CN111237108B - High-pressure common rail oil sprayer capable of directly controlling oil spray nozzle switch - Google Patents
High-pressure common rail oil sprayer capable of directly controlling oil spray nozzle switch Download PDFInfo
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- CN111237108B CN111237108B CN202010169117.8A CN202010169117A CN111237108B CN 111237108 B CN111237108 B CN 111237108B CN 202010169117 A CN202010169117 A CN 202010169117A CN 111237108 B CN111237108 B CN 111237108B
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- oil
- needle valve
- oil sprayer
- armature
- pressure
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- 239000007921 spray Substances 0.000 title abstract description 20
- 239000000446 fuel Substances 0.000 claims abstract description 64
- 238000002347 injection Methods 0.000 claims abstract description 28
- 239000007924 injection Substances 0.000 claims abstract description 28
- 238000007789 sealing Methods 0.000 claims description 55
- 238000000034 method Methods 0.000 claims description 7
- 238000005507 spraying Methods 0.000 claims description 6
- 238000005461 lubrication Methods 0.000 claims description 4
- 230000000149 penetrating effect Effects 0.000 claims 1
- 239000003502 gasoline Substances 0.000 abstract description 6
- 230000004044 response Effects 0.000 abstract description 3
- 230000009286 beneficial effect Effects 0.000 abstract description 2
- 239000003921 oil Substances 0.000 description 97
- 238000002485 combustion reaction Methods 0.000 description 7
- 239000000295 fuel oil Substances 0.000 description 6
- 230000009471 action Effects 0.000 description 2
- 239000010779 crude oil Substances 0.000 description 2
- 239000013078 crystal Substances 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 239000002828 fuel tank Substances 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 230000003321 amplification Effects 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 230000008030 elimination Effects 0.000 description 1
- 238000003379 elimination reaction Methods 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 210000002445 nipple Anatomy 0.000 description 1
- 238000003199 nucleic acid amplification method Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
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
- 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
-
- 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
-
- 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
-
- 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
- F02M61/1873—Valve seats or member ends having circumferential grooves or ridges, e.g. toroidal
-
- 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
- F02M61/1886—Details of valve seats not covered by groups F02M61/1866 - F02M61/188
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
The invention relates to a high-pressure common rail oil sprayer capable of directly controlling an oil spray nozzle switch; the oil sprayer mainly comprises a binding post assembly, an oil sprayer body, an electromagnet component, an intermediate body and a pressure balance oil sprayer, wherein the binding post assembly is connected above the oil sprayer body through a screw sleeve, and the intermediate body and the pressure balance oil sprayer are connected below the oil sprayer body through the screw sleeve of the oil sprayer; the electromagnet component is arranged in the oil sprayer body and is connected with the control pressure balance oil sprayer so as to realize the direct control of the on and off of the pressure balance oil sprayer. The beneficial effects of the invention are as follows: the electromagnet is used for directly controlling the pressure balance type oil nozzle, so that the oil injection response time can be improved, the structure of the oil injector is greatly simplified, a plurality of slender high-pressure and low-pressure oil return holes are not provided, the processing difficulty of the oil injector body is greatly simplified, and the cost of the common rail oil injector is reduced. 2. The invention is also used in the fuel spray nozzle of gasoline injection, and can improve the fuel pressure of direct injection gasoline injection so as to improve the performance of the gasoline engine.
Description
Technical Field
The invention relates to a common rail fuel injector of a diesel engine, in particular to a common rail fuel injector capable of directly controlling a fuel injection nozzle to switch, and belongs to the field of fuel systems of internal combustion engines.
Background
The existing common rail fuel injector of the diesel engine has two modes of controlling the fuel injector to switch by an electromagnet and a piezoelectric crystal, wherein the two modes mainly control the switch of the fuel injector indirectly through a hydraulic servo valve, the structure is complex, the processing precision is high, meanwhile, the response speed is low, the current common rail fuel injector which directly controls the fuel injector to switch by the piezoelectric crystal is not through the hydraulic servo valve abroad, and the common rail fuel injector which directly controls the fuel injector to switch is used for the diesel engine by delta Fu corporation and Germany continental corporation in the United states.
The electromagnet controlled common rail injector has small volume, acting force of only 100 newtons and much smaller than thousands of newtons of control force of the piezocrystal, the current common closed type oil nozzle is shown in fig. 7, the needle valve guiding sealing diameter d1=4 mm, the conical surface sealing diameter d2=2 mm, and when the electromagnet is in a low pressure area, high pressure fuel oil acted on the needle valve of the oil nozzle can generate upward unbalanced hydraulic force. When the fuel injection pressure is 200Mpa, the upward unbalanced hydraulic pressure is up to 1800 newton above, the electromagnetic force of the electromagnet is far smaller than the unbalanced hydraulic pressure, the electromagnet can not directly pull the needle valve to control the switch of the fuel injection nozzle, and the electromagnetic force is converted into strong hydraulic pressure through the hydraulic servo valve to pull the needle valve to control the switch of the fuel injection nozzle. So at present, no high-pressure common rail fuel injector directly controlling the fuel spray nozzle switch by an electromagnet exists at home and abroad.
Fig. 7 shows a typical structure of a conventional common rail injector for diesel engine manufactured by BOSCH in germany. The upper end of the common rail oil sprayer is provided with an electromagnet 21, an armature 22 and a spherical two-position two-way servo valve 23, so that the high-pressure hydraulic pressure on a hydraulic piston 24 is quickly changed to low pressure or is quickly changed from low pressure to high pressure, thereby controlling the switch of an oil nozzle 25.
The patent 20081004087 of this company proposes a high-pressure common rail injector which directly controls the switch of the oil nozzle, and it puts the two-position two-way servo control valve at the upper end of the oil nozzle, but still controls the switch of the oil nozzle through the servo valve, not the real electromagnet directly controls the high-pressure common rail injector of the switch of the oil nozzle.
Disclosure of Invention
The invention aims at: providing a high-pressure common rail fuel injector directly controlling a fuel injection nozzle switch; the high-pressure common rail injector of diesel engine adopts the principle of equal sealing line to make the resultant force of high-pressure fuel oil pressure on the needle valve of the oil nozzle be zero, namely the closed type oil nozzle with balanced pressure and the electromagnet to directly switch the oil nozzle. Under the condition that the spray hole angle and the spray line direction of the oil spray nozzle are basically unchanged from those of the crude oil spray nozzle, the hydraulic pressure acted on the needle valve is balanced so that the electromagnetic valve has enough electromagnetic force to directly control the switch of the oil spray nozzle.
The invention is realized by the following technical scheme: the common rail oil sprayer is mainly composed of a wiring terminal assembly 1, an oil sprayer body 2, an electromagnet part, an intermediate body 7 and a pressure balance oil sprayer 6, wherein the wiring terminal assembly 1 is connected above the oil sprayer body 2 through a screw sleeve 19, and the intermediate body 7 and the pressure balance oil sprayer 6 are connected below the oil sprayer body 2 through the oil sprayer screw sleeve 9; the electromagnet component is arranged in the oil sprayer body 2 and is connected with the control pressure balance oil sprayer 6 to realize the direct control of the on-off of the pressure balance oil sprayer 6.
Compared with the prior art, the invention has the beneficial effects that:
1. The invention uses the electromagnet to directly control the pressure balance type oil nozzle, can improve the oil injection response time, greatly simplifies the structure of the oil injector, simultaneously has no long and thin high-pressure and low-pressure oil return holes, greatly simplifies the processing difficulty of the oil injector body 2 and reduces the cost of the common rail oil injector.
2. The invention is also used in the fuel spray nozzle of gasoline injection, and can improve the fuel pressure of direct injection gasoline injection so as to improve the performance of the gasoline engine.
Drawings
FIG. 1 is a first embodiment of the direct control fuel injector switch of the present invention;
FIG. 2 is a block diagram of a pressure balanced closed fuel injector;
FIG. 3 is a block diagram of the elimination of the dead volume of the nipple;
FIG. 4 is a second embodiment of the present invention;
FIG. 5 is a view of the F-F face of FIG. 4;
FIG. 6 is a view showing the structure of the tail of the needle valve, wherein a is a whole structure, and b is a split structure;
FIG. 7 is a prior art common rail injector with a servo ball valve;
The reference numbers 1 terminal assembly, 10 guide sleeve, 11 valve seat, 12 needle valve, 13 seal sleeve, 14 gap, 15 spring seat, 16 lever, 17 pin shaft, 18 return spring, 19 screw sleeve, 20 low pressure oil return hole, 101 terminal, 1101 high pressure oil inlet hole, 1102 oil holding groove, 1103 sealing conical surface A, 1104 oil injection hole, 1105 cylindrical hole, 1106 valve seat outer circle, 1107 inner channel, 1201 central oil return hole, 1202 sealing conical surface B, 1203 needle valve cylinder, 1204 small lubrication groove, 1205 cylinder ring groove, 1206 inclined hole A, 1207 upper groove edge, 1208 lower groove edge, 1209 lower ring groove, 1210 inclined hole B, 1211 low pressure oil return hole, 1212 hinge seat, 1213 outer side wall, 1214 cap, 1215 limit hole, 1216 groove, 2 oil injector body, 26 ring channel, 201 high pressure oil inlet hole A, 202 high pressure oil return hole A, 203 adjusting gasket, 204 electromagnet coil wire hole A, 205 inner oil return hole A, 206 high pressure oil inlet hole A, 3 return spring, 4 electromagnet part, 401 coil, 5, armature rod, 502 armature head, 701, 6 pressure balance nozzle, 7 middle spring seat, 702, and 8 return spring sleeve.
Detailed Description
The invention is described in detail below with reference to the accompanying drawings:
As shown in fig. 1-6: the invention relates to a common rail oil sprayer capable of directly controlling an oil sprayer switch, which mainly comprises a wiring terminal assembly 1, an oil sprayer body 2, an electromagnet part, an intermediate body 7 and a pressure balance oil sprayer 6, wherein the wiring terminal assembly 1 is connected above the oil sprayer body 2 through a screw sleeve 19, and the intermediate body 7 and the pressure balance oil sprayer 6 are connected below the oil sprayer body 2 through an oil sprayer screw sleeve 9; the electromagnet component is arranged in the oil sprayer body 2 and is connected with the control pressure balance oil sprayer 6 to realize the direct control of the on-off of the pressure balance oil sprayer 6.
The basic mechanism of the binding post assembly 1 and the oil sprayer body 2 is not too large to be in and out of the existing binding post assembly 1 and the existing oil sprayer body 2, and a binding post 101 is arranged on the binding post assembly 1; the oil atomizer body 2 is internally provided with high-pressure oil inlet holes a201 and 206, a low-pressure oil return hole a202, an electromagnet coil wire guide hole a204, an internal oil return hole a205 and the like.
According to the connection between the electromagnet part and the pressure-balancing nozzle 6, the invention can be divided into the following two embodiments:
Example 1
As shown in fig. 1-2: the pressure balance oil nozzle comprises a valve seat 11, a needle valve 12, a guide sleeve 10, a sealing sleeve 13 and a resetting structure;
the middle part of the valve seat 11 is provided with a valve seat inner channel 1107 which is coaxially arranged with the valve seat 11, the upper part of the valve seat inner channel 1107 is annularly provided with an oil containing groove 1102, the side wall of the valve seat 11 is provided with a high-pressure oil inlet hole 1101 which is communicated with the oil containing groove 1102, the lower part of the inner channel 1107 is annularly provided with a sealing conical surface A1103, the part of the inner channel 1107 positioned below the sealing conical surface A1103 forms a cylindrical hole 1105, and the side wall of the lower part of the valve seat 11 is annularly provided with a plurality of oil injection holes 1104 which are communicated with the cylindrical hole 1105;
The needle valve 12 extends into the inner channel 1107 of the valve seat 11 and can move up and down in the inner channel 1107, and the needle valve 12 is provided with a central oil return hole 1201 extending along the axial direction of the needle valve 12; the upper side wall of the needle valve 12 is provided with a low-pressure oil return hole 1211 communicated with the central oil return hole 1201, and the lower side wall of the needle valve 12 is annularly provided with a sealing conical surface B1202, so that the needle valve 12 positioned below the sealing conical surface B1202 forms a needle valve cylinder 1203; a cylinder ring groove 1205 is arranged at the joint of the outer periphery of the needle valve cylinder 1203 and the sealing conical surface B1202; a plurality of small lubrication grooves 1204 are annularly arranged on the periphery of the needle valve cylinder 1203 below the cylinder ring groove 1205;
The sealing sleeve 13 is plugged at the bottom of the inner channel 1107; after the needle valve 12 is lifted, the high-pressure fuel in the cylinder ring groove 1205 mainly seeps out through the gap between the needle valve cylinder 1203 of the needle valve 12 and the cylinder hole 1105 of the valve seat 11 to become low-pressure fuel, and returns from the low-pressure oil return hole a 202 to the fuel tank through the gap 14 between the needle valve cylinder 1203 and the seal sleeve 13, through the center oil return hole 1201 of the needle valve 12, the low-pressure oil return hole 1211 and the inner oil return hole a 205.
The inner bore of the sealing sleeve 13 is tightly matched with the valve seat excircle 1106, and is welded on the valve seat excircle 1106 by laser, so that low-pressure fuel can be sealed in use, and the low-pressure fuel cannot fall into a diesel engine combustion chamber from the nozzle valve seat 11.
The guide sleeve 10 is sleeved on the upper part of the needle valve 12, is arranged on the periphery and is in interference fit with the valve seat inner hole 1108;
the reset structure is disposed on top of the needle valve 12 and cooperates with the electromagnet member.
The taper angle of the sealing taper surface B1202 is B, the taper angle of the sealing taper surface A1103 is A, and the taper angle A is 0.5-3 degrees larger than the taper angle B.
The needle valve 12 is a cylinder with gradually changed diameter, the diameter of the region where the upper part of the needle valve 12 is matched with the guide sleeve 10 is d1, the diameter of the needle valve cylinder 1203 is d2, and the diameter of the middle region of the needle valve 12 is d3, wherein d1=d2, and d3 is 0.5-1 mm larger than d 2.
Because the diameter of the seal ring formed by the contact of the sealing cone a1103 with the sealing cones a1205, B1202 is d2, which is smaller than d3, and because d1=d2, in order to be easily assembled and disassembled, the guide sleeve 10 must be sleeved on the needle valve 12, and the inner hole diameter d1 of the guide sleeve 10, the hydraulic force acting on the needle valve 12 statically is zero; after the needle valve 12 is lifted, because of the precise matching of the sealing conical surface A1103 and the sealing conical surface B1202, the hydraulic resultant force of the sealing fuel acting on the needle valve 11 is zero, so that the electromagnet can lift or press the sealing conical surface B1202 of the needle valve 11 against the sealing conical surface A1103 of the valve seat 11 with a small force, and the fuel nozzle can switch high-pressure fuel, and a gap between an inner channel 1107 in the valve seat 11 and an outer side wall 1213 of the needle valve 12 forms a loop 26.
The reset structure comprises a cap 1214 and a return spring 8;
the cap 1214 is fixedly attached to the top of the needle 12 with the return spring 8 positioned between the cap 1214 and the top of the valve seat 11.
Since the cylinder ring groove 1205 cuts off the high pressure fuel after the sealing cone B1202 and the sealing cone a1103 are connected, but the injection hole 1104 is still communicated with the cylinder ring groove 1205, the dead volume of the cylinder ring groove 1205 is larger, so that the harmful emission of the diesel engine is increased, and the dead volume must be reduced as much as possible. The following modifications were made.
As shown in fig. 3: the needle valve cylinder 1203 is also provided with a lower annular groove 1209 below the cylinder annular groove 1205, the cylinder annular groove 1205 is provided with an inward extending inclined hole A1206, the lower annular groove 1209 is provided with an inward extending inclined hole B1210, and the inclined hole A1206 and the inclined hole B1210 are mutually communicated; the relationship of the lower ring groove 1209 and the cylinder ring groove 1205 satisfies the following conditions: the lower groove edge 1208 of the cylinder ring groove 1205 is not communicated with the oil spraying hole 1104; after the needle valve 12 descends, a distance H exists between the upper groove edge 1207 of the lower annular groove 1209 and the oil spraying hole 1104; when the needle valve 12 is lifted, the lower ring groove 1209 communicates with the oil jet hole 1104. Sharp edges and burrs are removed at the intersections of the holes A1206 and B1210 to prevent stress concentrations. After the high pressure fuel is cut off, the injection hole 1104 and the cylinder ring groove 1205 are not communicated any more, and the dead volume is zero.
When the needle valve 12 is lifted, the conical surface 1202 of the needle valve leaves the conical surface 1103 of the valve seat, high-pressure fuel in the annular groove 26 reaches the lower annular groove through the cylinder annular groove 1205, the inclined hole A1206 and the inclined hole B1210, and after the lift of the needle valve 12 exceeds H, the upper annular edge 1207 is communicated with the fuel injection hole 1104, and the high-pressure fuel is injected into the combustion chamber of the diesel engine. The magnitude of H and the lift of the needle 12 affect the cross-sectional area of the injector 1104, and at full load, the needle 12 lifts very much, which opens the orifice cross-sectional area entirely, while at small load and idle, the injector 1104 cross-sectional area is only partially open. Therefore, the injection rate of the spray holes can be changed by controlling the size of H, so that the combustion of the diesel engine is improved.
The electromagnet part comprises an adjusting gasket 203, a return spring 3, a spring seat 15, an armature rod 501 and an armature 5 which are arranged in the oil sprayer body 2 from top to bottom in sequence, the electromagnet part 41 for controlling the armature to lift is arranged above the armature 5 and at the periphery of the armature rod 501, and a coil 401 is arranged in the electromagnet part 4;
the armature head 502 of the armature rod 501 abuts the upper surface of the cap 1214.
The working procedure of example 1 is as follows:
The high-pressure fuel oil flows from high-pressure oil inlet holes A201 and 206 on the oil sprayer body 2, through a high-pressure oil inlet hole 1101 of the valve seat 11, to the oil containing groove 1102, then flows through the annular channel 26 and before reaching the sealing conical surface B1202, after the coil 401 of the electromagnet 4 is electrified, electromagnetic attraction force is generated, the armature assembly 5 and the armature rod 501 are sucked, the pretightening force of the return spring 3 is overcome, the needle valve 12 is lifted under the action of the return spring 8, the sealing conical surface B1202 is separated from the sealing conical surface A1103, the high-pressure fuel oil flows into the cylinder annular groove 1205 from the gap between the two conical surfaces, and then is sprayed into the combustion chamber of the diesel engine from the plurality of oil spraying holes 1104 for combustion.
The high pressure fuel in the cylinder ring groove 1205 is sealed above the needle cylinder 1203, and a small amount of fuel leaking from the gap between the cylinder bore 1105 and the needle cylinder 1203 flows back to the fuel tank through the center oil return hole 1201, the low pressure oil return hole 1211, the inner oil return hole a205 to the low pressure oil return hole a 202.
When the line graph 401 of the electromagnet 4 is powered off, the electromagnetic force is lost, and the return spring 8 is much lower than the stiffness of the return spring 3, so that the return spring 3 can press the sealing conical surface B1202 of the needle valve 12 against the sealing conical surface A1103, high-pressure fuel is cut off, and the fuel injection hole 1104 stops injecting fuel.
Example 2
As shown in fig. 4-6: the pressure balance type oil nozzle comprises a valve seat 11, a needle valve 12, a guide sleeve 10 and a reset structure;
The middle part of the valve seat 11 is provided with a valve seat inner channel 1107 which is coaxially arranged with the valve seat 11, the upper part of the valve seat 11 inner channel 1107 is annularly provided with an oil containing groove 1102, the side wall of the valve seat 11 is provided with a high-pressure oil inlet hole 1101 which is communicated with the oil containing groove 1102, the lower part of the inner channel 1107 is annularly provided with a sealing conical surface A1103, the part of the inner channel 1107 positioned below the sealing conical surface A1103 forms a cylindrical hole 1105, and the side wall of the lower part of the valve seat 11 is annularly provided with a plurality of oil injection holes 1104 which are communicated with the cylindrical hole 1105;
The needle valve 12 extends into the inner channel 1107 of the valve seat 11 and can move up and down in the inner channel 1107, and the needle valve 12 is provided with a central oil return hole 1201 extending along the axial direction of the needle valve 12; the upper side wall of the needle valve 12 is provided with a low-pressure oil return hole 1211 communicated with the central oil return hole 1201, and the lower side wall of the needle valve 12 is annularly provided with a sealing conical surface B1202, so that the needle valve 12 positioned below the sealing conical surface B1202 forms a needle valve cylinder 1203; a cylinder ring groove 1205 is arranged at the joint of the outer periphery of the needle valve cylinder 1203 and the sealing conical surface B1202; a plurality of small lubrication grooves 1204 are annularly arranged on the periphery of the needle valve cylinder 1203 below the cylinder ring groove 1205;
The guide sleeve 10 is sleeved on the outer periphery of the upper part of the needle valve 12 and is in interference fit with the valve seat inner hole 1108;
the reset structure is disposed on top of the needle valve 12 and cooperates with the electromagnet member.
The taper angle of the sealing taper surface B1202 is B, the taper angle of the sealing taper surface A1103 is A, and the taper angle A is 0.5-3 degrees larger than the taper angle B.
The needle valve 12 is a cylinder with gradually changed diameter, the diameter of the region where the upper part of the needle valve 12 is matched with the guide sleeve 10 is d1, the diameter of the needle valve cylinder 1203 is d2, and the diameter of the middle region of the needle valve 12 is d3, wherein d1=d2, and d3 is 0.5-1 mm larger than d 2.
The reset structure comprises a hinge seat 1212, a lever 16 and a reset spring 18 which are positioned at the upper end of the needle valve 12; the hinge seat 1212 is provided with a slot 1216, two side walls of the slot 1216 are provided with limiting holes 1215, and one end of the lever 16 is embedded in the slot 1216 and hinged on the hinge seat 1212 through a pin shaft 17 passing through the limiting holes 1215 and the lever 16. As can be seen in fig. 5, the intermediate body 7 is provided with a transverse groove 701 and a straight groove 702 of the return spring 18, so that the lever 16 rotates in the transverse groove 701, and 20 is a low-pressure oil return hole.
The electromagnet part comprises an adjusting gasket 203, a return spring 3, a spring seat 15, an armature rod 501 and an armature 5 which are arranged in the oil sprayer body 2 from top to bottom in sequence, the electromagnet part 41 for controlling the armature to lift is arranged above the armature 5 and at the periphery of the armature rod 501, and a coil 401 is arranged in the electromagnet part 4;
As shown in fig. 4: the armature head 502 of the armature pin 501 abuts the upper surface of the lever 16 to form a fulcrum a, and the lower surface of the lever 16 contacts the upper surface of the valve seat 11 to form a contact b. J is the distance from the center of the pin shaft to the contact point b, K is the distance from the fulcrum a to the contact point b, and the needle valve lift amplification ratio is J/K
The working procedure of example 2 is as follows:
Because the high-pressure fuel inlet hole A206 in the fuel injector body 2 exists, when the electromagnet is installed in the middle of the fuel injector, the diameter of the selectable electromagnet is smaller, the maximum electromagnetic force of the electromagnet is smaller, and in order to increase the electromagnetic force and speed up the switching speed of the needle valve, the diameter of the electromagnet is the best choice, and the electromagnet is deviated from the center by a certain distance, so that the diameter of the electromagnet is increased.
Because the electromagnetic force is larger when the travel of the flat electromagnet is small (generally about 0.1), and the travel of the needle valve 12 is 0.2-0.3 mm, a lever 16 is designed between the needle valve and the electromagnet, and the lift of the needle valve 12 is increased by using the lever 16. And when the armature lift of the electromagnet is smaller, the larger lift of the needle valve 12 can be obtained. The structure can increase the needle valve lift by 1-2 times.
When the electromagnet is specifically used, after the coil 401 of the electromagnet 4 is electrified, the return spring 3 presses the head 502 of the armature pin 501 on the point a of the lever 16, the lever 16 takes the point B as a fulcrum, overcomes the elasticity of the return spring 18, presses the sealing conical surface B1202 on the sealing conical surface A1103 through the pin 17, cuts off the passage of high-pressure fuel oil flowing to the spray hole 1104, and the spray nozzle is not provided with a spray nozzle.
After the coil 401 of the electromagnet 4 is electrified, the electromagnetic attraction force makes the armature rod 501 rise through the armature 5, the lever 16 rises by taking B as a fulcrum under the action of the return spring 18 and the pin shaft 17, so that the needle valve 12 is lifted, the sealing conical surface B1202 is separated from the sealing conical surface A1103, and high-pressure fuel is sprayed into the combustion chamber from the conical surface gap through the cylinder ring groove 1205 and the fuel injection hole 1104.
Because the bias electromagnet and the lever 16 are adopted, the lifting range of the electromagnet is reduced, the suction force is greatly increased, the lifting range of the needle valve is also increased, and the switching speed of the needle valve 12 is increased by 1-2 times.
The invention provides an equal seal line method, which enables the resultant force of high-pressure fuel oil pressure acting on a nozzle needle valve to be zero, namely a pressure balanced closed fuel nozzle, and a diesel engine high-pressure common rail fuel injector using an electromagnet to directly switch the fuel nozzle. Under the condition that the spray hole angle and the spray line direction of the oil spray nozzle are basically unchanged from those of the crude oil spray nozzle, the hydraulic pressure acted on the needle valve is balanced so that the electromagnetic valve has enough electromagnetic force to directly control the switch of the oil spray nozzle.
The above-described equal seal line method balances the high-pressure hydraulic forces acting on the needle valve. The basic idea is as follows: the intersection line of the conical surface of the valve seat and the inner hole with the diameter d2 is used as a sealing line, the sealing line contacts with the conical surface of the needle valve to seal high-pressure oil, the diameter d2 of the sealing line is increased, and the sealing line is as large as the inner diameter d1 of the outer circle of the needle valve matched with the guide sleeve in the valve seat, so that the resultant force of static hydraulic pressure acting on the needle valve is zero. The pressure balance control valve of the common rail fuel injector and the unit pump is used for discharging high-pressure fuel to low pressure. The pressure balanced fuel injection nozzle controls the high pressure fuel in the common rail before being sent to the fuel injection hole, the fuel injection hole is smaller, the original high pressure is kept in front of the fuel injection hole, the two-position two-way control valve is generally uncontrollable, and in order to balance the hydraulic force acting on the needle valve in the process of lifting and closing the needle valve, a section of cylinder with the diameter of d2 of a conical surface sealing line is added at the top of the needle valve, and the cylinder keeps sealing with an inner hole with the diameter of d2 of the lower end of the valve seat, so that the high pressure fuel in front of the fuel injection hole cannot flow to the bottom of the needle valve, and the balance of the hydraulic force is destroyed.
While the invention has been illustrated and described with respect to specific embodiments and alternatives thereof, it will be appreciated that various changes and modifications can be made therein without departing from the spirit of the invention. It is, therefore, to be understood that the invention is not to be in any way limited except by the appended claims and their equivalents.
Claims (7)
1. A common rail oil sprayer for directly controlling an oil sprayer switch mainly comprises a wiring terminal assembly (1), an oil sprayer body (2), an electromagnet component, an intermediate body (7) and a pressure balance oil sprayer (6), wherein the wiring terminal assembly (1) is connected above the oil sprayer body (2) through a screw sleeve (19), and the intermediate body (7) and the pressure balance oil sprayer (6) are connected below the oil sprayer body (2) through an oil sprayer screw sleeve (9); the method is characterized in that: the electromagnet component is arranged in the oil sprayer body (2) and is connected with the control pressure balance oil sprayer (6) to realize the direct control of the on-off of the pressure balance oil sprayer (6);
the pressure balance oil nozzle comprises a valve seat (11), a needle valve (12), a guide sleeve (10), a sealing sleeve (13) and a reset structure;
An inner channel (1107) which is coaxially arranged with the valve seat (11) is arranged in the middle of the valve seat (11), an oil containing groove (1102) is annularly arranged at the upper part of the inner channel (1107) of the valve seat (11), a high-pressure oil inlet hole (1101) which is communicated with the oil containing groove (1102) is formed in the side wall of the valve seat (11), a sealing conical surface A (1103) is annularly arranged at the lower part of the inner channel (1107), a cylindrical hole (1105) is formed at the position, below the sealing conical surface A (1103), of the inner channel (1107), and a plurality of oil injection holes (1104) which are communicated with the cylindrical hole (1105) are annularly arranged at the side wall of the lower part of the valve seat (11);
The needle valve (12) stretches into an inner channel (1107) of the valve seat (11) and can move up and down in the inner channel (1107), and the needle valve (12) is provided with a central oil return hole (1201) extending along the axial direction of the needle valve (12); a low-pressure oil return hole (1211) communicated with the central oil return hole (1201) is formed in the upper side wall of the needle valve (12), and a sealing conical surface B (1202) is annularly arranged on the lower side wall of the needle valve (12) so that a needle valve cylinder (1203) is formed at the position of the needle valve (12) below the sealing conical surface B (1202); a cylinder ring groove (1205) is arranged at the joint of the outer periphery of the needle valve cylinder (1203) and the sealing conical surface B (1202); a plurality of small lubrication grooves (1204) are annularly arranged below the cylinder ring groove (1205) at the periphery of the needle valve cylinder (1203);
the sealing sleeve (13) is plugged at the bottom of the inner channel (1107);
the guide sleeve (10) is sleeved on the periphery of the upper part of the needle valve (12) and is in interference fit with the valve seat inner hole (1108);
the reset structure is arranged at the top of the needle valve (12) and is matched with the electromagnet part.
2. The direct-control fuel injector switching common rail injector of claim 1, wherein:
The cone angle of the sealing cone B (1202) is B, the cone angle of the sealing cone A (1103) is A, and the cone angle A is 0.5-3 degrees larger than the cone angle B;
The needle valve (12) is a cylinder with gradually changed diameter, the diameter of the region where the upper part of the needle valve (12) is matched with the guide sleeve (10) is d1, the diameter of the needle valve cylinder (1203) is d2, the diameter of the middle region of the needle valve (12) is d3, wherein d1=d2, and d3 is 0.5-1 mm larger than d 2.
3. The direct-control fuel injector switching common rail injector of claim 2, wherein:
The reset structure comprises a cap (1214) and a return spring (8);
The cap (1214) is fixedly connected to the top of the needle valve (12), and the return spring (8) is positioned between the cap (1214) and the top of the valve seat (11).
4. A direct-control fuel injector common rail switch as defined in claim 3, wherein: the needle valve cylinder (1203) is also provided with a lower annular groove (1209) below the cylinder annular groove (1205), the cylinder annular groove (1205) is provided with an inward extending inclined hole A (1206), the lower annular groove (1209) is provided with an inward extending inclined hole B (1210), and the inclined hole A (1206) and the inclined hole B (1210) are mutually communicated; the relationship between the lower ring groove (1209) and the cylinder ring groove (1205) satisfies the following conditions: the lower groove edge (1208) of the cylinder ring groove (1205) is not communicated with the oil spraying hole (1104); after the needle valve (12) descends, a distance H exists between the upper groove edge (1207) of the lower annular groove (1209) and the oil spraying hole (1104); when the needle valve (12) is lifted, the lower annular groove (1209) is communicated with the oil spraying hole (1104).
5. The direct control fuel injector switching common rail injector of claim 3 or 4, wherein: the electromagnet part comprises an adjusting gasket (203), a return spring (3), a spring seat (15), an armature pin (501) and an armature (5) which are arranged in the oil sprayer body (2) from top to bottom in sequence, an electromagnet part (41) for controlling the armature to lift is arranged above the armature (5) and at the periphery of the armature pin (501), and a coil (401) is arranged in the electromagnet part (41);
the armature head (502) of the armature rod (501) abuts the upper surface of the cap (1214).
6. The direct-control fuel injector switching common rail injector of claim 2, wherein:
The reset structure comprises a hinge seat (1212), a lever (16) and a reset spring (18) which are positioned at the upper end of the needle valve (12); the hinge seat (1212) is provided with a slot (1216), two side walls of the slot (1216) are provided with limiting holes (1215), and one end of the lever (16) is embedded in the slot (1216) and hinged on the hinge seat (1212) through a pin shaft (17) penetrating through the limiting holes (1215) and the lever (16).
7. The common rail injector for directly controlling a fuel injector switch according to claim 6, the method is characterized in that: the electromagnet part comprises an adjusting gasket (203), a return spring (3), a spring seat (15), an armature pin (501) and an armature (5) which are arranged in the oil sprayer body (2) from top to bottom in sequence, an electromagnet part (41) for controlling the armature to lift is arranged above the armature (5) and at the periphery of the armature pin (501), and a coil (401) is arranged in the electromagnet part (41);
The armature head (502) of the armature pin (501) is propped against the upper surface of the lever (16) to form a fulcrum a, and the lower surface of the lever (16) is contacted with the upper surface of the valve seat (11) to form a contact b.
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| CN202010169117.8A CN111237108B (en) | 2020-03-12 | 2020-03-12 | High-pressure common rail oil sprayer capable of directly controlling oil spray nozzle switch |
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| CN102434346A (en) * | 2011-11-23 | 2012-05-02 | 哈尔滨工程大学 | Low oil-return type electromagnetic control oil sprayer |
| CN212508611U (en) * | 2020-03-12 | 2021-02-09 | 莆田市宏业精密机械有限公司 | High-pressure common rail oil sprayer for directly controlling opening and closing of oil nozzle |
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| JP3303630B2 (en) * | 1995-09-19 | 2002-07-22 | 三菱自動車工業株式会社 | Fuel injection device |
| CN101539084B (en) * | 2009-03-20 | 2010-12-29 | 天津大学 | Common rail electronic control jet apparatus |
| EP2405127B1 (en) * | 2010-07-07 | 2013-04-03 | Wärtsilä Switzerland Ltd. | A fuel injector for internal combustion engines |
| DE102010040401A1 (en) * | 2010-09-08 | 2012-03-08 | Robert Bosch Gmbh | fuel injector |
| CN106014739B (en) * | 2016-05-25 | 2018-05-18 | 中国第一汽车股份有限公司无锡油泵油嘴研究所 | A kind of atomizer |
| CN209781103U (en) * | 2019-04-17 | 2019-12-13 | 无锡格林鲍尔科技有限公司 | Common rail oil sprayer with pressure-resisting and blockage-preventing functions |
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Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102434346A (en) * | 2011-11-23 | 2012-05-02 | 哈尔滨工程大学 | Low oil-return type electromagnetic control oil sprayer |
| CN212508611U (en) * | 2020-03-12 | 2021-02-09 | 莆田市宏业精密机械有限公司 | High-pressure common rail oil sprayer for directly controlling opening and closing of oil nozzle |
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