CN106762286B - Micro-dynamic oil return bypass type electric control oil injector with hydraulic feedback - Google Patents
Micro-dynamic oil return bypass type electric control oil injector with hydraulic feedback Download PDFInfo
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- CN106762286B CN106762286B CN201710034962.2A CN201710034962A CN106762286B CN 106762286 B CN106762286 B CN 106762286B CN 201710034962 A CN201710034962 A CN 201710034962A CN 106762286 B CN106762286 B CN 106762286B
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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
- 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
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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
Abstract
The invention aims to provide a micro-dynamic oil return bypass type 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 needle valve limiting sleeve, a nozzle and a needle valve body. 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 is guaranteed under the condition of large oil spraying quantity. The flow-limiting valve assembly is placed below the pressure accumulation chamber, and the abnormal oil injection is prevented from being continuously performed. The electromagnetic valve component is processed at the bottom of the oil injector body, and the balance valve rod is driven by electromagnetic force to move. The electromagnetic valve adopts a two-position three-way valve form, so that the dynamic oil return amount in the oil injection process is greatly reduced. The control cavity is internally provided with a control slide block which is contacted with the middle block, and the functions of slowing down the oil injection speed in the initial stage of injection and accelerating the seating response of the needle valve are achieved. The hydraulic feedback oil circuit machined in the middle block further enhances the effect. The static pressure difference does not exist in the oil sprayer, the oil sprayer does not have static leakage, and the hydraulic efficiency of the system is improved.
Description
Technical Field
The invention relates to an engine fuel injection device.
Background
In order to optimize the fuel economy and emission indexes of a diesel engine, the electric control fuel injector of the diesel engine on the current market starts to adopt high-speed electromagnetic switch valve type control, and the electric control fuel injector has the advantages of quick system response, high control precision, flexible control strategy, reliable working performance and the like. However, as the fuel injection pressure is gradually increased, the performance shortcomings of conventional electrically controlled fuel injectors are also revealed.
Firstly, the fuel injector needs to reduce the emission of nitrogen oxides, which requires that the instantaneous fuel injection rate in the fuel injection process is controlled to reduce the fuel injection rate in the initial stage of injection. On the other hand, 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. Namely, the fuel injector needs to form a 'slow first then fast' fuel injection speed time course curve. Conventional electronically controlled fuel injectors have been difficult to achieve. Secondly, at present, the domestic electronic control oil injector mostly adopts a two-position two-way high-speed electromagnetic valve to control the oil injection process, the two-position two-way valve is always in an open state in the oil injection process, and the communication of a high-pressure oil circuit and a low-pressure oil circuit causes large dynamic oil return amount and energy loss. Meanwhile, the limitation of the hole diameter of the oil inlet and outlet throttling hole and the existence of the dynamic oil return amount also make the quick seating response of the needle valve difficult to realize. Further, at the time of large-quantity injection, the fluctuation of the fuel pressure of the high-pressure common rail may cause inconsistency of the injection process of each cylinder.
Disclosure of Invention
The invention aims to provide a micro-dynamic oil return bypass type electric control oil injector with hydraulic feedback, which is provided with a hydraulic feedback oil path, has micro-dynamic oil return and no static leakage function and can realize a slow-first-then-fast oil injection rate time history curve.
The purpose of the invention is realized by the following steps:
the invention relates to a micro-dynamic oil return bypass type electric control oil injector with hydraulic feedback, which is characterized in that: the high-pressure fuel injection device comprises a fuel injector head, a fuel injector body, a flow limiting valve component, a solenoid valve component, a needle valve component and a downlink high-pressure oil way, wherein the fuel injector head is arranged above the fuel injector body, a main oil inlet is arranged in the fuel injector head, a pressure accumulation cavity is arranged in the fuel injector body, the main oil inlet is communicated with the pressure accumulation cavity, the flow limiting valve component is arranged in the pressure accumulation cavity, the solenoid valve component and the needle valve component are sequentially arranged at the lower end of the fuel injector body, a tightening cap is positioned outside the solenoid valve component and the needle valve component, and the upper end of the tightening cap is connected with the lower end of the fuel injector body in a threaded connection manner;
the flow limiting valve assembly comprises a limiting spring seat, a flow limiting piston, a ball valve reset spring seat and a supporting slide block, wherein the limiting spring seat, the flow limiting piston and the ball valve reset spring seat are arranged from top to bottom;
the electromagnetic valve assembly 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 upper cavity is formed between the middle part of the balance valve rod and the valve seat, an oil cavity is formed between the lower end part of the balance valve rod, the valve seat and the intermediate block, an oil inlet orifice is arranged in the valve seat, an oil return hole, the intermediate oil duct, the intermediate orifice and a hydraulic feedback oil duct are arranged in the intermediate block, the oil inlet orifice is communicated with the balance valve rod upper cavity, the intermediate orifice is respectively communicated with the oil cavity and the intermediate oil duct, the hydraulic feedback oil duct is communicated with the oil cavity, and the oil return hole is communicated with or disconnected with the intermediate oil duct and the oil tank under the control of the balance valve rod;
the needle valve assembly comprises a needle valve limiting sleeve, a control slide block and a needle valve body, wherein the control slide block is positioned in the needle valve limiting sleeve, 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 a nozzle, a control cavity is formed between the control slide block and the needle valve body, a control slide block return spring is arranged in the control cavity, a bulge part is arranged in the middle of the needle valve body, the needle valve return spring is arranged between the bulge part and the needle valve limiting sleeve above the bulge part, a middle cavity is arranged on the upper end face of the control slide block, a control slide block through hole and a bypass oil path are arranged in the control slide block, the control slide block through hole is respectively communicated with the middle cavity and the control cavity, the bypass oil path is communicated with the control cavity, an oil containing groove is formed between the needle valve body and the nozzle, and a spray hole is arranged at the end part of the nozzle;
the upper end of the downlink high-pressure oil way is communicated with a transition oil cavity and is communicated with an oil containing groove through an oil sprayer body, a valve seat, a middle block and a nozzle, and an oil inlet throttling hole and a hydraulic feedback oil way are respectively communicated with the downlink 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 current-limiting piston, the ball valve and the supporting slide block integrally move downwards, the ball valve is not seated on the ball valve reset spring seat, and the current-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 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 upper cavity of the balance valve rod is in a disconnected state with the oil cavity, the oil return hole is in a communicated state with the oil tank, fuel oil in the control cavity returns to the oil tank through the middle oil duct, the middle throttle hole 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 surface of the middle block, the upper cavity of the balance valve rod is communicated with the oil cavity, 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 oil inlet throttling hole, the upper cavity of the balance valve rod, the oil cavity, the middle throttling hole, the middle oil duct and the middle cavity on the one hand and enters the control cavity through the hydraulic feedback oil duct, the oil cavity, the middle oil duct and the middle cavity on the other hand.
3. When the spray hole stops spraying oil, the fuel pressure of the upper end face of the control slide block is higher than that of the lower end face of the control slide block, the control slide block overcomes the pre-tightening force of the return spring of the control slide block to move downwards, the bypass oil way is opened, and the control slide block returns to the initial position under the action force of the return spring of the control slide block along with the fuel entering the control cavity.
The invention has the advantages that: the invention adopts the pressure accumulation cavity structure, and ensures that the continuous oil injection process of the oil injector can not cause great fluctuation to the common rail fuel pressure to cause influence on the oil injection process of other oil injectors under the condition of large oil injection quantity. The invention adopts the flow limiting valve assembly, thereby effectively reducing the occurrence of abnormal oil injection conditions and ensuring the normal and stable oil injection process. The oil injector adopts the electromagnetic valve to control the balance valve rod to adjust the switch of the oil return circuit, thereby improving the control precision and flexibility, effectively improving the emission of the whole diesel engine and improving the fuel economy. The balance valve rod of the oil sprayer adopts a two-position three-way form, so that two ways of sealing of a conical surface and a plane can be realized, the dynamic oil return amount is reduced, and the micro-dynamic oil return function is realized. The bypass oil duct of the control slide block in the control cavity can enable the control cavity to build pressure quickly, and response characteristics of the needle valve are improved. The design of the throttle hole of the control slide block and the middle throttle hole ensures that the oil injector can inject oil slowly at the initial stage, and the formation of nitrogen oxides is reduced. The hydraulic feedback oil channel further slows down initial oil injection and accelerates the seating of the needle valve. And the static pressure difference does not exist in the oil sprayer, so that the oil sprayer can realize the function of static leakage-free.
Drawings
FIG. 1 is a schematic view of the structure 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 schematic view of a needle valve assembly;
FIG. 5 isbase:Sub>A schematic view A-A.
Detailed Description
The invention is described in more detail below by way of example with reference to the accompanying drawings:
with reference to fig. 1-5, the main structure of the micro-dynamic oil return bypass type electric control oil injector with hydraulic feedback comprises an oil injector head 1, an oil injector body 11, a flow limiting valve assembly 3, an electromagnetic valve assembly 10, a tightening cap 9, a needle valve assembly 5 and a nozzle 6. The injector head 1 is connected with the injector body 11 in a matching way through threads and is sealed by a sealing ring 12 arranged on the injector body 11. The main oil inlet hole 13 on the injector head 1 is communicated with the pressure accumulation cavity 2 in the injector body 11. Below the injector body 11, there are a solenoid valve assembly 10, a nozzle 6 and a needle valve assembly 5, which are assembled and connected by a locking cap 9. The flow limiting valve component 3 is arranged in the oil injector body 11 and mainly comprises a retainer ring 14, a limiting spring seat 25, a damping spring 15, a flow limiting piston 16, a ball valve 23, a supporting slide block 18, a ball valve return spring 19 and a ball valve return spring seat 21. The flow-limiting piston 16 is provided with a flow-limiting hole 17 and a piston blind hole 24, and the supporting slide block 18 is provided with an axial central through hole 22 to ensure that fuel oil can pass through a lower oil path. An electromagnetic valve assembly 10 is arranged between the bottom of the oil injector body 11 and the upper part of the nozzle 6, and mainly structurally comprises an electromagnetic valve return spring 26, an electromagnetic valve return spring seat 39, a coil 27, an electromagnet 38, an armature 37, a valve seat 28, an intermediate block 34 and a balance valve rod 36. The armature 37 and balance valve stem 36 combination are placed in the valve seat 28 and the oil inlet orifice 29 is machined into the valve seat 28. The intermediate block 34 is internally processed with a hydraulic feedback oil passage 31, an oil return hole 32, an intermediate oil passage 33, an intermediate orifice 35, and the like. Below the solenoid valve assembly 10 is a needle valve assembly 5, which mainly comprises a control slider 46, a needle valve stop collar 44, a control slider return spring 41, a needle valve body 42, and a needle valve return spring 43. The control slider 46 is arranged in the control cavity 45 and is provided with a control slider through hole 47 and the bypass oil passage 40.
Fig. 1 is a schematic view of the overall structure of a fuel injector according to the present invention. A main oil inlet hole 13 is processed on the injector head 1, and high-pressure fuel oil conveyed by a high-pressure oil pipe enters the inside of the injector through the main oil inlet hole 13. The injector head 1 and the injector body 11 are assembled through threads, and a sealing ring 12 is arranged between the injector head and the injector body for sealing. The main oil inlet hole 13 communicates with the pressure accumulation chamber 2. The fuel in the accumulator chamber 2 will pass down through the restrictor valve assembly 3. After flowing out of the flow limiting valve assembly 3, the fuel enters the control cavity 45 and the oil containing groove 8 through the descending high-pressure oil way 4. The solenoid valve assembly 10 is arranged between the lower part of the injector body 11 and the needle valve assembly 5. The lifting and seating of the armature 37 and the balance valve stem 36 is controlled by electromagnetic forces within the solenoid operated valve assembly 10. When the balance valve rod 36 is lifted upwards, the oil return hole 32 is opened, and the fuel in the control cavity 45 flows through the control slider through hole 47, the intermediate oil passage 33 and the intermediate throttle hole 35 and is discharged through the oil return hole 32. The fuel pressure in the control chamber 45 decreases and forms a fuel pressure difference with the oil groove 8, so that the needle valve body 42 is lifted against the spring pre-tightening force of the needle valve return spring 43 and the oil injection starts. At this time, the needle valve body 42 is limited by the needle valve limiting sleeve 44. Due to the two-stage throttling action of the control slider through hole 47 and the intermediate throttling hole 35, the fuel pressure of the intermediate oil passage 33 does not drop rapidly, so that the dropping speed of the fuel pressure of the control chamber 45 is slowed down. In the oil injection process, high-pressure fuel oil always enters the oil cavity 30 formed by the valve seat 28 and the balance valve rod 36 through the hydraulic feedback oil passage 31, the oil drainage rate of the oil cavity 30 and the control cavity 45 is slowed down, the pressure drop of the control cavity 45 at the initial oil injection stage is further reduced and slowed down, and the generation of nitrogen oxides is reduced. When the balance valve rod 36 is seated downwards, the oil return hole 32 is closed, fuel oil enters the control cavity 45 through the oil inlet throttling hole 29 and flows through the balance valve rod 36, the middle throttling hole 35, the middle oil passage 33, the control slider through hole 47 and the bypass oil passage 40, oil is also fed through the hydraulic feedback oil passage 31, oil pressure is built in the control cavity 45, the needle valve body 42 is seated under the action of the spring pre-tightening force of the needle valve return spring 43, and the oil injection process is finished. meanwhile,base:Sub>A needle valve body 42 pressed bybase:Sub>A needle valve return spring 43 is placed in the nozzle 6, and as shown in fig. 5, an enlarged view ofbase:Sub>A sectionbase:Sub>A-base:Sub>A of the needle valve body 42 is shown. The arc-shaped surface of the needle valve body 42 can play a good role in guiding. And no static pressure difference exists in the needle valve component 5, so that the characteristic of no static leakage of the oil injector is ensured. The needle valve component 5 and the solenoid valve component 10 are placed in the tightening cap 9 and are fastened with the oil injector body 11 through threads.
Fig. 2 is a schematic view of a portion of a constrictor valve assembly of the present invention. The flow limiting valve assembly 3 mainly comprises a retainer ring 14, a limiting spring seat 25, a damping spring 15, a flow limiting piston 16, a ball valve 23, a supporting slider 18, a ball valve return spring 19, a ball valve return spring seat 21 and the like. The whole flow limiting valve assembly 3 is arranged inside the oil injector body 11 through the pressure accumulation cavity 2 and is limited by the check ring 14. The limiting spring seat 25 cooperates with the retainer ring 14 to act as a spring seat for the damping spring 15 on the one hand and to limit the maximum displacement of the limiting piston 16 on the other hand. Under the spring pre-tightening force of the damping spring 15 and the ball valve return spring 19, the ball valve 23 is matched with the lower end face of the flow limiting piston 16 and the upper end face of the supporting slide block 18. The ball return spring seat 21 is pressed against the bottom by the spring force of the ball return spring 19, and its upper variable cross-section is a seating surface of the ball 23. The fuel enters the blind piston hole 24 in the flow-limiting piston 16 from the pressure accumulation chamber 2 and then enters the axial central through hole 22 of the supporting slide block 18 through the flow-limiting hole 17. The fuel oil flowing out from the axial central through hole 22 passes through the descending high-pressure oil passage 4 to the lower oil passage. When the oil injector injects oil normally, the nozzle 7 injects the fuel oil, and the pressure of the fuel oil in the transition oil cavity 20 is reduced. Due to the throttling effect of the throttling hole 17 on fuel, the pressure of the fuel in the piston blind hole 24 in the throttling piston 16 and the pressure accumulation cavity 2 is higher, and pressure difference is formed between the pressure accumulation cavity and the transition oil cavity 20, so that the throttling piston 16, the ball valve 23 and the supporting slide block 18 are displaced downwards, fuel sprayed by the fuel injector is compensated, and the ball valve 23 cannot be seated on the ball valve reset spring seat 21. When oil injection is finished, the pressure difference between the upper part and the lower part of the flow-limiting piston 16 is gradually reduced along with the flow of fuel through the flow-limiting hole 17, and the flow-limiting piston 16, the ball valve 23 and the supporting slide block 18 are restored to the original positions under the action of the return spring force of the ball valve. When the fuel injector continuously injects fuel, the mass of the fuel flowing out exceeds the threshold value, and the fuel injector is in an abnormal working state, because the flow of the fuel injected by the injection hole 7 is large and the flow speed is high, the oil pressure of the transition oil cavity 20 below the flow limiting piston 16 is rapidly reduced, and an up-down pressure difference is formed, so that the flow limiting piston 16 presses the ball valve 23 to be seated on the ball valve reset spring seat 21, and the fuel is prevented from flowing. Due to the lack of fuel supply, the injector stops operating, preventing continuation of abnormal fuel injection.
Fig. 3 is a partial structural schematic diagram of the solenoid valve assembly of the present invention. The solenoid valve assembly 10 mainly includes a solenoid valve return spring 26, a solenoid valve return spring seat 39, a coil 27, an electromagnet 38, an armature 37, a valve seat 28, an intermediate block 34, a balance valve rod 36, and the like. The solenoid valve return spring seat 39, the solenoid valve return spring 26, the coil 27 and the electromagnet 38 are embedded inside the injector body 11, wherein the solenoid valve return spring seat 39 is fastened to the topmost end of the solenoid valve by a screw thread. Between the solenoid valve return spring seat 39 and the armature 37 is the solenoid valve return spring 26. The armature 37 and the balancing valve rod 36 are placed inside the valve seat 28 below the injector body 11. The component that engages the valve seat 28 below is an intermediate block 34. The whole electromagnetic valve adopts a two-position three-way valve form. When the injector starts to inject fuel, the coil 27 of the solenoid valve is energized to form a magnetic circuit with the electromagnet 38 and the armature 37, and electromagnetic force is generated to attract the balance valve rod 36 to move upwards, so that the oil return hole 32 in the middle block 34 is opened and the oil inlet throttle hole 29 is blocked. At this time, the fuel in the control chamber 45 returns to the fuel tank through the intermediate oil passage 33, the intermediate orifice 35, and the return hole 32, the pressure in the control chamber 45 decreases, the upper surface of the needle valve body 42 is pressurized, and a pressure difference is formed between the upper surface of the needle valve body and the pressure of the fuel in the fuel tank 8. The needle valve body 42 is lifted upwards, and the spray hole 7 is opened to spray oil. When the injector stops injecting fuel, the armature 37 and the balance valve rod 36 are tightly combined into a whole, so that they are pressed on the intermediate block 34 under the spring pre-load of the solenoid valve return spring 26 and block the oil return hole 32. At the same time, the balance valve stem 36 opens an oil path from the inlet orifice 29, the intermediate orifice 35, and the intermediate oil passage 33 to the control chamber 45.
FIG. 4 is a schematic view of a portion of a needle valve assembly according to the present invention. The needle valve assembly 5 basically includes a control slider 46, a control slider return spring 41, a needle valve stop 44, a needle valve body 42 and a needle valve return spring 43. The control slide 46 is placed inside the control chamber 45 and is lifted by the control slide return spring 41 and abuts against the lower end face of the intermediate block 34. A control slider through hole 47 and the bypass oil passage 40 are machined in the control slider 46. When the oil injection starts, due to the two-stage throttling action of the middle throttling hole 35 on the middle block 34 and the control slide block through hole 47, the pressure of the fuel oil in the control cavity 45 drops more slowly than that of the normal oil injector, and the high-pressure fuel oil enters through the hydraulic feedback oil passage 31, so that the effect is further enhanced, and the aim of reducing the emission of nitrogen oxides is fulfilled. When oil injection is finished, because the fuel pressure on the upper end face of the control slider 46 is higher than that on the lower end face, the control slider 46 can overcome the spring pre-tightening force of the control slider return spring 41 to displace downwards and open the bypass oil passage 40, so that the fuel pressure in the control cavity 45 is quickly established, and the seating response of the needle valve is improved. At this time, the hydraulic feedback oil passage 31 becomes another oil inlet oil passage, and also has an effect of accelerating seating of the needle valve. As fuel enters the control chamber 45, the oil pressure on the upper and lower end faces of the control slider 46 tends to be uniform. The control slider 46 is reset by the control slider return spring 41.
According to the working process, in the oil injection process of the micro-dynamic oil return bypass type electric control oil injector with hydraulic feedback, a two-position three-way valve is adopted, so that the dynamic oil return amount is greatly reduced, and the micro-dynamic oil return function is realized. The structure of the control slide block 46 arranged in the control cavity 45 and the hydraulic feedback oil channel 31 in the middle block 34 ensure the characteristics of low oil injection speed in the initial stage of injection and quick oil cut-off after the end of oil injection. The whole oil injection process is controlled by an electromagnetic valve, and the electromagnetic force is utilized to drive the balance valve rod 36 to move, so that the requirements of high response speed and high control precision in the oil injection process are met. The limiting valve component 3 is arranged in the oil sprayer body 11, so that the abnormal oil spraying state is prevented from being continuously carried out, and the stability of the working process is ensured. When the common rail pressure storage cavity is applied to a common rail system, the pressure storage cavity 2 can effectively reduce the pressure fluctuation of the common rail under the large-oil-quantity injection state, so that the phenomenon that the uniformity and the stability of the oil injection process of each cylinder are reduced is reduced.
Claims (3)
1. The utility model provides a take fine motion attitude oil return by-pass formula automatically controlled sprayer of hydraulic feedback which characterized by: 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 slide block, wherein the limiting spring seat, the flow limiting piston and the ball valve reset spring seat are arranged from top to bottom;
the electromagnetic valve assembly 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 upper cavity is formed between the middle part of the balance valve rod and the valve seat, an oil cavity is formed between the lower end part of the balance valve rod, the valve seat and the intermediate block, an oil inlet throttling hole is arranged in the valve seat, an oil return hole, the intermediate oil passage, the intermediate throttling hole and a hydraulic feedback oil passage are arranged in the intermediate block, the oil inlet throttling hole is communicated with the balance valve rod upper cavity and the intermediate oil passage respectively, the hydraulic feedback oil passage is directly communicated with the oil cavity, and the oil return hole is communicated or disconnected with the intermediate oil passage and the oil tank under the control of the balance valve rod;
the needle valve assembly comprises a needle valve limiting sleeve, a control slide block and a needle valve body, wherein the control slide block is positioned in the needle valve limiting sleeve, 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 a nozzle, a control cavity is formed between the control slide block and the needle valve body, a control slide block return spring is arranged in the control cavity, a bulge part is arranged in the middle of the needle valve body, the needle valve return spring is arranged between the bulge part and the needle valve limiting sleeve above the bulge part, a middle cavity is arranged on the upper end face of the control slide block, a control slide block through hole and a bypass oil path are arranged in the control slide block, the control slide block through hole is respectively communicated with the middle cavity and the control cavity, the bypass oil path is communicated with the control cavity, an oil containing groove is formed between the needle valve body and the nozzle, and a spray hole is arranged at the end part of the nozzle;
the upper end of the downlink high-pressure oil way is communicated with a transition oil cavity and is communicated with an oil containing groove through an oil sprayer body, a valve seat, a middle block and a nozzle, and an oil inlet throttling hole and a hydraulic feedback oil way are respectively communicated with the downlink high-pressure oil way;
when the spray hole sprays oil, the fuel pressure of the transition oil cavity is reduced, the flow-limiting piston, the ball valve and the supporting slide block integrally move 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 slide block are integrally restored to the initial positions under the action of the ball valve return spring.
2. The micro-dynamic oil return bypass type electric control oil injector with hydraulic feedback as claimed in claim 1, is characterized in that: when the coil is electrified, the balance valve rod moves upwards, the upper cavity of the balance valve rod is in a disconnected state with the oil cavity, the oil return hole is in a communicated state with the oil tank, fuel oil in the control cavity returns to the oil tank through the middle oil duct, the middle throttling hole and the oil return hole, the needle valve body is lifted upwards, and the spraying hole is opened to spray oil; 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 upper cavity of the balance valve rod is communicated with the oil cavity, the oil return hole is disconnected with the oil tank, and meanwhile, fuel oil in the downlink high-pressure oil way enters the control cavity through the oil inlet throttling hole, the upper cavity of the balance valve rod, the oil cavity, the middle throttling hole, the middle oil duct and the middle cavity on one hand and enters the control cavity through the hydraulic feedback oil duct, the oil cavity, the middle oil duct and the middle cavity on the other hand.
3. The micro-dynamic oil return bypass type electric control oil injector with hydraulic feedback as claimed in claim 1 or 2, is characterized in that: when the spray hole stops spraying oil, the fuel pressure of the upper end face of the control slide block is higher than that of the lower end face of the control slide block, the control slide block overcomes the pre-tightening force of the return spring of the control slide block to move downwards, the bypass oil way is opened, and the control slide block returns to the initial position under the action force of the return spring of the control slide block along with the fuel entering the control cavity.
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| CN201710034962.2A CN106762286B (en) | 2017-01-18 | 2017-01-18 | Micro-dynamic oil return bypass type electric control oil injector with hydraulic feedback |
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| CN201710034962.2A CN106762286B (en) | 2017-01-18 | 2017-01-18 | Micro-dynamic oil return bypass type electric control oil injector with hydraulic feedback |
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| CN106762286B true CN106762286B (en) | 2023-03-21 |
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| CN108443040A (en) * | 2018-05-25 | 2018-08-24 | 李玉龙 | Medium and heavy-duty engines monomer crosspointer valve twin-jet nozzle high pressure common rail injector |
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| DE19963934A1 (en) * | 1999-12-31 | 2001-07-12 | Bosch Gmbh Robert | Control valve for an injector for a fuel injection system with an actuator guided by a tappet |
| ES2344695T3 (en) * | 2001-07-03 | 2010-09-03 | Crt Common Rail Technologies Ag | FUEL INJECTION VALVE FOR INTERNAL COMBUSTION ENGINES. |
| DE102006049883A1 (en) * | 2006-10-23 | 2008-04-24 | Robert Bosch Gmbh | Fuel injecting valve for internal-combustion engine, has housing with inlet connected with side of draining throttle over inlet throttle, where side is turned away from chamber that is connected with inlet over another inlet throttle |
| DE102009027504A1 (en) * | 2009-07-07 | 2011-01-20 | Robert Bosch Gmbh | Fuel injector for an internal combustion engine |
| CN104018966B (en) * | 2014-05-29 | 2016-06-29 | 哈尔滨工程大学 | Pressure accumulation current-limiting type electromagnetic control oil sprayer |
| CN104018964B (en) * | 2014-05-29 | 2016-05-04 | 哈尔滨工程大学 | Pressure accumulation current-limiting type piezoelectric control fuel injector |
| CN104533683B (en) * | 2014-11-26 | 2017-01-25 | 中国北方发动机研究所(天津) | High-pressure co-rail oil sprayer sliding valve structure |
| CN204458154U (en) * | 2015-03-09 | 2015-07-08 | 龙口龙泵燃油喷射有限公司 | A kind of pressure balance type common-rail injector |
| CN104912707A (en) * | 2015-06-23 | 2015-09-16 | 哈尔滨工程大学 | Bivalve-cooperated electromagnetic control oil spray device |
| CN206352541U (en) * | 2017-01-18 | 2017-07-25 | 哈尔滨工程大学 | A kind of On Fluctuations oil return bypass type electric-controlled fuel injector with hydraulic feedback |
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