting piston 29, the ball valve 21 and the support control slider 22 are integrally displaced downwards, the fuel sprayed by the fuel injector is compensated to a certain extent, and the ball valve 21 is not seated on the ball valve reset spring seat 27. When the fuel injection stops working, the pressure difference between the upper surface and the lower surface of the flow-limiting piston 29 is gradually reduced along with the fuel flowing through the flow-limiting hole 20, and the flow-limiting piston 29, the ball valve 21 and the support control slider 22 are restored to the initial positions again under the action of the ball valve return spring 27. When the fuel is continuously injected from the injection hole 9, and the mass of the fuel flowing out exceeds a threshold value, so that the abnormal working state of the fuel injector occurs, the oil pressure of the transition oil cavity 25 below the flow limiting piston 29 is rapidly reduced to form an upper-lower pressure difference, so that the flow limiting piston 29 presses the ball valve 21 to be seated on the ball valve reset spring seat 28, and the fuel is prevented from continuously flowing. Because the fuel supply is cut off, the fuel injector stops working, thereby reducing the occurrence of abnormal fuel injection to a certain extent and improving the fuel economy and the working stability of the fuel injector.
Fig. 3 is a schematic view of a part of the structure of the solenoid valve assembly of the present invention. The electromagnetic valve comprises an electromagnetic valve return spring seat 32, a coil 33, an armature 34, a valve seat 35, an intermediate block 40, a balance valve rod 41, an electromagnet 42, an electromagnetic valve return spring 43 and the like. The solenoid valve return spring seat 32, the coil 33, the electromagnet 42, and the solenoid valve return spring 43 are built in the injector body 15, wherein the solenoid valve return spring seat 30 is fastened to the top end of the solenoid valve by a screw. The solenoid return spring 43 is between the solenoid return spring seat 32 and the armature 34, and the armature 34 and the balance valve rod 41 are disposed inside the valve seat 35 below the injector body 15. The intermediate block 40 is located below the valve seat 35. When the injector starts to inject fuel, the coil 33 is electrified to form a magnetic circuit with the armature 34 and the electromagnet 42, electromagnetic force is generated, the balance valve rod 41 is attracted to move upwards, and the oil return hole 37 in the middle block 40 is opened. At this time, the fuel in the control chamber 13 passes through the intermediate oil passage 39 and the oil return hole 37 and returns to the oil tank, the pressure in the control chamber 13 decreases, the upper surface of the needle valve body 8 is pressed and reduced, and a pressure difference is formed between the upper surface of the needle valve body and the pressure of the fuel in the oil containing groove 10. Under the action of pressure difference, the needle valve body 8 is slowly lifted upwards, and the spray hole 9 is opened to spray oil. When the injector stops injecting fuel, the coil 33 is cut off, and because the armature 34 and the balance valve rod 41 are tightly combined into a whole, they are jointly moved downwards under the action of the spring pre-tightening force of the electromagnetic valve return spring 43, and are pressed on the upper end surface of the intermediate block 40, and the oil return hole 37 is blocked. Meanwhile, two paths of oil are fed into the middle block 40, and one path of oil flows through the middle oil path 39 through the feedback oil path 36 and enters the control cavity 13; the other way is directly into the control chamber 13 through the lower inlet port 38. In the whole oil injection process, high-pressure fuel oil always enters an upper oil cavity through the feedback oil way 36, so that the oil pressure reduction rate of the control cavity 13 is reduced, the pressure drop of the control cavity 13 at the initial stage of oil injection is reduced and slowed, and the generation of nitrogen oxides is reduced; when oil injection is finished, the pressure building speed of a normal single oil inlet hole to the control cavity 13 is increased, the seating speed of the needle valve is increased, and the response speed of the needle valve is optimized.
Fig. 4 is an enlarged view of the needle valve body 8 in section a-a. The arc-shaped surface can play a good role in guiding.
According to the working process, in the oil injection process of the resonant electric control oil injector with hydraulic feedback, the feedback oil way 36 is added in the electromagnetic valve component 5 part, so that the needle valve is opened slowly; and two paths of oil are fed through the feedback oil path 36 and the downlink oil inlet hole 38, so that the system pressure is built quickly, the seating speed of the needle valve is improved, and the oil injector is controlled to finish oil injection quickly. The whole oil injection process is controlled by the electromagnetic valve, so that the requirements of high response speed, high control precision and controllable oil injection rule in the oil injection process are met. The flow-limiting valve assembly 3 arranged in the oil injector body 15 effectively prevents the abnormal oil injection state from continuing. In addition, the resonance structure effectively reduces the fuel pressure fluctuation, and ensures the stability and the fuel economy of the working process. When the common rail pressure storage cavity 16 structure is applied to a common rail system, the common rail pressure fluctuation can be effectively reduced by adopting the pressure storage cavity 16 structure under the large-oil-quantity injection state, so that the phenomena of uniformity and stability reduction of the oil injection process of each cylinder are reduced.
Claims (5)
1. A resonant electric control oil injector with hydraulic feedback is characterized in that: the oil sprayer comprises an oil sprayer head, an oil sprayer body, a flow limiting valve assembly, a solenoid valve assembly, a needle valve assembly and a downlink high-pressure oil way, wherein the oil sprayer head is arranged above the oil sprayer body, a main oil inlet hole is formed in the oil sprayer head, a pressure storage cavity is formed in the oil sprayer body, the main oil inlet hole is communicated with the pressure storage cavity, the flow limiting valve assembly is arranged in the pressure storage cavity, the solenoid valve assembly and the needle valve assembly are sequentially arranged at the lower end of the oil sprayer body, a tightening cap is positioned outside the solenoid valve assembly and the needle valve assembly, and the upper end of the tightening cap is connected with the lower end of the oil sprayer body in a threaded connection mode;
the flow limiting valve assembly comprises a limiting spring seat, a flow limiting piston, a ball valve reset spring seat and a supporting control slider, wherein the limiting spring seat, the flow limiting piston and the ball valve reset spring seat are arranged from top to bottom, a damping spring is arranged between the limiting spring seat and the flow limiting piston, the supporting control slider is arranged in the ball valve reset spring seat, a ball valve is arranged between the upper end of the supporting control slider and the flow limiting piston, a ball valve reset spring is arranged between the lower end of the supporting control slider and the ball valve reset spring seat below the supporting control slider, a piston blind hole and a flow limiting hole are formed in the flow limiting piston, an axial central through hole is formed in the supporting control slider, a resonance through hole and a resonance orifice are formed in the ball valve reset spring seat, a transition oil cavity is formed between the ball valve reset spring seat and an oil sprayer body below the ball valve reset spring seat, the piston blind hole is communicated with a pressure storage cavity and the flow limiting hole, and the flow limiting hole are communicated or disconnected with the axial central through hole under the control of the ball valve, the resonance through hole and the resonance throttling hole are communicated with the axial central through hole and the transition oil cavity;
the electromagnetic valve component comprises an electromagnet, a coil, an armature, a balance valve rod, a valve seat and an intermediate block, wherein the coil is wound on the electromagnet, an electromagnetic valve reset spring seat is arranged above the electromagnet, the armature is arranged below the electromagnet, an electromagnetic valve reset spring is arranged between the armature and the electromagnetic valve reset spring seat, the balance valve rod is positioned in the valve seat, the upper end part of the balance valve rod is fixedly connected with the armature, the intermediate block is arranged below the valve seat, a balance valve rod cavity is formed among the lower end part of the balance valve rod, the valve seat and the intermediate block, an oil return hole, an intermediate oil path, a downward oil inlet hole and a feedback oil path are arranged in the intermediate block, the intermediate oil path and the feedback oil path are respectively communicated with the balance valve rod cavity, and the oil return hole is communicated with or disconnected with the intermediate oil path and an oil tank under the control of the balance valve rod;
the needle valve assembly comprises a needle valve limiting sleeve, a nozzle and a needle valve body, the needle valve limiting sleeve is positioned in the nozzle, the upper part of the needle valve body is positioned in the needle valve limiting sleeve, the lower part of the needle valve body is positioned in the nozzle, a control cavity is formed between the upper part of the needle valve body and the needle valve limiting sleeve, a needle valve cavity is formed between the needle valve limiting sleeve and the nozzle, a bulge is arranged on the needle valve limiting sleeve and positioned at the control cavity, a needle valve reset spring is arranged between the needle valve body and the bulge, the control cavity is respectively communicated with a middle oil path and a descending oil inlet, an oil containing groove is formed between the needle valve body and the nozzle, and the end part of the nozzle is provided with a spray hole;
the upper end of the descending high-pressure oil way is communicated with a transition oil cavity and is communicated with an oil containing groove through an oil injector body, a valve seat, a middle block, a needle valve cavity and a nozzle, and the feedback oil way and the descending oil inlet hole are respectively communicated with the descending high-pressure oil way.
2. The resonant electronic control fuel injector with hydraulic feedback as claimed in claim 1, wherein: when the spray hole sprays oil, the fuel pressure of the transition oil cavity is reduced, the whole of the flow-limiting piston, the ball valve and the supporting control slide block moves downwards, the ball valve is not seated on the ball valve reset spring seat, and the flow-limiting hole is communicated with the axial central through hole; when the mass of the fuel flowing out of the spray hole exceeds a threshold value, the flow limiting piston compresses the ball valve and enables the ball valve to be seated on a ball valve reset spring seat, and the flow limiting hole is disconnected with the axial central through hole; when the spray hole stops spraying oil, the flow-limiting piston, the ball valve and the supporting control slide block are integrally restored to the initial positions under the action of the ball valve return spring.
3. The resonant electronic control fuel injector with hydraulic feedback as claimed in claim 1 or 2, wherein: when the coil is electrified, the balance valve rod moves upwards, the oil return hole is communicated with the oil tank, fuel oil in the control cavity returns to the oil tank through the middle oil way and the oil return hole, the needle valve body is lifted upwards, and the spray hole opens for oil injection; after the coil is powered off, the balance valve rod moves downwards under the action of the electromagnetic valve reset spring and is pressed on the upper end face of the middle block, the oil return hole is disconnected with the oil tank, and meanwhile, fuel in the downlink high-pressure oil way enters the control cavity through the feedback oil way, the balance valve rod cavity and the middle oil way and enters the control cavity through the downlink oil inlet hole.
4. The resonant electronic control fuel injector with hydraulic feedback as claimed in claim 1 or 2, wherein: the diameter of the middle part of the resonance throttling hole is smaller than the diameters of the two ends of the resonance throttling hole and smaller than the diameter of the resonance through hole, and the total axial length of the resonance throttling hole and the resonance through hole is consistent.
5. The resonant electronic control fuel injector with hydraulic feedback as claimed in claim 3, wherein: the diameter of the middle part of the resonance throttling hole is smaller than the diameters of the two ends of the resonance throttling hole and smaller than the diameter of the resonance through hole, and the total axial length of the resonance throttling hole and the resonance through hole is consistent.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710034986.8A CN106523225B (en) | 2017-01-18 | 2017-01-18 | Resonant type electric control oil injector with hydraulic feedback |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201710034986.8A CN106523225B (en) | 2017-01-18 | 2017-01-18 | Resonant type electric control oil injector with hydraulic feedback |
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| CN106523225A CN106523225A (en) | 2017-03-22 |
| CN106523225B true CN106523225B (en) | 2022-03-18 |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| US6308690B1 (en) * | 1994-04-05 | 2001-10-30 | Sturman Industries, Inc. | Hydraulically controllable camless valve system adapted for an internal combustion engine |
| WO2011025512A1 (en) * | 2009-08-27 | 2011-03-03 | Mcallister Technologies, Llc | Integrated fuel injectors and igniters and associated methods of use and manufacture |
| US8746050B2 (en) * | 2008-09-19 | 2014-06-10 | Omar Cueto | Fuel injection feedback system and method |
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