CN111237108A - High-pressure common rail oil sprayer for directly controlling opening and closing of oil nozzle - Google Patents
High-pressure common rail oil sprayer for directly controlling opening and closing of oil nozzle Download PDFInfo
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- CN111237108A CN111237108A CN202010169117.8A CN202010169117A CN111237108A CN 111237108 A CN111237108 A CN 111237108A CN 202010169117 A CN202010169117 A CN 202010169117A CN 111237108 A CN111237108 A CN 111237108A
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- 238000002347 injection Methods 0.000 claims abstract description 35
- 239000007924 injection Substances 0.000 claims abstract description 35
- 238000007789 sealing Methods 0.000 claims description 58
- 239000007921 spray Substances 0.000 claims description 24
- 238000000034 method Methods 0.000 claims description 6
- 230000001050 lubricating effect Effects 0.000 claims description 3
- 230000000149 penetrating effect Effects 0.000 claims 1
- 239000000446 fuel Substances 0.000 abstract description 44
- 230000004044 response Effects 0.000 abstract description 4
- 230000009286 beneficial effect Effects 0.000 abstract description 2
- 230000002035 prolonged effect Effects 0.000 abstract 1
- 239000003921 oil Substances 0.000 description 121
- 230000001276 controlling effect Effects 0.000 description 10
- 239000000295 fuel oil Substances 0.000 description 8
- 238000002485 combustion reaction Methods 0.000 description 6
- 230000009471 action Effects 0.000 description 3
- 239000013078 crystal Substances 0.000 description 3
- 239000010779 crude oil Substances 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 239000000543 intermediate Substances 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000003321 amplification Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000008030 elimination Effects 0.000 description 1
- 238000003379 elimination reaction Methods 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 239000000178 monomer Substances 0.000 description 1
- 238000003199 nucleic acid amplification method Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 230000003068 static effect Effects 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
- 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
- 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
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- 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
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
The invention relates to a high-pressure common rail oil sprayer for directly controlling the opening and closing of an oil nozzle; the device mainly comprises a wiring column assembly, an oil sprayer body, an electromagnet assembly, an intermediate and a pressure balance oil nozzle, wherein the wiring column assembly is connected above the oil sprayer body through a threaded sleeve, and the intermediate and the pressure balance oil nozzle are connected below the oil sprayer body through an oil nozzle threaded sleeve; the electromagnet part is arranged in the oil sprayer body and is connected with the pressure balance oil nozzle to directly control the opening and closing of the pressure balance oil nozzle. The invention has the beneficial effects that: the electromagnet directly controls the pressure balance type oil nozzle, so that the oil injection response time can be prolonged, the structure of the oil injector is greatly simplified, a plurality of long and thin high-pressure and low-pressure oil return holes are not formed, the processing difficulty of an 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 injection nozzle for 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 oil sprayer of a diesel engine, in particular to a common rail oil sprayer for directly controlling the opening and closing of an oil nozzle, belonging to the field of fuel oil systems of internal combustion engines.
Background
The common rail oil injector of the prior diesel engine has two modes of controlling the opening and closing of an oil nozzle by an electromagnet and a piezoelectric crystal, the common rail oil injector indirectly controls the opening and closing of the oil nozzle mainly through a hydraulic servo valve, has a complex structure, high processing precision and low response speed, is not directly controlled by the piezoelectric crystal through the hydraulic servo valve at home and abroad at present, and is a product, for example, the common rail oil injector directly controlling the opening and closing of the oil nozzle is used on the diesel engine by America Delfu company and Germany continental company.
The common rail injector controlled by the electromagnet has a small high-speed electromagnet volume, the acting force is only 100 newtons and is much smaller than thousands of newtons of the piezoelectric crystal control force, a common closed type oil nozzle is shown in fig. 7 at present, the needle valve guide sealing diameter d1 is 4mm, the conical surface sealing diameter d2 is 2mm, and when the electromagnet is in a low-pressure area, high-pressure fuel acting on the nozzle needle valve can generate upward unbalanced hydraulic pressure. When the fuel injection pressure is 200Mpa, the fuel acts on a nozzle needle valve, the upward unbalanced hydraulic pressure is as high as 1800 Newton, the electromagnetic force of the electromagnet is far less than the unbalanced hydraulic pressure, the electromagnet cannot directly pull the needle valve to control the opening and closing of the nozzle, and the electromagnetic force is converted into strong hydraulic pressure through a hydraulic servo valve to pull the needle valve to control the opening and closing of the nozzle. Therefore, at present, no high-pressure common rail oil sprayer with an oil nozzle being directly controlled by an electromagnet exists at home and abroad.
FIG. 7 shows a typical configuration of a common rail injector for a diesel engine manufactured by BOSCH in Germany. The common rail oil injector has the advantages that on one hand, the electromagnet switches the oil injection nozzle through the servo valve, the response speed is slower than that of the oil injection nozzle by direct control, in addition, the hydraulic impact force of up to 180 and 200Mpa acts on the hydraulic piston, so that the precise sealing conical surface of a needle valve and a valve seat is worn quickly, the service life of the oil nozzle is shortened, and the working reliability is reduced.
The patent 20081004087 of the present company proposes a high pressure common rail injector for directly controlling the opening and closing of an injection nozzle, which places a two-position two-way servo control valve at the upper end of the injection nozzle, but controls the opening and closing of the injection nozzle through the servo valve, and is not a real high pressure common rail injector with an electromagnet directly controlling the opening and closing of the injection nozzle.
Disclosure of Invention
The invention aims to: the high-pressure common rail oil injector directly controls the opening and closing of an oil nozzle; the high-pressure common rail oil sprayer adopts an equal sealing line principle, so that the resultant force of the high-pressure fuel oil pressure acting on an oil nozzle needle valve is zero, namely, a closed oil nozzle with balanced pressure, and the diesel engine high-pressure common rail oil sprayer directly switches the oil nozzle by using an electromagnet. The oil nozzle keeps the spray hole angle and the oil spray line direction of the oil nozzle and the crude oil nozzle basically unchanged, and the hydraulic pressure acting on the needle valve is balanced mutually, so that the electromagnetic valve has enough electromagnetic force to directly control the opening and closing of the oil nozzle.
The invention is realized by the following technical scheme: a common rail oil atomizer of the direct control fuel spray nozzle switch, it is mainly by terminal block assembly 1, oil atomizer body 2, electromagnet part, midbody 7 and pressure balance fuel spray nozzle 6 to form, the terminal block assembly 1 is connected to the oil atomizer body 2 above through the swivel nut 19, midbody 7 and pressure balance fuel spray nozzle 6 are connected to the lower side of oil atomizer body 2 through the fuel spray nozzle swivel nut 9; the electromagnet component is arranged in the oil sprayer body 2 and is connected with the pressure balance control oil nozzle 6 so as to realize the direct control of the opening and closing of the pressure balance oil nozzle 6.
Compared with the prior art, the invention has the beneficial effects that:
1. the invention uses electromagnet to directly control the pressure balance type oil nozzle, which can improve the oil injection response time, greatly simplifies the structure of the oil injector, does not have a plurality of slender 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 injection nozzle for 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 present invention for directly controlling the opening and closing of an oil jet;
FIG. 2 is a structural view of a pressure balanced closed fuel injector;
FIG. 3 is a block diagram of the elimination of choke dead volume;
FIG. 4 is a second embodiment of the present invention;
FIG. 5 is a plan view of portion F-F of FIG. 4;
FIG. 6 is a view of the structure of the tail of the needle valve, wherein a is an integral structure and b is a split structure;
FIG. 7 is a prior art common rail injector with a servo ball valve;
description of the reference numerals 1 terminal assembly, 10 guide sleeve, 11 valve seat, 12 needle valve, 13 sealing sleeve, 14 clearance, 15 spring seat, 16 lever, 17 pin shaft, 18 reset spring, 19 screw sleeve, 20 low pressure oil return hole, 101 terminal, 1101 high pressure oil inlet hole, 1102 oil containing groove, 1103 sealing cone A, 1104 oil spray hole, 1105 cylindrical hole, 1106 valve seat excircle, 1107 inner channel, 1201 central oil return hole, 1202 sealing cone 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 cover cap, spacing hole, 1216 groove, 2 oil sprayer body, 26 ring channel, 201 high pressure oil inlet hole A, 202 low pressure oil return hole A, 203 regulating gasket, 204 wire coil hole A, 205 internal electromagnet oil return hole A, 206 high pressure oil inlet hole A, 204 oil spray hole A, 17 low pressure oil return hole A, 17 low pressure oil spray hole, 17 low pressure, 3 return springs, 4 electromagnet components, 401 coils, 5 armatures, 501 armature rods, 502 armature heads, 701 transverse grooves, 6 pressure balance oil nozzles, 7 intermediates, 701 transverse grooves, 702 straight grooves, 8 return springs and 9 oil nozzle screw sleeves.
Detailed Description
The invention is described in detail below with reference to the following description of the drawings:
as shown in fig. 1-6: the invention is a common rail oil atomizer of the direct control fuel spray nozzle switch, it is mainly by terminal block assembly 1, oil atomizer body 2, electromagnet part, midbody 7 and pressure balance fuel spray nozzle 6 to form, the terminal block assembly 1 is connected to the upper side of the oil atomizer body 2 through the swivel nut 19, midbody 7 and pressure balance fuel spray nozzle 6 are connected to the lower side of the oil atomizer body 2 through the fuel spray nozzle swivel nut 9; the electromagnet component is arranged in the oil sprayer body 2 and is connected with the pressure balance control oil nozzle 6 so as to realize the direct control of the opening and closing of the pressure balance oil nozzle 6.
The basic mechanisms of the terminal assembly 1 and the oil injector body 2 do not have too large access with the existing terminal assembly 1 and the oil injector body 2, and the terminal 101 is arranged on the terminal assembly 1; 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 are machined in the oil injector body 2.
According to the connection mode between the electromagnet part and the pressure-balanced fuel injector 6, the invention can be divided into the following two embodiments:
example 1
As shown in fig. 1-2: the pressure balance type oil nozzle comprises a valve seat 11, a needle valve 12, a guide sleeve 10, a sealing sleeve 13 and a reset structure;
a valve seat inner channel 1107 which is coaxial 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 valve seat inner channel 1107, a high-pressure oil inlet 1101 communicated with the oil containing groove 1102 is arranged on the side wall of the valve seat 11, a sealing conical surface A1103 is annularly arranged at the lower part of the inner channel 1107 so that a cylindrical hole 1105 is formed at the part of the inner channel 1107 below the sealing conical surface A1103, and a plurality of oil injection holes 1104 communicated with the cylindrical hole 1105 are annularly arranged on the side wall of the lower;
the needle valve 12 extends 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; 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 is positioned below the sealing conical surface B1202 to form a needle valve cylinder 1203; a cylinder ring groove 1205 is arranged at the joint of the periphery of the needle valve cylinder 1203 and the sealing conical surface B1202; a plurality of small lubricating 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 blocked at the bottom of the inner channel 1107; the sealing sleeve 13 mainly after the needle valve 12 is lifted, the high-pressure fuel in the cylinder ring groove 1205 can seep out through the gap between the needle valve cylinder 1203 of the needle valve 12 and the cylindrical hole 1105 of the valve seat 11 to become low-pressure fuel, and the low-pressure fuel returns to the oil tank from the low-pressure fuel return hole a202 through the central oil return hole 1201 of the needle valve 12, the low-pressure oil return hole 1211 and the internal oil return hole a205 through the gap 14 between the needle valve cylinder 1203 and the sealing sleeve 13.
The inner hole of the sealing sleeve 13 is tightly matched with the outer circle 1106 of the valve seat and is welded on the outer circle 1106 of the valve seat by laser, so that low-pressure fuel can be sealed in use, and the low-pressure fuel cannot fall into a combustion chamber of a diesel engine from the nozzle valve seat 11.
The guide sleeve 10 is sleeved on the upper part of the needle valve 12, and the periphery of the guide sleeve is in interference fit with the inner hole 1108 of the valve seat;
the reset structure is arranged on the top of the needle valve 12 and is matched with the electromagnet part.
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 area 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 area in the middle of the needle valve 12 is d3, wherein d1 is d2, and d3 is 0.5-1 mm larger than d 2.
Because the sealing conical surface a1103 contacts with the sealing conical surfaces a1205, B1202 to form the sealing ring with the diameter d2, which is smaller than d3, and because d1 is d2, the guide sleeve 10 must be sleeved on the needle 12 for easy assembly and disassembly, and the inner hole diameter d1 of the guide sleeve 10, the hydraulic pressure acting on the needle 12 statically is zero; after the needle valve 12 is lifted, because the sealing conical surface A1103 and the sealing conical surface B1202 are precisely matched, the hydraulic resultant force of sealing fuel acting on the needle valve 11 is zero, so the electromagnet only needs to use a small force to make the sealing conical surface B1202 of the needle valve 11 lifted or pressed on the sealing conical surface A1103 of the valve seat 11, so that the fuel injection nozzle can switch high-pressure fuel, and a gap between an inner channel 1107 in the valve seat 11 and the outer side wall 1213 of the needle valve 12 forms an annular channel 26.
The reset structure comprises a cover cap 1214 and a return spring 8;
a cap 1214 is fixedly attached to the top of the needle 12, with a return spring 8 positioned between the cap 1214 and the top of the valve seat 11.
Because the cylinder ring groove 1205 cuts off high-pressure fuel after the sealing conical surface B1202 and the sealing conical surface A1103 are communicated, but the spray holes 1104 are still communicated with the cylinder ring groove 1205, the dead volume of the cylinder ring groove 1205 is large, harmful discharge of a diesel engine is increased, and the dead volume must be reduced as much as possible. So the following modifications are made.
As shown in fig. 3: a lower ring groove 1209 is further formed below the cylindrical ring groove 1205 and the needle valve cylinder 1203, the cylindrical ring groove 1205 is provided with an inward extending inclined hole A1206, the lower ring groove 1209 is provided with an inward extending inclined hole B1210, and the inclined hole A1206 and the inclined hole B1210 are communicated with each other; the relationship of the lower ring groove 1209 and the cylinder ring groove 1205 satisfies the following condition: the lower groove edge 1208 of the cylinder ring groove 1205 is not communicated with the oil spray hole 1104; after the needle valve 12 descends, an upper groove edge 1207 of the lower ring groove 1209 has a certain distance H with the oil spray hole 1104; when the needle 12 is lifted, the lower ring groove 1209 communicates with the oil jet 1104. The intersection of the inclined hole A1206 and the inclined hole B1210 is to remove sharp-edge burrs so as to prevent stress concentration. After the high pressure fuel is cut off, the spray holes 1104 are not communicated with the cylinder ring groove 1205, and the dead volume is zero.
When the needle valve 12 rises and the conical surface 1202 of the needle valve leaves the conical surface 1103 of the valve seat, high-pressure fuel in the ring groove 26 reaches the ring groove below the groove through the cylindrical ring groove 1205, the inclined hole A1206 and the inclined hole B1210, and after the lift of the needle valve 12 exceeds H, the upper groove edge 1207 is communicated with the fuel injection hole 1104, and the high-pressure fuel is injected into a combustion chamber of a diesel engine. The size of H and the lift of the needle 12 affect the cross-sectional area of the nozzle 1104. at full load, the lift of the needle 12 is large, allowing the nozzle cross-sectional area to be fully open, while at light load and idle, the nozzle cross-sectional area 1104 is only partially open. Controlling H can change the orifice injection rate and thus improve diesel combustion.
The electromagnet component 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 injector body 2 from top to bottom in sequence, an electromagnet component 41 for controlling the armature to ascend and descend is arranged above the armature 5 and on the periphery of the armature rod 501, and a coil 401 is arranged in the electromagnet component 4;
the armature head 502 of the armature stem 501 rests on the upper surface of the cap 1214.
The working procedure of example 1 is as follows:
high-pressure fuel oil flows from high-pressure oil inlet holes A201 and 206 on an oil injector body 2, passes through a high-pressure oil inlet hole 1101 of a valve seat 11, reaches an oil containing groove 1102, passes through a ring channel 26, reaches the front of a sealing conical surface B1202, generates electromagnetic suction force after a coil 401 of an electromagnet 4 is electrified, sucks an armature assembly 5 and an armature rod 501, rises under the action of the pre-tightening force of a return spring 3, a needle valve 12 rises under the action of a return spring 8, the sealing conical surface B1202 is separated from the sealing conical surface A1103, the high-pressure fuel oil flows into a cylindrical ring groove 1205 from a gap between the two conical surfaces, and then is sprayed into a combustion chamber of a diesel engine from a plurality.
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 hole 1105 and the needle cylinder 1203 flows back to the tank through the center oil return hole 1201, the low pressure oil return hole 1211, the internal oil return hole a205, and the low pressure oil return hole a 202.
When the diagram 401 of the electromagnet 4 is de-energized, the electromagnetic force is lost, and the pressure of 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 to cut off the high-pressure fuel, 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;
a valve seat inner channel 1107 which is coaxial 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 1101 communicated with the oil containing groove 1102 is arranged on the side wall of the valve seat 11, a sealing conical surface A1103 is annularly arranged at the lower part of the inner channel 1107 so that a cylindrical hole 1105 is formed at the part of the inner channel 1107 below the sealing conical surface A1103, and a plurality of oil injection holes 1104 communicated with the cylindrical hole 1105 are annularly arranged on the side wall of the;
the needle valve 12 extends 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; 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 is positioned below the sealing conical surface B1202 to form a needle valve cylinder 1203; a cylinder ring groove 1205 is arranged at the joint of the periphery of the needle valve cylinder 1203 and the sealing conical surface B1202; a plurality of small lubricating 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 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 on the top of the needle valve 12 and is matched with the electromagnet part.
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 area 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 area in the middle of the needle valve 12 is d3, wherein d1 is d2, and d3 is 0.5-1 mm larger than d 2.
The resetting structure comprises a hinge seat 1212 positioned at the upper end of the needle valve 12, a lever 16 and a resetting spring 18; the hinge base 1212 is provided with a slot 1216, two side walls of the slot 1216 are provided with a limit hole 1215, and one end of the lever 16 is embedded in the slot 1216 and is hinged on the hinge base 1212 by a pin 17 passing through the limit hole 1215 and the lever 16. As can be seen in fig. 5, a transverse groove 701 and a straight groove 702 of the return spring 18 are formed in the intermediate body 7, so that the lever 16 rotates in the transverse groove 701, and 20 is a low-pressure oil return hole.
The electromagnet component 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 injector body 2 from top to bottom in sequence, an electromagnet component 41 for controlling the armature to ascend and descend is arranged above the armature 5 and on the periphery of the armature rod 501, and a coil 401 is arranged in the electromagnet component 4;
as shown in fig. 4: the armature head 502 of the armature rod 501 forms a fulcrum a against the upper surface of the lever 16, and the lower surface of the lever 16 contacts the upper surface of the valve seat 11 to form a contact point 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 lift amplification ratio of the needle valve 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 electromagnet capable of being selected is smaller, the maximum electromagnetic force of the electromagnet is smaller, and in order to increase the electromagnetic force and accelerate the opening and closing speed of the needle valve, the diameter of the electromagnet is the best choice, so that the electromagnet is deviated from the center by a certain distance, and the diameter of the electromagnet is increased.
Because the electromagnetic force is larger when the flat-plate electromagnet stroke is small (generally about 0.1), and the stroke 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 utilizing the lever 16. When the lift of the armature of the electromagnet is small, a large lift of the needle valve 12 can be obtained. The structure can increase the lift of the needle valve by 1-2 times.
When the high-pressure fuel injector is used specifically, after the coil 401 of the electromagnet 4 is electrified, the return spring 3 presses the head 502 of the armature rod 501 on the point a of the lever 16, the lever 16 overcomes the elastic force of the return spring 18 by taking the point B as a fulcrum, the sealing conical surface B1202 is pressed on the sealing conical surface A1103 through the pin shaft 17, the passage of high-pressure fuel to the spray hole 1104 is cut off, and the fuel injector does not have a nozzle.
After the coil 401 of the electromagnet 4 is electrified, the electromagnet attraction force enables the armature rod 501 to ascend through the armature 5, the lever 16 ascends through the pin 17 by taking the B as a fulcrum under the action of the return spring 18, 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 oil is sprayed into a combustion chamber from the conical surface clearance through the cylindrical ring groove 1205 and the oil spray hole 1104.
Because the bias electromagnet and the lever 16 are adopted, the lift range of the electromagnet is reduced, the suction force is greatly increased, the lift range of the needle valve is also improved, and the switching speed of the needle valve 12 is improved by 1-2 times.
The invention provides an equal sealing line method, which is a closed oil nozzle with zero resultant force of high-pressure fuel oil pressure acting on an oil nozzle needle valve, namely pressure balance, and a diesel engine high-pressure common rail oil injector with an oil nozzle directly opened and closed by an electromagnet. The oil nozzle keeps the spray hole angle and the oil spray line direction of the oil nozzle and the crude oil nozzle basically unchanged, and the hydraulic pressure acting on the needle valve is balanced mutually, so that the electromagnetic valve has enough electromagnetic force to directly control the opening and closing of the oil nozzle.
The above-described seal line methods balance 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 a sealing line which is in contact with the conical surface of the needle valve to seal high-pressure oil, the diameter d2 of the sealing line is increased and 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 valves of the common rail fuel injector and the monomer pump discharge high-pressure fuel to low pressure. The pressure-balanced oil nozzle controls that high-pressure fuel oil in a common rail is sent to the front of an oil injection hole, the original high pressure is kept in the front of the oil injection hole due to the fact that the oil injection hole is small, a two-position two-way control valve cannot be controlled generally, and in order to balance hydraulic pressure acting on a needle valve in the lifting and closing processes of the needle valve, a section of cylinder with the diameter d2 equal to the diameter of a conical surface sealing line must be added to the top of the needle valve and is sealed with an inner hole with the diameter d2 at the lower end of a valve seat, so that the high-pressure fuel oil in the front of the oil injection hole cannot.
While the invention has been illustrated and described with respect to specific embodiments and alternatives thereof, it will be understood that various changes and modifications can be made without departing from the spirit and scope of the invention. It is understood, therefore, that the invention is not to be in any way limited except by the appended claims and their equivalents.
Claims (8)
1. A common rail oil sprayer for directly controlling an oil nozzle switch mainly comprises a terminal post assembly (1), an oil sprayer body (2), an electromagnet assembly, an intermediate body (7) and a pressure balance oil nozzle (6), wherein the terminal post assembly (1) is connected above the oil sprayer body (2) through a threaded sleeve (19), and the intermediate body (7) and the pressure balance oil nozzle (6) are connected below the oil sprayer body (2) through an oil nozzle threaded sleeve (9); the method is characterized in that: the electromagnet part is arranged in the oil injector body (2) and is connected with the pressure balance control oil nozzle (6) to realize the direct control of the opening and closing of the pressure balance oil nozzle (6).
2. The common rail injector that directly controls the opening and closing of the injection nozzle according to claim 1, characterized in that:
the pressure balance type oil nozzle comprises a valve seat (11), a needle valve (12), a guide sleeve (10), a sealing sleeve (13) and a reset structure;
the middle of the valve seat (11) is provided with an inner channel (1107) which is coaxial with the valve seat (11), the upper part of the inner channel (1107) of the valve seat (11) 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 A (1103) to enable the inner channel (1107) to be positioned below the sealing conical surface A (1103) to form 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);
the needle valve (12) extends 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 side wall of the upper portion of the needle valve (12), a sealing conical surface B (1202) is annularly formed in the side wall of the lower portion of the needle valve (12), and a needle valve cylinder (1203) is formed in the position, below the sealing conical surface B (1202), of the needle valve (12); a cylinder ring groove (1205) is arranged at the joint of the periphery of the needle valve cylinder (1203) and the sealing conical surface B (1202); a plurality of small lubricating 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);
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 inner hole (1108) of the valve seat;
the reset structure is arranged on the top of the needle valve (12) and is matched with the electromagnet component.
3. The common rail injector that directly controls the opening and closing of the injection nozzle according to claim 2, characterized in that:
the cone angle of the sealing conical surface B (1202) is B, the cone angle of the sealing conical surface 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 an area 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 area of the needle valve (12) is d3, wherein d1 is d2, and d3 is 0.5-1 mm larger than d 2.
4. The common rail injector that directly controls the opening and closing of the injection nozzle according to claim 3, characterized in that:
the reset structure comprises a cover 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).
5. The common rail injector that directly controls the opening and closing of the injection nozzle according to claim 4, characterized in that: a lower ring groove (1209) is further formed below the cylindrical ring groove (1205) and on the needle valve cylinder (1203), an inward extending inclined hole A (1206) is formed in the cylindrical ring groove (1205), an inward extending inclined hole B (1210) is formed in the lower ring groove (1209), and the inclined hole A (1206) and the inclined hole B (1210) are communicated with each other; the relationship of the lower ring groove (1209) and the cylinder ring groove (1205) satisfies the following condition: the lower groove edge (1208) of the cylinder ring groove (1205) is not communicated with the oil spray hole (1104); after the needle valve (12) descends, an upper groove edge (1207) of the lower ring groove (1209) has a certain distance H with the oil spray hole (1104); when the needle valve (12) is lifted, the lower ring groove (1209) is communicated with the oil spray hole (1104).
6. The common rail injector that directly controls opening and closing of the injection nozzle according to claim 4 or 5, characterized in that: the electromagnet component 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 injector body (2) from top to bottom in sequence, an electromagnet component (41) for controlling the armature to lift is arranged above the armature (5) and on the periphery of the armature rod (501), and a coil (401) is arranged in the electromagnet component (4);
the armature head (502) of the armature rod (501) abuts the upper surface of the cap (1214).
7. The common rail injector that directly controls the opening and closing of the injection nozzle according to claim 3, characterized in that:
the resetting structure comprises a hinge seat (1212) positioned at the upper end of the needle valve (12), a lever (16) and a resetting spring (18); an open groove (1216) is formed in the hinge seat (1212), two side walls of the open groove (1216) are provided with limit holes (1215), and one end of the lever (16) is embedded in the open groove (1216) and is hinged to the hinge seat (1212) through a pin shaft (17) penetrating through the limit holes (1215) and the lever (16).
8. The common rail injector directly controlling opening and closing of the injection nozzle according to any one of claims 7, characterized in that: the electromagnet component 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 injector body (2) from top to bottom in sequence, an electromagnet component (41) for controlling the armature to lift is arranged above the armature (5) and on the periphery of the armature rod (501), and a coil (401) is arranged in the electromagnet component (4);
an armature head (502) of the armature rod (501) is pressed 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 point b.
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| CN202010169117.8A CN111237108A (en) | 2020-03-12 | 2020-03-12 | High-pressure common rail oil sprayer for directly controlling opening and closing of oil nozzle |
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| CN202010169117.8A CN111237108A (en) | 2020-03-12 | 2020-03-12 | High-pressure common rail oil sprayer for directly controlling opening and closing of oil nozzle |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN116952314A (en) * | 2023-09-21 | 2023-10-27 | 海默新宸水下技术(上海)有限公司 | Flow measuring method for underwater medicament injection equipment |
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