CN111502880A - Electric control high-pressure fuel injection device capable of preventing dynamic leakage - Google Patents
Electric control high-pressure fuel injection device capable of preventing dynamic leakage Download PDFInfo
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- CN111502880A CN111502880A CN202010188090.7A CN202010188090A CN111502880A CN 111502880 A CN111502880 A CN 111502880A CN 202010188090 A CN202010188090 A CN 202010188090A CN 111502880 A CN111502880 A CN 111502880A
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- 239000000446 fuel Substances 0.000 title claims abstract description 85
- 238000002347 injection Methods 0.000 title claims abstract description 82
- 239000007924 injection Substances 0.000 title claims abstract description 82
- 238000007789 sealing Methods 0.000 claims abstract description 31
- 238000004519 manufacturing process Methods 0.000 abstract description 3
- 239000003921 oil Substances 0.000 description 66
- 239000000295 fuel oil Substances 0.000 description 12
- 230000007547 defect Effects 0.000 description 5
- 238000013016 damping Methods 0.000 description 3
- 238000003754 machining Methods 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 230000008569 process Effects 0.000 description 3
- 230000007704 transition Effects 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 238000004458 analytical method Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000003111 delayed effect Effects 0.000 description 1
- 239000010710 diesel engine oil Substances 0.000 description 1
- 238000009826 distribution Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000003344 environmental pollutant Substances 0.000 description 1
- 238000001914 filtration Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 231100000719 pollutant Toxicity 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 239000007921 spray Substances 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 238000003860 storage Methods 0.000 description 1
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Classifications
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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
- F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for valve bodies
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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
Abstract
The invention discloses an electric control high-pressure fuel injection device for preventing dynamic leakage, which is characterized in that: a piston sleeve seat (26) is arranged between the lower plane of the valve seat (11) and the piston sleeve (12), the piston sleeve seat (26) is cylindrical, a taper hole is formed at the bottom of the piston sleeve seat, a step hole is formed in the upper surface of the taper hole, a small round hole is formed in the upper surface of the step hole, and the upper plane of the piston sleeve seat (26) is abutted against the lower plane of the valve seat (11); the upper end of the piston sleeve (12) is provided with a spherical surface in a segment shape which is matched with a taper hole at the bottom of the piston sleeve seat (26) to form a hinged line sealing structure. The piston sleeve (12) can freely rotate around the sphere center of the piston sleeve to compensate the shape and position errors of the fuel injector body 13, the needle valve body 25 and the piston needle valve 27, and a leakage gap between the valve seat (11) and the piston sleeve seat (26) is eliminated, so that accurate injection is obtained, and meanwhile, the manufacturing cost is reduced.
Description
Technical Field
The invention relates to an electric control high-pressure fuel injection device, in particular to an electric control high-pressure fuel injection device which is mainly used for a high-pressure common rail oil supply system and prevents dynamic leakage.
Background
In the prior art, the electric control oil supply systems adopted by diesel engines, such as an electric control monoblock pump, an electric control pump nozzle, an electric control distribution pump and the like, control of oil injection timing and oil injection quantity parameters is realized by controlling an oil pump. The injection pressure of these systems is difficult to regulate due to the influence of the engine speed. The electric control high-pressure common rail oil supply system is the most advanced oil supply system of the diesel engine at present. Compared with the prior electric control system, the electric control high-pressure common rail oil supply system has three main characteristics. Firstly, the system can control not only the high-pressure oil pump but also the oil injector, and can realize multiple injections in one working cycle according to the requirements of combustion efficiency, pollutant discharge, comfort and the like; secondly, the electric control high-pressure common rail oil supply system has a common oil storage volume, namely a common high-pressure oil rail, which is called a common rail for short, a high-pressure oil pump compresses fuel oil and then sends the compressed fuel oil into the volume of the common high-pressure oil rail, and then the common high-pressure oil rail conveys the high-pressure fuel oil to the electric control fuel oil injection devices of all corresponding cylinders, so that the electric control fuel oil injection devices of all the cylinders inject the fuel oil under the same injection pressure, and the accuracy and the consistency of the fuel oil injection quantity and the injection pressure of all the cylinders are ensured; meanwhile, based on the technology of controlling the oil inlet amount of the high-pressure oil pump, the injection pressure of the system can be decoupled with the rotating speed of the engine, so that the injection pressure of the system is irrelevant to the rotating speed of the engine, and the electric control high-pressure common rail oil supply system can provide the optimal injection pressure no matter what working condition the engine works under without being influenced by the rotating speed of the engine. The electric control high-pressure common rail oil supply system has the characteristics that any oil supply system adopted on the diesel engine in the past does not have, so the electric control high-pressure common rail oil supply system becomes the first choice of the existing diesel engine oil supply system. The electric control high-pressure common rail oil supply system mainly comprises an electric control high-pressure oil pump, a high-pressure oil rail (namely a common rail), an electric control high-pressure fuel injection device, a controller (namely an electric control unit ECU), a sensor, control software and the like, wherein the control software written according to the working condition of an engine is stored in the ECU, and the intention of a driver and real-time working condition parameters of the engine detected by the sensor are as follows when the engine works: the information of the rotating speed, the load, the temperature, the pressure and the like is input into the ECU, and then the command is sent to the electric control high-pressure oil pump and the electric control high-pressure fuel injection device according to the operation result of the ECU so as to control the oil quantity and the pressure output by the electric control high-pressure oil pump, the injection starting time of the electric control high-pressure fuel injection device, the injection duration, the injection frequency in one cycle and the like. Furthermore, the ECU may also participate in the operation management of the automobile.
The electric control high-pressure fuel injection device is an actuator of an electric control high-pressure common rail oil supply system, is the most important, the most complex and the highest technical difficulty component in the electric control high-pressure common rail oil supply system, and comprises the following components: the fuel injection device comprises a front control part, a hydraulic amplifying part, a fuel injection part, a fuel injector body, a fuel inlet assembly and other parts, wherein the front control part comprises an electromagnet, a control valve assembly and the like, the hydraulic amplifying part comprises a piston sleeve, a piston and the like, the fuel injection part comprises a needle valve, a needle valve body and the like, the fuel injector body provides high-pressure and low-pressure fuel flow channels for the electronic control fuel injection device, and functions of filtering, sealing, fixedly connecting and the like of the fuel. FIG. 3 shows an electric control high pressure common rail fuel injection device in the prior art, which comprises an injector body 13, wherein the injector body 13 is provided with a central cavity with multiple diameters, a valve seat 11 and a valve rod stroke adjusting pad 8 are sequentially stacked on a step plane on the upper part of the cavity, a fastening screw sleeve 7 is fixedly connected on the injector body 13, the upper part of the valve seat 11 is provided with a taper hole, an oil outlet metering hole 111 is connected with the lower end of the taper hole, the lower end of the oil outlet metering hole 111 penetrates through the bottom surface of the valve seat 11, the taper hole on the upper part of the valve seat 11 is matched with a sealing ball 10 to form a linear sealing structure, a sealing ball seat 9 and a valve rod 3 are sequentially stacked on the sealing ball 10, a fastening screw sleeve 28 fixedly connects an electromagnet 1 and the injector body 13, an electromagnet spring 2 is supported between the shoulder of the valve rod 3 and the step plane of the cavity of the electromagnet 1, the upper part of the valve rod 3 is, the armature 5 is concentrically sleeved on the valve rod 3, and the damping spring 6 is supported between the armature 5 and the fastening threaded sleeve 7 so that the upper end face of the armature 5 abuts against the bottom plane of the opening gasket 4; the nozzle tip fastening screw 24 fixedly connects the needle valve body 25 to the lower end plane of the injector body 13. A middle hole is concentrically formed in the needle valve body 25, a taper hole is formed at the lower end of the middle hole and connected with the middle hole, a pressure chamber 251 with a bag-shaped center hole is formed at the lower end of the taper hole, one end of a radially distributed oil injection hole 252 is communicated with the pressure chamber 251, and the other end of the oil injection hole is communicated with the outside of the needle valve body 25; the piston 17 is inserted in the central hole of the piston sleeve 12, the needle valve 19 is inserted in the central hole of the needle valve body 25, the connecting rod sleeve 18 fixedly connects the piston 17 and the needle valve 19 together, a cone at the lower end of the needle valve 19 and a cone hole at the lower end of the needle valve body 25 form an openable sealing strip, a straight groove which is formed on the diameter of the needle valve 17 and used for conveying high-pressure fuel oil in the high-pressure oil containing cavity 132 to the sealing strip is formed, and the high-pressure fuel oil can pass through the sealing strips of the needle valve 19 and the needle valve body 25 after the needle valve 19 is opened, flow into the pressure chamber 251 and is.
The electric control high-pressure fuel injection device in the prior art has the following defects: reducing the efficiency of the system. The shape and position errors generated in the manufacturing process of parts are inevitable, and the errors mainly comprise that the center hole of the needle valve body 25 cannot be absolutely vertical to the plane of the upper end of the needle valve body, the plane of the lower end of the fuel injector body 13 cannot be absolutely parallel to the plane of the central cavity of the upper end of the fuel injector body, and the center hole of the piston sleeve 12 cannot be absolutely vertical to the plane of the upper end of the fuel injector body. Since the above-mentioned error is inevitable, the upper plane of the piston sleeve 12 cannot be completely fitted with the step plane of the valve seat 11, that is, a gap is inevitable between the upper plane of the piston sleeve 12 and the step plane of the valve seat 11, when the injection device injects oil, the electromagnet 1 is first energized, the electromagnet 1 drives the armature 5 to lift the valve rod 3 after being energized, at this time, the high-pressure fuel in the control chamber 113 flushes up the sealing ball 10, and the fuel in the control chamber 113 flows to the low-pressure region through the gap between the oil outlet metering hole 111, the tapered hole of the valve seat 11, and the sealing ball 10. Since the diameter of the oil inlet measuring hole 112 is smaller than that of the oil outlet measuring hole 111, the pressure in the control chamber is reduced, and since the outside of the piston sleeve 12 is immersed in the high-pressure oil accommodating chamber 132 in the center of the injector body 13, the high-pressure oil accommodating chamber 132 is still high in pressure, so that a pressure difference exists between the control chamber 113 and the high-pressure oil accommodating chamber 132, and high-pressure fuel oil in the high-pressure oil accommodating chamber 132 is leaked into the control chamber 113 through a gap between the upper plane of the piston sleeve 12 and the step plane of the valve seat 11 under the driving of the pressure difference, so that the fuel oil pressure in the control chamber 113 is increased. The fuel pressure in the control chamber 113 determines whether the piston 17 is raised or lowered for opening or closing the injection. The presence of said dynamic leaks disturbs the switching behaviour of the injection device by changing the state of the control chamber 113. In order not to affect the injection law of the injection device, the excess fuel that dynamically leaks into the control chamber 113 must be discharged by increasing the diameter of the fuel outlet metering orifice. Resulting in a reduction in the efficiency of the system.
The electric control high-pressure fuel injection device in the prior art has the following defects: affecting the accuracy of the "injection timing" and the injected quantity of the engine. The fuel pressure in the control chamber 113 is originally determined by the fuel inlet metering hole 112 and the fuel outlet metering hole 111, but due to the existence of the gap leakage between the upper plane of the piston sleeve 12 and the step plane of the valve seat 11, a channel entering the control chamber 113 is added, so that the fuel pressure in the control chamber 113 is slowly reduced, and the opening delay time in the transitional process of opening the injection is increased as a result. When the gap is too large, it may even result in the spray device not being able to open. The phase of the timing at which the injection starts corresponds to the "injection timing" of the engine, and if the opening delay time is increased, it means that the timing at which the injection starts is delayed. During the injection closing transition, due to the gap leakage between the upper plane of the piston sleeve 12 and the stepped plane of the valve seat 11, the high-pressure fuel in the high-pressure fuel accommodating chamber 132 can enter the control chamber 113 from the gap to accelerate the pressure rise in the control chamber 113, so that the closing delay time of the injection closing transition is reduced. Further, as a result of the above analysis, the opening delay time of the injection device is lengthened and the closing delay time is shortened due to the existence of the gap leakage between the upper plane of the piston sleeve 12 and the step plane of the valve seat 11, and the result of the late opening and early closing means that the injection duration from the opening to the closing is shortened, and the fuel injection duration is shortened, meaning that the fuel injection amount is decreased. Therefore, the accuracy of the injection quantity of the injection device is also affected.
The prior art electric control high-pressure fuel injection device has the following defects: affecting the uniformity of the performance of the jetting device. The influence of the gap leakage is not only as described above, but also may cause the uncontrollable property of the "fuel injection timing" and the fuel injection amount due to the machining error, and may seriously affect the consistency of the engine performance, and if the difference between the "fuel injection timing" and the fuel injection amount exceeds the standard requirement due to the different leakage amount of the injection device of each cylinder in an engine, the performance of the engine in terms of fuel consumption, noise, vibration, emission, etc. may be affected, which is unacceptable. In an extreme case, if a large amount of high-pressure fuel leaks into the control chamber 113 from the gap between the upper end plane of the piston sleeve 12 and the step plane of the valve seat 11, there is a possibility that the pressure of the fuel in the control chamber 113 cannot be lowered to the critical pressure required to lift the needle 19, at which time the needle 19 cannot be lifted, and the electronically controlled high-pressure fuel injection device loses the injection function, which is absolutely intolerable.
The prior art electric control high-pressure fuel injection device has the following defects: the precision requirement is high, and the processing cost is improved. Because the shape and position errors generated in the manufacturing process of parts are inevitable, the errors of the perpendicularity of the central hole of the needle valve body 25 and the upper end plane thereof, the parallelism of the lower end plane of the fuel injector body 13 and the upper end central cavity plane thereof and the perpendicularity of the central hole of the piston sleeve 12 and the upper end plane are inevitable, so that the upper plane of the piston sleeve 12 cannot be completely attached to the step plane of the valve seat 11. In order to bring the upper plane of the piston sleeve 12 into close contact with the step plane of the valve seat 11, the dynamic leakage is reduced only by improving the machining accuracy of the above-mentioned components, which means an increase in cost.
Disclosure of Invention
The invention aims to overcome the defect of dynamic leakage of an electric control high-pressure fuel injection device in the prior art, and aims to provide the electric control high-pressure fuel injection device capable of preventing dynamic leakage, which can eliminate the influence of shape and position errors caused by part machining on leakage.
The invention adopts the technical scheme that an electric control high-pressure fuel injection device for preventing dynamic leakage is characterized in that: a piston sleeve seat 26 is arranged between the lower plane of the valve seat 11 and the piston sleeve 12, the piston sleeve seat 26 is cylindrical, a taper hole is formed at the bottom of the piston sleeve seat 26, a step hole is formed in the upper surface of the taper hole, a small round hole is formed in the upper surface of the step hole, and the upper plane of the piston sleeve seat 26 is abutted against the lower plane of the valve seat 11; the upper end of the piston sleeve 12 is provided with a spherical surface in a segment shape which is matched with a taper hole at the bottom of the piston sleeve seat 26 to form a hinged line sealing structure.
Further, a piston needle valve 27, which is integrally manufactured by a piston and a needle valve, is inserted into the piston sleeve 12.
Further, a vertical hole 272 is formed at the center of the upper end of the piston needle 27, and a cross hole 271 is formed at the lower end of the vertical hole 272 to communicate with the vertical hole 272, and both ends of the cross hole 271 of the piston needle 27 are flattened to communicate the cross hole 271 with the control chamber 113, so that the fuel in the control chamber 113 can flow out of the control chamber 113 to a low pressure region through the cross hole 271 and the vertical hole 272 when the top of the piston needle 27 moves to contact the lower surface of the piston sleeve seat 26 to seal the center hole of the valve seat 11.
Compared with the prior art, the electric control high-pressure fuel injection device has the following beneficial effects: because the linear sealing structure in the form of spherical hinge joint of the piston sleeve 12 and the piston sleeve seat 26 is adopted, the piston sleeve 12 can freely rotate around the self spherical center, errors such as parallelism between the plane of the step of the middle hole of the fuel injector body 13 and the bottom plane of the fuel injector body 13, verticality between the middle hole of the needle valve body 25 and the upper plane thereof, straightness of the piston needle valve 27 and the like can be compensated through the free rotation of the piston sleeve 12 around the self spherical center, possible leakage gaps between the lower plane of the valve seat 11 and the upper plane of the piston sleeve seat 26 can be eliminated in the dynamic opening and closing process, and accordingly high-pressure fuel can be prevented from flowing into the control chamber 113 during injection, the pressure controllability in the control chamber 113 is greatly improved, and accurate injection opening delay time, closing delay time and accurate injection quantity can be obtained. Furthermore, the adoption of the spherical hinged line sealing structure of the piston sleeve 12 and the piston sleeve seat 26 simplifies the process difficulty of the parts forming the spherical hinged line sealing structure, thereby greatly reducing the cost of the electric control injection device.
Drawings
Fig. 1 is a schematic structural view of an electronically controlled high-pressure fuel injection apparatus for preventing dynamic leakage according to the present invention.
Fig. 2 is a partially enlarged schematic view of fig. 1.
Fig. 3 is a schematic view of a high-pressure fuel injection device according to the prior art.
In the figure: 1 electromagnet, 2 electromagnet springs, 3 valve rods, 4 split washers, 5 armatures, 6 damping springs, 7 fastening screw sleeves, 8 valve rod stroke adjusting gaskets, 9 sealing ball seats, 10 sealing balls, 11 valve seats, 12 piston sleeves, 13 fuel injector bodies, 14 needle valve springs, 15 adjusting gaskets, 16 split check rings, 17 pistons, 18 extension rod sleeves, 19 needle valves, 20 electromagnet sealing rings, 21 fuel inlet bolt sealing gaskets, 22 fuel inlet filter cores, 23 fuel inlet bolts, 24 fuel nozzle fastening screw sleeves, 25 needle valve bodies, 26 piston sleeve seats, 27 piston needle valves, 28 fastening screw sleeves, 101 low-pressure oil outlets, 701 low-pressure oil through holes, 111 oil outlet metering holes, 112 fuel inlet metering holes, 113 control chambers, 114 transverse grooves, 131 high-pressure oil inlet holes, 132 high-pressure oil containing chambers, 251 pressure chambers, 252 oil injection holes, 271 transverse holes and 272 vertical holes.
Detailed Description
For further explanation of the principles and construction of the present invention, reference will now be made in detail to the embodiments of the present invention, examples of which are illustrated in the accompanying drawings.
Fig. 1 and 2 show an embodiment of an electronically controlled high-pressure fuel injection apparatus for preventing dynamic leakage according to the present invention, characterized in that: a piston sleeve seat 26 is arranged between the lower plane of the valve seat 11 and the piston sleeve 12, the piston sleeve seat 26 is cylindrical, a taper hole is formed at the bottom of the piston sleeve seat 26, a step hole is formed in the upper surface of the taper hole, a small round hole is formed in the upper surface of the step hole, and the upper plane of the piston sleeve seat 26 is abutted against the lower plane of the valve seat 11; the upper end of the piston sleeve 12 is provided with a spherical surface in a segment shape which is matched with a taper hole at the bottom of the piston sleeve seat 26 to form a hinged line sealing structure.
Further, a piston needle valve 27, which is integrally manufactured by a piston and a needle valve, is inserted into the piston sleeve 12.
Further, a vertical hole 272 is formed at the center of the upper end of the piston needle 27, and a cross hole 271 is formed at the lower end of the vertical hole 272 to communicate with the vertical hole 272, and both ends of the cross hole 271 of the piston needle 27 are flattened to communicate the cross hole 271 with the control chamber 113, so that the fuel in the control chamber 113 can flow out of the control chamber 113 to a low pressure region through the cross hole 271 and the vertical hole 272 when the top of the piston needle 27 moves to contact the lower surface of the piston sleeve seat 26 to seal the center hole of the valve seat 11.
Further, a valve seat 11 with a two-stage concentric cylinder with a thick upper part and a thin lower part is concentrically arranged on the plane of a central cavity of an oil injector body 13, the valve seat 11 and a valve rod stroke adjusting pad 8 are fixedly connected on the step plane of the central cavity of the oil injector body 13 by a fastening screw sleeve, the valve seat 11 is concentrically provided with a central hole, the middle upper part of the left side of the cylinder with a long and thin diameter of the valve seat 11 is provided with a transverse taper hole, the bottom of the taper hole is provided with a transverse oil inlet metering hole 112 communicated with the central hole of the valve seat 11, the upper part of the central hole of the valve seat 11 is provided with an oil outlet metering hole 111, the upper end of the oil outlet metering hole 111 is connected with a taper hole, a sealing ball 10, a sealing ball seat 9 and a valve rod 3 are concentrically arranged on the taper hole in sequence, an electromagnet spring 2 is concentrically sleeved on the upper shoulder of the, the valve rod is supported on the upper shoulder plane of the valve rod 3, the electromagnet 1 is fixedly connected to the upper part of the fuel injector body 13 by the concentric fastening threaded sleeve 28 on the electromagnet 1, and the electromagnet sealing ring 20 is arranged between the electromagnet 1 and the fuel injector body 13 to play a role in sealing low-pressure fuel and preventing leakage. A concentric annular groove is formed in the middle upper portion of the valve rod 3, the split washer 4 is clamped in the groove of the valve rod 3, the armature 5 is concentrically sleeved on the valve rod, and the damping spring 6 is concentrically supported between the fastening threaded sleeve 7 and the armature 5 so as to ensure that the upper plane of the armature 5 always abuts against the lower plane of the split washer 4 in a static state. The piston needle valve 27 is a part integrating two functions of a piston and a needle valve, the diameter part of the piston at the upper end of the piston needle valve 27 is concentrically arranged in an inner hole of the piston sleeve 12, the volume of the central cavity part of the piston sleeve 12, which is governed by the lower end of the piston sleeve seat 26 and the upper end of the piston needle valve 27, is called a control chamber 113, the outer parts of the piston sleeve seat 26 and the piston sleeve 12 are immersed in a high-pressure oil containing chamber 132 at the central part of the fuel injector body 13, a concentric annular groove is arranged at the middle part of the piston needle valve 27, a split retainer ring 16 is clamped in the groove, an adjusting pad 15 is concentrically arranged on the upper plane of the split retainer ring 16 for adjusting the precompression quantity of the needle valve spring 14, and the needle valve spring 14 is supported between the upper plane. The needle valve body 25 is concentrically and fixedly connected on the lower plane of the injector body by a nozzle fastening screw sleeve 24, a cone is manufactured at the lower end of the lower needle valve part of the piston needle valve 27, the cone body is matched with a conical hole of a central cavity at the lower part of the needle valve body 25 to form a switchable sealing strip, a bag-shaped central hole called a pressure chamber 251 is formed at the lower part of the conical hole of the needle valve body 25, one end of a fuel injection hole 252 which is distributed radially is communicated with the pressure chamber 251, the other end of the fuel injection hole leads to the outside of the needle valve body 25, an axially concave straight groove is manufactured on the diameter of the matching part of the piston needle valve 27 and the needle valve body 25, so that the diameter of the piston needle valve 27 and the needle valve body 25 can not only guide the up-and-down movement of the needle valve, but also provide a flow channel for the high-pressure fuel oil of the high-pressure fuel containing cavity 132 to flow into the pressure chamber during injection, and as long.
When in injection, firstly the electromagnet 1 is electrified, the armature 5 generates an upward electromagnetic force, the electromagnetic force overcomes the spring force of the electromagnet spring 2 and drives the valve rod 3 to move upwards, meanwhile, the fuel pressure in the control chamber 113 directly impacts the sealing ball 10 and drives the sealing ball seat 9 to leave the sealing conical surface of the valve seat 11 together, the fuel in the control chamber starts to flow to the low-pressure oil return tank through the oil outlet metering hole 111, the low-pressure oil through hole 701 and the low-pressure oil outlet hole 101, so that the fuel pressure in the control chamber 113 continuously drops, the downward acting force of the piston needle valve 27 is continuously reduced, on the other hand, the upward acting force of the fuel in the high-pressure oil containing chamber 132 on the piston needle valve 27 is not changed, when the downward combined force of the spring forces of the piston needle valve 27 and the needle valve spring 14 is smaller than the upward acting force of the fuel in the high-pressure oil containing chamber 132, the high-pressure oil accommodating chamber 132 is made to communicate with the pressure chamber 251, and high-pressure fuel from the high-pressure oil accommodating chamber 132 enters the pressure chamber 251 and is injected outward via the injection hole 252 communicating with the pressure chamber 251.
After the electromagnet 1 is powered off, the electromagnetic force disappears, the valve rod 3 moves downwards under the action of the electromagnet spring 2 to drive the sealing ball seat 9 and the sealing ball 10 to be seated, the tapered hole of the valve seat 11 is sealed, the outward flowing path of the oil outlet metering hole 111 is cut off, but at the moment, high-pressure fuel still flows into the control chamber 113 through the oil inlet metering hole 112, the pressure in the control chamber 113 is rapidly increased, the piston needle valve 27 is pushed to move downwards until the piston needle valve is closed, and oil injection is finished.
The above description is only a preferred embodiment of the present invention, and therefore should not be taken as limiting the scope of the invention, which is defined by the appended claims and their equivalents and modifications within the scope of the description.
Claims (3)
1. An automatically controlled high pressure fuel injection apparatus that prevents dynamic leakage, its characterized in that: a piston sleeve seat (26) is arranged between the lower plane of the valve seat (11) and the piston sleeve (12), the piston sleeve seat (26) is cylindrical, a taper hole is formed at the bottom of the piston sleeve seat, a step hole is formed in the upper surface of the taper hole, a small round hole is formed in the upper surface of the step hole, and the upper plane of the piston sleeve seat (26) is abutted against the lower plane of the valve seat (11); the upper end of the piston sleeve (12) is provided with a spherical surface in a segment shape which is matched with a taper hole at the bottom of the piston sleeve seat (26) to form a hinged line sealing structure.
2. An electronically controlled high pressure fuel injection apparatus against dynamic leakage as set forth in claim 1, wherein: and a piston needle valve (27) integrally manufactured by a piston and a needle valve is inserted in the piston sleeve (12).
3. An electronically controlled high pressure fuel injection apparatus against dynamic leakage as set forth in claim 2, wherein: a vertical hole 272 is formed in the center of the upper end of the piston needle 27, and a cross hole 271 is formed at the lower end of the vertical hole 272 to communicate with the vertical hole 272. both ends of the cross hole 271 of the piston needle 27 are flattened to communicate the cross hole 271 with the control chamber 113 so that the fuel in the control chamber 113 can flow out of the control chamber 113 to a low pressure region through the cross hole 271 and the vertical hole 272 when the top of the piston needle 27 moves to contact the lower surface of the piston sleeve seat 26 to seal the center hole of the valve seat 11.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010188090.7A CN111502880A (en) | 2020-03-17 | 2020-03-17 | Electric control high-pressure fuel injection device capable of preventing dynamic leakage |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010188090.7A CN111502880A (en) | 2020-03-17 | 2020-03-17 | Electric control high-pressure fuel injection device capable of preventing dynamic leakage |
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| Publication Number | Publication Date |
|---|---|
| CN111502880A true CN111502880A (en) | 2020-08-07 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202010188090.7A Pending CN111502880A (en) | 2020-03-17 | 2020-03-17 | Electric control high-pressure fuel injection device capable of preventing dynamic leakage |
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Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1650427A1 (en) * | 2004-10-23 | 2006-04-26 | Robert Bosch Gmbh | Fuel injection valve for internal combustion engines |
| DE102008001913A1 (en) * | 2008-05-21 | 2009-11-26 | Robert Bosch Gmbh | Fuel injector |
| CN103047062A (en) * | 2013-01-10 | 2013-04-17 | 无锡开普机械有限公司 | Electronic control oil sprayer for injection valve |
| EP2735725A1 (en) * | 2012-11-27 | 2014-05-28 | Robert Bosch Gmbh | Fuel injector valve for combustion engines |
| CN104314725A (en) * | 2014-09-25 | 2015-01-28 | 辽宁新风企业集团有限公司 | Middle hole pressure storage static leakage-free oil sprayer |
| CN105840376A (en) * | 2016-05-23 | 2016-08-10 | 辽阳新风科技有限公司 | No-static-leakage low-inertia oil sprayer module and oil sprayer |
-
2020
- 2020-03-17 CN CN202010188090.7A patent/CN111502880A/en active Pending
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1650427A1 (en) * | 2004-10-23 | 2006-04-26 | Robert Bosch Gmbh | Fuel injection valve for internal combustion engines |
| DE102008001913A1 (en) * | 2008-05-21 | 2009-11-26 | Robert Bosch Gmbh | Fuel injector |
| EP2735725A1 (en) * | 2012-11-27 | 2014-05-28 | Robert Bosch Gmbh | Fuel injector valve for combustion engines |
| DE102012221624A1 (en) * | 2012-11-27 | 2014-05-28 | Robert Bosch Gmbh | Fuel injection valve for internal combustion engines |
| CN103047062A (en) * | 2013-01-10 | 2013-04-17 | 无锡开普机械有限公司 | Electronic control oil sprayer for injection valve |
| CN104314725A (en) * | 2014-09-25 | 2015-01-28 | 辽宁新风企业集团有限公司 | Middle hole pressure storage static leakage-free oil sprayer |
| CN105840376A (en) * | 2016-05-23 | 2016-08-10 | 辽阳新风科技有限公司 | No-static-leakage low-inertia oil sprayer module and oil sprayer |
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