CN109404189B - Heavy oil electric control fuel injector for low-speed diesel engine - Google Patents
Heavy oil electric control fuel injector for low-speed diesel engine Download PDFInfo
- Publication number
- CN109404189B CN109404189B CN201811635342.5A CN201811635342A CN109404189B CN 109404189 B CN109404189 B CN 109404189B CN 201811635342 A CN201811635342 A CN 201811635342A CN 109404189 B CN109404189 B CN 109404189B
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- injector
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- 239000000446 fuel Substances 0.000 title claims abstract description 234
- 239000000295 fuel oil Substances 0.000 title claims abstract description 90
- 239000003921 oil Substances 0.000 claims abstract description 436
- 239000010724 circulating oil Substances 0.000 claims abstract description 23
- 230000000903 blocking effect Effects 0.000 claims abstract description 5
- 238000001816 cooling Methods 0.000 claims description 62
- 238000007789 sealing Methods 0.000 claims description 36
- 238000002156 mixing Methods 0.000 claims description 32
- 239000002283 diesel fuel Substances 0.000 claims description 12
- 238000005520 cutting process Methods 0.000 claims description 7
- 230000006835 compression Effects 0.000 claims description 5
- 238000007906 compression Methods 0.000 claims description 5
- 239000007921 spray Substances 0.000 claims description 2
- 238000005507 spraying Methods 0.000 claims description 2
- 230000000694 effects Effects 0.000 abstract description 7
- 239000011148 porous material Substances 0.000 abstract description 4
- 238000005260 corrosion Methods 0.000 abstract description 3
- 230000007797 corrosion Effects 0.000 abstract description 3
- 238000007711 solidification Methods 0.000 abstract description 2
- 230000008023 solidification Effects 0.000 abstract description 2
- 230000000670 limiting effect Effects 0.000 description 11
- 238000002347 injection Methods 0.000 description 10
- 239000007924 injection Substances 0.000 description 10
- 230000001105 regulatory effect Effects 0.000 description 10
- 238000011161 development Methods 0.000 description 6
- 238000010586 diagram Methods 0.000 description 4
- 238000009434 installation Methods 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 238000002485 combustion reaction Methods 0.000 description 3
- 238000004519 manufacturing process Methods 0.000 description 3
- 230000033228 biological regulation Effects 0.000 description 2
- 230000003749 cleanliness Effects 0.000 description 2
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 238000013461 design Methods 0.000 description 2
- 238000002955 isolation Methods 0.000 description 2
- 239000003208 petroleum Substances 0.000 description 2
- 125000006850 spacer group Chemical group 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 238000011109 contamination Methods 0.000 description 1
- 230000001276 controlling effect Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000003912 environmental pollution Methods 0.000 description 1
- 239000003502 gasoline Substances 0.000 description 1
- 239000010763 heavy fuel oil Substances 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 230000013011 mating Effects 0.000 description 1
- 238000013021 overheating Methods 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 239000002994 raw material Substances 0.000 description 1
- 238000004064 recycling Methods 0.000 description 1
- 238000007670 refining Methods 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
- F02M51/0603—Injectors peculiar thereto with means directly operating the valve needle using piezoelectric or magnetostrictive 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
- 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
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/0012—Valves
- F02M63/0014—Valves characterised by the valve actuating means
- F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
- F02M63/0017—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/0012—Valves
- F02M63/0014—Valves characterised by the valve actuating means
- F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
- F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
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 heavy oil electric control fuel injector for a low-speed diesel engine, which is used for realizing the effects of preventing solidification in the heavy oil electric control fuel injector and preventing corrosion of devices in the fuel injector. The electronic fuel injector comprises: the upper body of the oil sprayer, the oil sprayer body, the oil inlet pore plate, the needle valve body and the nozzle are sequentially arranged from top to bottom; the end face of the needle valve body, which faces the oil inlet orifice, is respectively provided with a control volume cavity and a high-pressure fuel cavity; an oil inlet channel, an oil return channel and a circulating oil channel are sequentially arranged among the upper body of the oil injector, the oil injector body and the oil inlet pore plate, the outlet of the oil inlet channel is respectively communicated with the control volume cavity and the high-pressure fuel cavity through oil channels, and the circulating oil channel is communicated with the high-pressure fuel cavity; a circulation valve for blocking or conducting the leakage of the fuel oil in the high-pressure fuel cavity is arranged in the circulation oil duct; an electromagnetic valve assembly and an oil outlet control valve assembly are arranged in the oil sprayer body; the high-pressure fuel cavity of the needle valve body is internally provided with a fuel injector lower body component.
Description
Technical Field
The invention relates to the field of low-speed diesel engines, in particular to a heavy oil electric control fuel injector for a low-speed diesel engine.
Background
In recent years, petroleum resources are increasingly scarce, environmental pollution is increasingly serious, and the light diesel oil and gasoline equivalent grids which take petroleum as raw materials are continuously increased, so that the maintenance quantity and the further development of low-speed diesel engines are severely restricted. Heavy oil belongs to inferior fuel oil, does not need further refining, has low fuel oil cost, and can obviously reduce the use cost of the marine low-speed diesel engine. Meanwhile, the emission regulation requirements of marine diesel engines are continuously improved, so that the use of low-speed diesel engines is greatly limited. In order to meet the use requirements of low-speed diesel engines, development of an electric fuel injector for burning heavy oil is imperative.
At present, the overseas companies such as Wasitan, mann and Rorun have autonomous low-speed diesel engine fuel systems, and serial products are formed, and the fuel systems are matched with low-speed diesel engines of different types to form monopoly trend, the current low-speed diesel engines in China mainly introduce patent permission production, the fuel systems are used as core sleeves of the diesel engines, the production capacity is completely absent, the overseas complete fuel systems are purchased, the price is extremely high, and the autonomous development process of the low-speed diesel engines in China is restricted. Therefore, the development of the low-speed diesel engine fuel system with complete independent intellectual property can break through the monopolization of foreign technology and promote the independent development process of the low-speed diesel engine in China.
The low-speed diesel engine is mainly a mechanical fuel system at present, a small amount of fuel system driven by servo oil is adopted, and electric control is realized, but a fuel injector of the fuel system still adopts a mechanical fuel injector, such as MC and ME series low-speed diesel engines of Mann company, RT-flex series diesel engines of Wasitan and the like. The mechanical fuel system cannot realize flexible regulation of the fuel injection rule, so that the power performance, the emission performance and the like of the diesel engine are affected. The electric control fuel injector can flexibly adjust the fuel injection rule and accurately control the fuel injection quantity, and has important effect on improving the combustion of the diesel engine. However, marine diesel engines mainly use heavy oil which has the characteristics of strong corrosiveness, high temperature and the like, and the working reliability of the electric control fuel injector is seriously affected.
Compared with the traditional fuel injector, the electronic control fuel injector has more complex structure and higher part precision in order to meet more advanced injection function. Meanwhile, the electronic control oil sprayer is additionally provided with a high-speed electromagnetic valve, the electromagnetic valve belongs to a vulnerable part, the electromagnetic valve works for a long time under the strong corrosiveness of heavy oil and high-temperature environment, the working reliability is one of the critical factors influencing the service life of the electronic control oil sprayer, and meanwhile, the reliability of precise parts under the strong corrosiveness of heavy oil is one of the key technical problems.
In the prior art, after the electromagnetic valve is powered off, heavy oil entering the electronic control oil sprayer still partially remains in the oil sprayer, and the heavy oil remaining in the oil sprayer can be solidified, so that the problem of corrosion of devices in the oil sprayer is caused.
Disclosure of Invention
The invention aims to provide a heavy oil electric control fuel injector for a low-speed diesel engine, which aims to solve the problem of corrosion of devices caused by solidification of heavy oil in the electric control fuel injector.
The technical scheme of the invention is as follows:
the invention provides a heavy oil electric control fuel injector for a low-speed diesel engine, which comprises the following components: the oil sprayer comprises an oil sprayer upper body, an oil sprayer body, an oil inlet pore plate, a needle valve body and a nozzle which are sequentially arranged from top to bottom;
the end face of the needle valve body, which faces the oil inlet orifice plate, is respectively provided with a control volume cavity and a high-pressure fuel cavity;
an oil inlet channel, an oil return channel and a circulating oil channel are sequentially formed among the upper body of the oil injector, the oil injector body and the oil inlet orifice plate, the outlet of the oil inlet channel is respectively communicated with the control volume cavity and the high-pressure fuel cavity through oil channels, and the circulating oil channel is communicated with the high-pressure fuel cavity; a circulation valve for blocking or conducting the fuel leakage in the high-pressure fuel cavity is arranged in the circulation oil duct;
An electromagnetic valve assembly for energizing or de-energizing and an oil outlet control valve assembly for switching on or off the control volume cavity and the oil return channel are arranged in the oil sprayer body;
a first gap for the fuel in the high-pressure fuel cavity to pass through or a sealed lower body assembly of the fuel injector is formed between the high-pressure fuel cavity of the needle valve body and the cavity wall of the high-pressure fuel cavity;
when the electromagnetic valve assembly is electrified, heavy oil enters the control volume cavity and the high-pressure fuel cavity through the fuel inlet channel respectively, the electromagnetic valve assembly drives the fuel outlet control valve assembly to conduct the control volume cavity and the fuel return channel, and the heavy oil in the control volume cavity leaks out through the fuel return channel so as to reduce the fuel pressure in the control volume cavity; after the oil pressure in the control volume cavity is reduced, the lower body assembly of the oil injector moves upwards under the action of the oil pressure of the fuel in the high-pressure fuel cavity so as to form a first gap with the cavity wall of the high-pressure fuel cavity, and heavy oil in the high-pressure fuel cavity flows into the nozzle through the first gap and is sprayed outwards; the circulating valve is closed to block the fuel in the high-pressure fuel cavity from leaking;
When the electromagnetic valve assembly is powered off, heavy oil enters the control volume cavity and the high-pressure fuel cavity through the fuel inlet channel respectively, and the oil outlet control valve assembly breaks off the control volume cavity and the oil return channel so as to raise the oil pressure in the control volume cavity; after the oil pressure in the control volume cavity is increased, the lower body component of the oil injector moves downwards under the action of the oil pressure of the fuel in the control volume cavity so as to form a seal with the cavity wall of the high-pressure fuel cavity, and the nozzle stops injecting outwards;
after the nozzle stops injecting outwards, diesel oil lower than heavy oil pressure enters the high-pressure fuel cavity through the oil inlet channel, the circulating valve is opened, and the fuel oil in the high-pressure fuel cavity is conducted to leak.
Preferably, the circulation oil passage includes a first circulation oil passage provided in the upper body of the fuel injector and a second circulation oil passage provided in the body of the fuel injector; a first mounting groove used for communicating with the first circulating oil duct is formed on the end face, facing the oil sprayer body, of the upper oil sprayer body, and a second mounting groove used for communicating with the second circulating oil duct is formed on the end face, facing the oil sprayer body, of the upper oil sprayer body; the connecting surface of the first mounting groove and the end surface of the upper body of the oil sprayer forms a first conical surface;
The circulation valve includes: one part of the circulating valve core is arranged in the first mounting groove, and the other part of the circulating valve core is arranged in the second mounting groove; a first axial cutting groove is formed in the outer surface of the part, which is placed in the first mounting groove, of the circulating valve core, the circulating valve core is placed in the first mounting groove, and a circulating valve spring is arranged between the circulating valve core and the groove bottom of the first mounting groove; the outer surface of the circulating valve core is provided with a second conical surface for forming conical surface sealing or a second gap with the first conical surface;
when the oil pressure in the second circulation oil duct is larger than the elastic force of the circulation valve spring, the circulation valve core moves upwards under the action of the oil pressure in the second circulation oil duct, and conical surface sealing is formed between the first conical surface and the second conical surface;
when the oil pressure in the second circulation oil duct is smaller than the elastic force of the circulation valve spring, the circulation valve core moves upwards under the action of the elastic force of the circulation valve spring, a second gap is formed between the first conical surface and the second conical surface, and fuel oil in the second circulation oil duct enters the first circulation oil duct through the second gap and the first axial cutting groove to be discharged outwards.
Preferably, a through groove is formed in an end face, facing the second circulation oil duct, of the circulation valve core, fuel in the second circulation oil duct flows into a space between the circulation valve core and the second mounting groove through the through groove, and flows into the first circulation oil duct through the second gap and the first axial cutting groove;
the circulating valve core extends towards the bottom of the first mounting groove to form a first limiting boss for supporting the circulating valve spring, and a step surface for abutting the end part of the circulating valve spring is formed between the first limiting boss and the circulating valve core.
Preferably, the solenoid valve assembly includes:
the device comprises a compression screw plug, an electromagnetic valve, a sleeve and an electromagnetic valve sleeve which are sequentially arranged from top to bottom;
an armature mounted within the sleeve, the armature disposed relative to the solenoid valve;
a control valve core installed in the valve housing of the solenoid valve, the control valve core partially penetrating the sleeve and being connected to the armature;
a solenoid valve spring sleeved on the control valve core;
the electromagnetic force generated when the electromagnetic valve is electrified attracts the armature to drive the control valve core to move upwards, and the control valve core is pushed to move downwards by the repulsive force generated by the electromagnetic valve spring when the electromagnetic valve is powered off.
Preferably, a second limiting boss is arranged on the outer surface of the control valve core in a protruding mode, and the electromagnetic valve spring is limited between the second limiting boss and the sleeve.
Preferably, be equipped with on the oil feed orifice plate with control volume chamber intercommunication's oil outlet, oil outlet control valve subassembly includes:
an oil outlet control valve sleeve and an oil outlet orifice plate which are sequentially arranged from top to bottom and integrally formed with the electromagnetic valve sleeve; the oil outlet orifice plate is provided with an oil outlet orifice communicated with the oil outlet hole, an oil outlet cavity communicated with the oil outlet orifice and an oil outlet pipe communicated with the oil outlet cavity; the oil outlet pipe is communicated with the oil return channel;
the ball valve guide rod is arranged in the oil outlet control valve sleeve and is arranged relative to the control valve core and the oil outlet throttle hole;
after the electromagnetic valve is electrified to drive the control valve core to move upwards, the ball valve guide rod moves upwards under the action of oil pressure in the control volume cavity, so that the oil outlet throttle hole is communicated with the oil outlet cavity, and fuel oil in the control volume cavity flows into the oil return channel through the oil outlet hole, the oil outlet throttle hole, the oil outlet cavity and the oil outlet pipe in sequence;
After the electromagnetic valve spring pushes the control valve core to move downwards, the control valve core pushes the ball valve guide rod to move downwards, the outlet of the oil outlet orifice is closed, and the fuel oil entering the oil outlet orifice is blocked from entering the oil outlet cavity.
Preferably, a cooling cavity is formed between the outer wall of the electromagnetic valve, the outer wall of the sleeve and the inner wall of the oil sprayer body, the upper body of the oil sprayer and the oil sprayer body are sequentially perforated to form a cooling oil inlet channel and a cooling oil return channel, and the cooling oil inlet channel and the cooling oil return channel are respectively communicated with the cooling cavity.
Preferably, a cooling oil through hole communicated with the cooling cavity is formed in the sleeve;
a mixing oil cavity is formed among the outer wall of the electromagnetic valve sleeve, the outer wall of the oil outlet control valve sleeve and the inner wall of the oil injector body, the upper body of the oil injector and the oil injector body are sequentially provided with holes to form a mixing oil return channel communicated with the mixing oil cavity, and a transverse oil channel communicated with the mixing oil cavity is arranged at the joint of the electromagnetic valve sleeve and the oil outlet control valve sleeve;
the cooling oil in the cooling cavity enters the sleeve through the cooling oil through hole, flows into the mixing oil cavity sequentially through a gap between the sleeve and the control valve core, a gap between the control valve core and the solenoid valve sleeve and the transverse oil duct, flows into the mixing oil cavity, and flows into the mixing oil cavity through the ball valve guide rod, the gap between the oil outlet control valve sleeve and the transverse oil duct, and the cooling oil and the fuel flowing into the mixing oil cavity are discharged outwards through the mixing oil return duct after being mixed.
Preferably, the nozzle is partially sleeved on the outer surface of the needle valve body in an interference fit mode, the nozzle and the needle valve body are tightly pressed through a nozzle tight cap, and the oil sprayer body, the oil inlet pore plate and the needle valve body are tightly pressed through a device tight cap.
Preferably, an upper sealing ring is arranged between the electromagnetic valve sleeve and the inner wall of the oil injector body, a lower sealing ring is arranged between the oil outlet control valve sleeve and the inner wall of the oil injector body, and the mixed oil cavity is positioned between the upper sealing ring and the lower sealing ring.
The beneficial effects of the invention are as follows:
(1) The electromagnetic valve of the electric control oil injector adopts the design of isolation, sealing and cooling simultaneously by combining the special requirements of heavy oil for low-speed engine combustion, the electromagnetic valve is isolated and sealed from a heavy oil working area by matching a support guide sleeve (which is formed by integrally forming an electromagnetic valve sleeve and an oil outlet control valve sleeve) with an even part formed between a ball valve guide rod and a control valve core, and a cooling cavity is designed around the electromagnetic valve to cool the electromagnetic valve, so that the electromagnetic valve is suitable for the use environment of heavy oil.
(2) And a circulating valve is designed in the electric control fuel injector, when the fuel in the fuel injector is at low pressure, an oil inlet channel and a circulating oil return channel of the fuel injector are communicated through the circulating valve, heavy oil in the fuel injector is circularly flushed, the cleanliness of an oil cavity and the oil channel in the fuel injector is improved, and meanwhile, the heavy oil is prevented from solidifying in the fuel injector.
(3) The supporting guide sleeve is designed in the electric control fuel injector, the lower body part of the fuel injector is separated from the electromagnetic valve by the supporting guide sleeve, and the installation position of the electromagnetic valve can be flexibly adjusted by designing the height of the supporting guide sleeve.
(4) The seat surface seal of the oil outlet plate adopts ball valve seal, a ball valve guide rod structure is designed, the self-alignment neutrality of the ball valve and the guide property and the tightness of the guide rod are fully utilized, and the seat surface seal of the oil outlet plate, the axial dynamic seal and the guide property of the ball valve guide rod are ensured.
(5) And a mixing oil cavity and a mixing oil duct are designed in the middle part of the oil sprayer body and are used for collecting and independently recycling the high-pressure fuel oil and the cooling oil leaked through the gap of the matching parts, so that the mutual pollution between the fuel oil and the cooling oil is prevented.
Drawings
FIG. 1 is a schematic diagram of the structure of the present invention;
FIG. 2 is one of the schematic structural diagrams of the middle portion of the fuel injector;
FIG. 3 is a second schematic diagram of the middle portion of the fuel injector;
FIG. 4 is a third schematic illustration of the middle portion of the fuel injector;
FIG. 5 is a schematic diagram of a middle portion of a fuel injector;
FIG. 6 is a schematic view of the lower body portion of the fuel injector;
FIG. 7 is a schematic illustration of the installation of a recirculation valve on and to an injector body;
FIG. 8 is a schematic view of a seal formed between a needle valve and a needle valve body;
FIG. 9 is a schematic illustration of the solenoid valve assembly and the oil outlet control valve assembly mated within the injector body;
FIG. 10 is a schematic illustration of the engagement of the solenoid valve assembly within the injector body;
FIG. 11 is a schematic view of the structure of the valve core of the circulation valve of the present invention;
reference numerals illustrate: 1-an upper body portion of the fuel injector; 11-an upper body of the oil injector; 111-first mounting groove: 112-a first conical surface; 12-a circulation valve spring; 13-a circulation valve spool; 131-a first axial slot; 132-a second conical surface; 133-through grooves; 134-first limit boss; 102-a first oil inlet duct; 103-a first circulation oil passage; 2-the middle part of the fuel injector; 21-compressing the screw plug; 22-an oil injector body; 221-a second mounting groove; 23-an electromagnetic valve sealing ring; 24-electromagnetic valve; 25-sleeve; 26-armature; 27-fixing screws; 28-a solenoid valve spring; 29-supporting a guide sleeve; 291-solenoid valve housing; 292-oil outlet control valve sleeve; 293-transverse oil channels; 30-adjusting the gasket; 31-an upper sealing ring; 32-a control valve core; 321-a second limiting boss; 33-ball valve guide rod; 34-a lower sealing ring; 35-an oil outlet plate; 351-an oil outlet orifice; 352-oil outlet chamber; 353-flowline; 202-a second circulation oil passage; 203-a second oil inlet duct; 204-a cooling chamber; 205-mixing oil chamber; 206-an oil outlet orifice; 209-cooling oil inlet duct; 210-a cooling oil return passage; 207-oil return passage; 208-mixing oil return ducts; 6-a lower body part of the fuel injector; 4-an oil inlet orifice plate; 61-needle valve body; 611-a fourth conical surface; 62-control plunger sleeve; 63-a pressure regulating spring; 64-needle valve; 641-third limit boss; 642-a third conical surface; 65-tightening the cap of the device body; 66-nozzle tightening cap; 67-nozzles; 402-an oil outlet hole; 403-a third circulation oil passage; 404-an oil inlet orifice; 602-controlling the volume chamber; 603-high pressure fuel chamber.
Detailed Description
Referring to fig. 1 to 11, the present invention provides a heavy oil electronically controlled fuel injector for a low speed diesel engine, comprising: the upper body 11, the injector body 22, the oil inlet orifice 4, the needle valve body 61 and the nozzle 67 are arranged in sequence from top to bottom; a control volume cavity 602 and a high-pressure fuel cavity 603 are respectively formed on the end face of the needle valve body 61 facing the fuel inlet orifice 4; an oil inlet channel, an oil return channel 207 and a circulating oil channel are sequentially arranged among the upper oil sprayer body 11, the oil sprayer body 22 and the oil inlet orifice plate 4, the outlet of the oil inlet channel is respectively communicated with the control volume cavity 602 and the high-pressure fuel cavity 603 through oil channels, and the circulating oil channel is communicated with the high-pressure fuel cavity 603; a circulation valve for blocking or conducting the fuel leakage in the high-pressure fuel cavity 603 is arranged in the circulation oil duct; a solenoid valve assembly for energizing or de-energizing and an oil outlet control valve assembly for switching on or off the control volume 602 and the oil return passage 207 are installed in the oil sprayer body 22; a first gap or a sealed lower body assembly of the fuel injector for allowing fuel in the high-pressure fuel cavity 603 to pass through is formed between the high-pressure fuel cavity 603 of the needle valve body 61 and the cavity wall of the high-pressure fuel cavity 603; when the electromagnetic valve assembly is electrified, heavy oil enters the control volume cavity 602 and the high-pressure fuel cavity 603 through the fuel inlet channel, the electromagnetic valve assembly drives the fuel outlet control valve assembly to conduct the control volume cavity 602 and the fuel return channel 207, and the heavy oil in the control volume cavity 602 leaks out through the fuel return channel 207 so as to reduce the fuel pressure in the control volume cavity 602; after the oil pressure in the control volume 602 decreases, the lower body assembly of the fuel injector moves upwards under the action of the oil pressure in the high-pressure fuel chamber 603 to form a first gap with the wall of the high-pressure fuel chamber 603, and the heavy oil in the high-pressure fuel chamber 603 flows into the nozzle 67 through the first gap and is injected outwards; the circulation valve is closed to block the fuel in the high-pressure fuel cavity 603 from leaking; when the electromagnetic valve assembly is powered off, heavy oil enters the control volume cavity 602 and the high-pressure fuel cavity 603 through the fuel inlet channel respectively, and the oil outlet control valve assembly breaks off the control volume cavity 602 and the oil return channel 207 so as to raise the oil pressure in the control volume cavity 602; after the oil pressure in the control volume 602 increases, the lower body assembly of the fuel injector moves downwards under the action of the oil pressure in the control volume 602 to form a seal with the wall of the high-pressure fuel chamber 603, and the nozzle 67 stops injecting outwards; after the nozzle 67 stops injecting, the diesel oil lower than the heavy oil pressure enters the high-pressure fuel cavity 603 through the oil inlet channel, and the circulation valve is opened to conduct the fuel in the high-pressure fuel cavity 603 to leak.
Referring to fig. 1 to 6 and 9, the oil intake passage includes a first oil intake passage 102 provided in the injector upper body 11 and a second oil intake passage 203 provided in the injector body 22, the first and second oil intake passages 102 and 203 communicating. When the fuel enters the oil feed orifice plate 4 through the second oil feed passage 203, the fuel is split into 2 paths, the first path is the main fuel flowing into the high-pressure fuel chamber 603, and the second path is the control fuel flowing into the control volume chamber 602 through the oil feed orifice 404 provided on the oil feed orifice plate 4.
In which, referring to fig. 6, the injector upper body 11 and the injector body 22 are integrally connected by bolts. The nozzle 67 is partially sleeved on the outer surface of the needle valve body 61 in an interference fit manner, the nozzle 67 and the needle valve body 61 are tightly pressed through a nozzle tightening cap 66, and the oil sprayer body 22, the oil inlet orifice plate 4 and the needle valve body 61 are tightly pressed through a device body tightening cap 65.
The electronic control fuel injector is mainly applied to a marine low-speed diesel engine. In particular, the electrically controlled fuel injector can realize the injection of heavy fuel oil. In this application, after solenoid valve subassembly outage, let in the light diesel oil that the oil pressure is less than this heavy oil in to automatically controlled sprayer, after the light fuel got into, can make the oil pressure that is located the oil inlet end of circulation valve drop, and then make the circulation valve open, the heavy oil of surviving in high pressure fuel cavity 603 outwards discharges through this circulation valve. Thus, after the electromagnetic valve assembly is powered down, the heavy oil in the electric control oil sprayer is discharged outwards by introducing light diesel oil, and the effects of preventing the heavy oil from solidifying in the electric control oil sprayer and preventing parts from being corroded and damaged are achieved.
Referring to fig. 6, the circulation oil passages include a first circulation oil passage 103 provided in the injector upper body 11 and a second circulation oil passage 202 provided in the injector body 22; a first mounting groove 111 for communicating with the first circulation oil duct 103 is formed on an end face of the upper injector body 11 facing the injector body 22, and a second mounting groove 221 for communicating with the second circulation oil duct 202 is formed on an end face of the injector body 22 facing the injector body 11; the connection surface between the first mounting groove 111 and the end surface of the injector upper body 11 forms a first conical surface 112; the circulation valve includes: a circulation valve core 13 having a part placed in the first mounting groove 111 and another part placed in the second mounting groove 221; a first axial cutting groove 131 is formed in the outer surface of the part, which is placed in the first mounting groove 111, of the circulating valve core 13, the circulating valve core 13 is placed in the first mounting groove 111, and a circulating valve spring 12 is arranged between the circulating valve core 13 and the groove bottom of the first mounting groove 111; a second conical surface 132 for forming a conical surface seal or a second gap with the first conical surface 112 is arranged on the outer surface of the circulating valve core 13; when the oil pressure in the second circulation oil passage 202 is greater than the elastic force of the circulation valve spring 12, the circulation valve core 13 moves upwards under the action of the oil pressure in the second circulation oil passage 202, and a conical surface seal is formed between the first conical surface 112 and the second conical surface 132; when the oil pressure in the second circulation oil passage 202 is smaller than the elastic force of the circulation valve spring 12, the circulation valve core 13 moves upward under the elastic force of the circulation valve spring 12, a second gap is formed between the first conical surface 112 and the second conical surface 132, and the fuel in the second circulation oil passage 202 enters the first circulation oil passage 103 through the second gap and the first axial slot 131 to be discharged outwards.
As shown in fig. 1 and 9, the circulation oil passage further includes a third circulation oil passage 403 provided on the oil intake orifice plate 4, the third circulation oil passage 403 being in communication with the second circulation oil passage 202 and the high-pressure oil chamber 603, respectively.
Specifically, when the solenoid valve assembly is energized, since the fuel oil introduced into the oil inlet passage is heavy oil, the oil pressure of the heavy oil is greater than the elastic force of the circulating valve spring 12, so that the circulating valve core 13 is moved upward under the pushing of the oil pressure of the heavy oil in the second circulating oil passage 202, the circulating valve spring 12 is compressed, the second conical surface 132 forms a seal with the first conical surface 112, and in this state, the fuel oil in the high-pressure fuel oil chamber 603 cannot be discharged outwards through the circulating valve, but can only be sprayed outwards through the nozzle 67, and the spraying effect of the electronic control fuel injector can be realized.
When the electromagnetic valve assembly is powered off, high-pressure heavy oil introduced into the oil inlet channel is switched into low-pressure diesel oil, the oil pressure in the second circulating oil channel 202 is reduced to low-pressure diesel oil pressure along with continuous introduction of the diesel oil, when the oil pressure in the second circulating oil channel 202 is smaller than the rebound force of the circulating valve spring 12, the compressed circulating valve spring 12 rebounds to push the circulating valve core 13 to move downwards, the first conical surface 112 and the second conical surface 132 form the second gap, and at the moment, heavy oil remained in the second circulating oil channel 202 and diesel oil introduced into the circulating oil channel flow into the first circulating oil channel 103 through the second gap and are finally discharged outwards; meanwhile, the residual heavy oil in the control volume cavity 602 and the diesel oil newly entering the control volume cavity 602 are discharged outwards through the oil return channel 207; thus, when the electric control fuel injector is not needed for heavy oil injection, the heavy oil in the control volume cavity 602 and the high-pressure fuel cavity 603 can be discharged outwards, and the heavy oil is prevented from being remained in the electric control fuel injector to corrode and block internal devices of the electric control fuel injector.
As for the circulation valve core 13, referring to fig. 11, a through groove 133 is formed on an end surface of the circulation valve core 13 facing the second circulation oil duct 202, and fuel in the second circulation oil duct 202 flows into a space between the circulation valve core 13 and the second mounting groove 221 through the through groove 133, and flows into the first circulation oil duct 103 through the second gap and the first axial slot 131; a first limit boss 134 for supporting the circulation valve spring 12 extends from the circulation valve spool 13 toward the bottom of the first installation groove 111, and a stepped surface for abutting the end of the circulation valve spring 12 is formed between the first limit boss 134 and the circulation valve spool 13. As can be seen in fig. 7 and 11, the circulating valve spring 12 is limited between the first limiting boss 134 and the circulating valve core 13, so that the compression effect on the circulating valve spring 12 and the pushing effect on the circulating valve core 13 when the circulating valve spring 12 rebounds can be enhanced.
Referring to fig. 2 to 5, the solenoid valve assembly includes: the compression screw plug 21, the electromagnetic valve 24, the sleeve 25 and the electromagnetic valve sleeve 29 are sequentially arranged from top to bottom; an armature 26 mounted within the sleeve 25, the armature 26 being disposed relative to the solenoid valve 24; a control valve core 32 mounted within the solenoid valve housing 29, the control valve core 32 partially passing through the sleeve 25 and connecting the armature 26; a solenoid valve spring 28 sleeved on the control valve core 32; the electromagnetic force generated when the electromagnetic valve 24 is electrified attracts the armature 26 to drive the control valve core 32 to move upwards, and the control valve core 32 is pushed to move downwards by the repulsive force generated by the electromagnetic valve spring 28 when the electromagnetic valve 24 is powered off. The hold-down screw 21 is used to hold down the components (solenoid valve 24, sleeve 25, solenoid valve housing 291, oil outlet control valve housing 292, and oil outlet plate 35) that are installed in the holes in the injector body 22. An electromagnetic valve sealing ring 23 for improving sealing performance is arranged between the electromagnetic valve 24 and the oil injector body 22, and the compression screw plug 21 is abutted against the upper body 11 of the oil injector. The armature 26 is fixed with the control valve core 32 through the fixing screw 27, so that the armature 26 can drive the control valve core 32 to move upwards when being attracted by electromagnetic force of the electromagnetic valve 24 to move upwards; when the control valve core 32 moves downward under the action of the solenoid valve spring 28, the control valve core 32 drives the armature 26 to move downward.
The ball valve guide rod 33 is integrally designed, and the valve core is an elongated rod with a sealing sphere at one end. Specifically, an arcuate surface or a hemispherical surface is formed on the end of the elongated rod to seal the outlet of the oil outlet orifice 351. Thus, the positioning of the elongated rod is achieved for the ball valve guide 33, and the hemispherical surface formed at the end of the elongated rod can provide a sealing effect. Compared with the ball valve guide rod in the prior art, the ball valve guide rod 33 in the application can be manufactured by one manufacturing process.
As shown in fig. 10, in order to improve the limiting effect of the solenoid valve spring 28, a second limiting boss 321 is protruding on the outer surface of the control valve core 32, and the solenoid valve spring 28 is limited between the second limiting boss 321 and the sleeve 25. Meanwhile, an adjusting spacer 30 is disposed between the solenoid valve spring 28 and the second limiting boss 321, and the height of the sleeve 25 can be adjusted by changing the thickness of the adjusting spacer 30 to compensate for the accumulated error of the machining.
Referring to fig. 1 to 6 and fig. 9 and 10, the oil inlet plate 4 is provided with an oil outlet hole 402 communicating with the control volume chamber 602, and the oil outlet control valve assembly includes: an oil outlet control valve sleeve 292 and an oil outlet plate 35 which are sequentially arranged from top to bottom and integrally formed with the electromagnetic valve sleeve 29; the oil outlet plate 35 is provided with an oil outlet orifice 206 communicated with the oil outlet hole 402, an oil outlet cavity 352 communicated with the oil outlet orifice 206, and an oil outlet pipe 353 communicated with the oil outlet cavity 352; the oil outlet pipe 353 is communicated with the oil return channel 207; a ball valve guide 33 installed in the oil outlet control valve housing 292, the ball valve guide 33 being disposed with respect to the control valve spool 32 and the oil outlet orifice 206; after the electromagnetic valve 24 is electrified to drive the control valve core 32 to move upwards, the ball valve guide rod 33 moves upwards under the action of oil pressure in the control volume cavity 602, so that the oil outlet throttle hole 206 is communicated with the oil outlet cavity 352, and fuel in the control volume cavity 602 flows into the oil return channel 207 through the oil outlet hole 402, the oil outlet throttle hole 206, the oil outlet cavity 352 and the oil outlet pipe 353 in sequence; after the solenoid valve spring 28 pushes the control valve core 32 to move downward, the control valve core 32 pushes the ball valve guide rod 33 to move downward, closing the outlet of the oil outlet orifice 206, and blocking the fuel entering the oil outlet orifice 206 from entering the oil outlet chamber 352.
The electromagnetic valve sleeve 29 and the oil outlet control valve sleeve 292 are integrally formed to form the supporting guide sleeve 29, and the supporting guide sleeve 29 is designed between the oil outlet plate 35 and the electromagnetic valve 24, so that the electromagnetic valve 24 is far away from the working area of heavy oil in the oil injector, and for the electromagnetic valve 24, the heat generated by heavy oil can be transmitted to the electromagnetic valve 24 as little as possible due to the far distance from the working area of heavy oil, thereby preventing the electromagnetic valve 24 from overheating. Meanwhile, the supporting guide sleeve 29 is respectively matched with the ball valve guide rod 33 and the control valve core 32 to form an even piece, so that the leakage quantity of fuel oil and cooling oil passing through gaps of the even piece is reduced, and the working areas of the electromagnetic valve 24 and the fuel oil are isolated from each other through dynamic sealing between the even pieces.
Preferably, referring to fig. 6, the injector lower body assembly includes: a control plunger sleeve 62, wherein a through hole communicated to the high-pressure fuel cavity 603 is formed in the end surface of the control plunger sleeve 62 facing the oil inlet orifice 4, one part of the control plunger sleeve passes through the high-pressure fuel cavity 603 and then is inserted into the through hole, and the other part of the control plunger sleeve is inserted into a needle valve 64 in the nozzle 67; the needle valve 64, the hole wall of the through hole and the oil inlet hole plate 4 are enclosed together to form the control volume cavity 602; the pressure regulating spring 63 is sleeved on the needle valve 64, and the pressure regulating spring 63 is limited between the control plunger sleeve 62 and a third limiting boss 641 protruding from the outer surface of the needle valve 64; after the fuel in the control volume 602 is partially depressurized, the needle valve 64 moves upward under the action of the oil pressure in the high-pressure fuel chamber 603 to form the first gap with the outlet chamber wall of the high-pressure fuel chamber 603; after the fuel in the control volume 602 is pressurized, the needle valve 64 moves downward by the oil pressure of the control volume 602 and the elastic force of the pressure regulating spring 63 to form a seal with the outlet chamber wall of the high pressure fuel chamber 603.
The needle valve 64, the control plunger sleeve 62 and the pressure regulating spring 63 are arranged in the middle holes of the needle valve body 61 and the nozzle 67, the upper end face of the control plunger sleeve 62 is attached to the lower end face of the oil inlet orifice plate 4, the lower end of the control plunger sleeve is supported by the pressure regulating spring 63, the pressure regulating spring 63 is supported on a spring supporting seat in the middle of the needle valve 64, and the outer circular surface of the upper end of the needle valve 64 is matched with the inner circular surface of the control plunger sleeve 62 by a coupling piece.
Specifically, referring to fig. 8, a second axial slot is formed on the outer surface of the portion of the needle valve 64 located in the high-pressure fuel chamber 603, a third conical surface 642 is formed on the outer surface of the needle valve 64 adjacent to the second axial slot, and a fourth conical surface 611 sealed with the third conical surface 642 is formed at the outlet chamber wall of the high-pressure fuel chamber 603; when the needle valve 64 moves upward, the third cone 642 and the fourth cone 611 form the first gap, and the fuel in the high-pressure fuel chamber 603 enters the nozzle 67 through the second axial slit and the first gap; the third taper 642 forms a seal with the fourth taper 611 as the needle 64 moves downward. The sealing principle between the third conical surface 642 and the fourth conical surface 611 is similar to that between the first conical surface 112 and the second conical surface 132, and will not be described here again.
Referring to fig. 4, a cooling cavity 204 is formed between the outer wall of the electromagnetic valve 24, the outer wall of the sleeve 25 and the inner wall of the injector body 22, the injector upper body 11 and the injector body 22 are sequentially perforated to form a cooling oil inlet channel 209 and a cooling oil return channel 210, and the cooling oil inlet channel 209 and the cooling oil return channel 210 are respectively communicated with the cooling cavity 204. The cooling oil cavity is designed around the electromagnetic valve 24, and the electromagnetic valve 24 is cooled by continuously circulating cooling oil, so that the working temperature of the electromagnetic valve 24 is reduced, and the working environment of the electromagnetic valve 24 is ensured.
In order to reduce the fuel leakage, in the present application, as shown in fig. 2 to 6, and fig. 9, the sleeve 25 is provided with a cooling oil through hole communicating with the cooling cavity 204; a mixing oil cavity 205 is formed among the outer wall of the electromagnetic valve sleeve 29, the outer wall of the oil outlet control valve sleeve 292 and the inner wall of the oil injector body 22, the upper oil injector body 11 and the oil injector body 22 are sequentially provided with holes to form a mixing oil return channel 208 communicated with the mixing oil cavity 205, and a transverse oil channel 293 communicated with the mixing oil cavity 205 is arranged at the joint of the electromagnetic valve sleeve 29 and the oil outlet control valve sleeve 292; the cooling oil in the cooling cavity 204 enters the sleeve 25 through the cooling oil through hole, flows into the mixing oil cavity 205 through a gap between the sleeve 25 and the control valve core 32, a gap between the control valve core 32 and the solenoid valve sleeve 29 and the transverse oil channel 293 in sequence, and the fuel oil entering the fuel outlet cavity 352 flows into the mixing oil cavity 205 through the gap between the ball valve guide rod 33 and the fuel outlet control valve sleeve 292 and the transverse oil channel 293, and flows into the mixing oil cavity 205, and the cooling oil and the fuel oil flowing into the mixing oil cavity 205 are mixed and then discharged outwards through the mixing oil return channel 208.
In order to prevent leakage of the mixed oil in the mixed oil chamber 205, as shown in fig. 2 to 6, an upper seal ring 31 is provided between the solenoid valve housing 29 and the inner wall of the injector body 22, a lower seal ring 34 is provided between the oil discharge control valve housing 292 and the inner wall of the injector body 22, and the mixed oil chamber 205 is located between the upper seal ring 31 and the lower seal ring 34.
The above-mentioned electric control fuel injector of the present invention mainly includes two states of the solenoid valve 24 being energized and the solenoid valve 24 not being energized when in use.
When the electromagnetic valve 24 is not electrified, the armature 26, the control valve core 32 and the ball valve guide rod 33 compress the ball head of the ball valve guide rod 33 on the sealing seat surface of the oil outlet plate 35 under the action of the electromagnetic valve spring 28, so that the sealing seat surface is in a sealing state. The needle valve 64 is in a closed state by the high-pressure fuel pressure and the pressure regulating spring 63.
After the electromagnetic valve 24 is electrified, electromagnetic force is generated, the armature 26 is acted by suction force from the electromagnetic valve 24, meanwhile, the control valve core 32 is driven to move upwards against the acting force of the electromagnetic valve spring 28, the pressing force at the upper end of the ball valve guide rod 33 is reduced, the ball valve guide rod 33 moves upwards under the action of hydraulic force at the lower end, the sealing seat surface at the lower end is opened, high-pressure fuel in the control volume cavity 602 flows out of the sealing seat surface through the oil outlet hole 402 and the oil outlet orifice 206, the fuel pressure in the control volume cavity 602 is gradually reduced, the needle valve 64 moves upwards against the acting force of the pressure regulating spring 63 under the action of hydraulic force at the lower end, the sealing surface of the nozzle 67 is opened, and the fuel in the high-pressure fuel cavity 603 is sprayed out from the spray hole at the end of the nozzle 67.
When the electromagnetic valve 24 is powered off, the electromagnetic force disappears, the control valve core 32 and the armature 26 move downwards under the action of the electromagnetic valve spring 28, the restoring force generated by the spring is transmitted to the ball valve guide rod 33 through the control valve core 32, the lower end face of the ball valve guide rod 33 seals the oil outlet orifice 206, high-pressure fuel in the oil injector enters a sealing state again, high-pressure fuel (diesel oil) in the oil inlet passage continuously enters the control volume cavity 602 and the high-pressure fuel cavity 603 of the oil injector, the fuel pressure in the control volume cavity 602 gradually rises, the needle valve 64 moves downwards under the double action of hydraulic pressure and spring force and closes the sealing face of the nozzle 67, and the oil injection process is finished.
When the pressure of the fuel flowing through the fuel inlet passage of the upper body 11 of the fuel injector is reduced to a certain limit pressure, the fuel injector cannot perform fuel injection, and the fuel injector is still full of fuel. At this time, the acting force of the circulation valve spring 12 is greater than the fuel hydraulic pressure of the lower end face of the circulation valve core 13, the circulation valve core 13 moves downwards under the action of the spring force and opens the sealing face of the circulation valve core 13, the fuel in the fuel injector enters the oil return channel 207 through the sealing face, the oil inlet channel and the oil return channel 207 are communicated with the high-pressure fuel cavity 603 in the fuel injector, and the fuel in the fuel injector enters the circulation mode to flow.
The middle support guide sleeve 29 in the injector body is matched with the ball valve guide rod 33 and the control valve core 32 in a matching way, in the continuous working process of the injector, the electromagnetic valve cooling cavity 204 is filled with low-pressure cooling oil, the control volume cavity 602 is filled with high-pressure fuel, the sealing seat surface of the lower end of the ball valve guide rod 33 and the oil outlet hole plate 35 is opened, a small amount of fuel can leak through the matching clearance between the ball valve guide rod 33 and the support guide sleeve 29, a small amount of cooling oil can leak through the matching clearance between the control valve core 32 and the support guide sleeve 29, the fuel and the cooling oil leak to the joint between the control valve core 32 and the ball valve guide rod 33, the fuel enters the mixing oil cavity 205 through the transverse oil duct 293 in the middle of the support guide sleeve 29, the two sealing rings of the outer ring of the support guide sleeve 29 can prevent the mixed oil in the mixing oil cavity 205 from leaking to other parts to pollute the cooling oil, and the mixed oil in the mixing cavity can be introduced to the outside the injector body 22 through the mixing oil return duct 208 of the injector body 22.
During operation of the fuel injector, the solenoid valve 24 receives heat from heavy oil, resulting in high operating temperature of the solenoid valve 24, and in order to prevent failure of the solenoid valve 24, a cooling cavity 204 and a cooling oil passage are designed around the solenoid valve 24. The cooling oil enters the solenoid valve cooling chamber 204 from the cooling oil inlet passage 209, flows in the solenoid valve cooling chamber 204 to take away heat, and flows out from the cooling oil return passage 210.
In this application, the sprayer includes sprayer upper body part 1, sprayer intermediate part 2 and sprayer lower body part 6, sprayer upper body 11, circulating valve spring 12 and circulating valve case 13 form sprayer upper body part 1 jointly, sprayer intermediate part 2 includes parts such as sprayer body 22, play oil orifice plate 35, support uide bushing 29, ball valve guide arm 33 and high-speed solenoid valve 24 jointly form sprayer intermediate part 2, advance oil orifice plate 4, needle valve body 61, control plunger sleeve 62, pressure regulating spring 63, needle valve 64 and parts such as nozzle 67 jointly form sprayer lower body part 6.
The electric control fuel injector can be suitable for the use environment with strong corrosiveness and high temperature of heavy oil, has the characteristics of flexibly adjusting fuel injection rule, accurately controlling circulating fuel injection quantity and the like, and meets the development requirement of a low-speed diesel engine. The invention has the advantages that:
(1) The electromagnetic valve 24 of the electric control oil injector adopts the design of isolation, sealing and cooling simultaneously by combining the special requirements of heavy oil for low-speed engine combustion, the electromagnetic valve 24 is isolated and sealed from the heavy oil working area by matching the support guide sleeve 29 with the coupling part formed between the ball valve guide rod 33 and the control valve core 32 respectively, and the cooling cavity 204 is designed around the electromagnetic valve 24 to cool the electromagnetic valve 24, so that the electromagnetic valve is suitable for the use environment of heavy oil.
(2) And a circulating valve is designed in the electric control fuel injector, when the fuel in the fuel injector is at low pressure, an oil inlet channel and a circulating oil return channel of the fuel injector are communicated through the circulating valve, heavy oil in the fuel injector is circularly flushed, the cleanliness of an oil cavity and the oil channel in the fuel injector is improved, and meanwhile, the heavy oil is prevented from solidifying in the fuel injector.
(3) The supporting guide sleeve 29 is designed in the electric control fuel injector, the supporting guide sleeve 29 separates the lower body part 6 of the fuel injector from the electromagnetic valve 24, and the installation position of the electromagnetic valve 24 can be flexibly adjusted by designing the height of the supporting guide sleeve 29.
(4) The seat surface seal of the oil outlet plate 35 adopts ball valve seal, the structure of the ball valve guide rod 33 is designed, the self-alignment neutrality of the ball valve and the guiding property and sealing property of the guide rod are fully utilized, and the seat surface seal of the oil outlet plate 35 and the axial dynamic seal and guiding property of the ball valve guide rod 33 are ensured.
(5) The mixing oil chamber 205 and the mixing oil passage are designed in the middle part of the injector body 22 for collecting and separately recovering the high-pressure fuel oil and the cooling oil leaked through the gap between the mating parts, thereby preventing mutual contamination between the fuel oil and the cooling oil.
Claims (9)
1. A heavy oil electronically controlled fuel injector for a low speed diesel engine, comprising: the oil sprayer comprises an oil sprayer upper body (11), an oil sprayer body (22), an oil inlet orifice plate (4), a needle valve body (61) and a nozzle (67) which are sequentially arranged from top to bottom;
The end face of the needle valve body (61) facing the oil inlet orifice (4) is respectively provided with a control volume cavity (602) and a high-pressure fuel cavity (603);
an oil inlet channel, an oil return channel (207) and a circulating oil channel are sequentially formed among the upper body (11), the oil injector body (22) and the oil inlet orifice plate (4), the outlet of the oil inlet channel is respectively communicated to the control volume cavity (602) and the high-pressure fuel cavity (603) through oil channels, and the circulating oil channel is communicated with the high-pressure fuel cavity (603); a circulation valve for blocking or conducting the fuel leakage in the high-pressure fuel cavity (603) is arranged in the circulation oil duct;
an electromagnetic valve assembly for powering on or off and an oil outlet control valve assembly for switching on or off the control volume cavity (602) and the oil return channel (207) are arranged in the oil sprayer body (22);
a high-pressure fuel cavity (603) of the needle valve body (61) is internally provided with a first gap or a sealed lower body assembly of the fuel injector, wherein the first gap is formed between the high-pressure fuel cavity (603) and a cavity wall of the high-pressure fuel cavity (603) for fuel in the high-pressure fuel cavity (603) to pass through;
when the electromagnetic valve assembly is electrified, heavy oil enters the control volume cavity (602) and the high-pressure fuel oil cavity (603) through the fuel inlet channel, the electromagnetic valve assembly drives the fuel outlet control valve assembly to conduct the control volume cavity (602) and the fuel return channel (207), and the heavy oil in the control volume cavity (602) leaks out through the fuel return channel (207) so as to reduce the oil pressure in the control volume cavity (602); after the oil pressure in the control volume cavity (602) is reduced, the lower body component of the oil injector moves upwards under the action of the oil pressure of the fuel in the high-pressure fuel cavity (603) so as to form a first gap with the cavity wall of the high-pressure fuel cavity (603), and heavy oil in the high-pressure fuel cavity (603) flows into the nozzle (67) through the first gap and is sprayed outwards; the circulating valve is closed to block the fuel in the high-pressure fuel cavity (603) from leaking;
When the electromagnetic valve assembly is powered off, heavy oil enters the control volume cavity (602) and the high-pressure fuel cavity (603) through the fuel inlet channel respectively, and the oil outlet control valve assembly breaks off the control volume cavity (602) and the oil return channel (207) so as to raise the oil pressure in the control volume cavity (602); after the oil pressure in the control volume cavity (602) rises, the lower body component of the oil injector moves downwards under the action of the oil pressure of the fuel in the control volume cavity (602) so as to form a seal with the cavity wall of the high-pressure fuel cavity (603), and the nozzle (67) stops injecting outwards;
after the spray nozzle (67) stops spraying outwards, diesel oil lower than heavy oil pressure enters the high-pressure fuel cavity (603) through the oil inlet channel, the circulation valve is opened, and the fuel oil in the high-pressure fuel cavity (603) is conducted to leak;
the circulating oil duct comprises a first circulating oil duct (103) arranged in the upper body (11) of the oil sprayer and a second circulating oil duct (202) arranged in the oil sprayer body (22); a first mounting groove (111) used for communicating with the first circulating oil duct (103) is formed on the end face of the upper oil sprayer body (11) facing the upper oil sprayer body (22), and a second mounting groove (221) used for communicating with the second circulating oil duct (202) is formed on the end face of the upper oil sprayer body (22) facing the upper oil sprayer body (11); the connecting surface of the first mounting groove (111) and the end surface of the upper body (11) of the oil sprayer forms a first conical surface (112);
The circulation valve includes: a circulation valve core (13) with one part arranged in the first mounting groove (111) and the other part arranged in the second mounting groove (221); a first axial cutting groove (131) is formed in the outer surface of a part, which is placed in the first mounting groove (111), of the circulating valve core (13), the circulating valve core (13) is placed in the first mounting groove (111), and a circulating valve spring (12) is arranged between the circulating valve core (13) and the groove bottom of the first mounting groove (111); a second conical surface (132) for forming conical surface sealing or a second gap with the first conical surface (112) is arranged on the outer surface of the circulating valve core (13);
when the oil pressure in the second circulation oil duct (202) is larger than the elastic force of the circulation valve spring (12), the circulation valve core (13) moves upwards under the action of the oil pressure in the second circulation oil duct (202), and conical surface sealing is formed between the first conical surface (112) and the second conical surface (132);
when the oil pressure in the second circulation oil duct (202) is smaller than the elastic force of the circulation valve spring (12), the circulation valve core (13) moves upwards under the action of the elastic force of the circulation valve spring (12), a second gap is formed between the first conical surface (112) and the second conical surface (132), and fuel in the second circulation oil duct (202) enters the first circulation oil duct (103) through the second gap and the first axial cutting groove (131) so as to be discharged outwards.
2. The heavy oil electronic control fuel injector for a low-speed diesel engine according to claim 1, wherein a through groove (133) is formed in an end surface of the circulation valve core (13) facing into the second circulation oil duct (202), and fuel in the second circulation oil duct (202) flows into a space between the circulation valve core (13) and the second mounting groove (221) through the through groove (133) and flows into the first circulation oil duct (103) through the second gap and the first axial cutting groove (131);
a first limit boss (134) for supporting the circulating valve spring (12) extends from the circulating valve core (13) towards the bottom of the first mounting groove (111), and a step surface for abutting the end part of the circulating valve spring (12) is formed between the first limit boss (134) and the circulating valve core (13).
3. The heavy oil electronically controlled fuel injector for a low speed diesel engine of claim 1, wherein said solenoid valve assembly comprises:
the device comprises a compression screw plug (21), an electromagnetic valve (24), a sleeve (25) and an electromagnetic valve sleeve (29) which are sequentially arranged from top to bottom;
an armature (26) mounted within the sleeve (25), the armature (26) being disposed relative to the solenoid valve (24);
A control valve core (32) mounted within the solenoid valve housing (29), the control valve core (32) partially passing through the sleeve (25) and connecting the armature (26);
a solenoid valve spring (28) sleeved on the control valve core (32);
electromagnetic force generated when the electromagnetic valve (24) is electrified attracts the armature (26) to drive the control valve core (32) to move upwards, and the control valve core (32) is pushed to move downwards by the repulsive force generated by the electromagnetic valve spring (28) when the electromagnetic valve (24) is powered off.
4. A heavy oil electronically controlled fuel injector for a low speed diesel engine according to claim 3, characterized in that the control spool (32) is provided with a second limit boss (321) protruding on the outer surface, the solenoid valve spring (28) being limited between the second limit boss (321) and the sleeve (25).
5. A heavy oil electronically controlled fuel injector for a low speed diesel engine according to claim 3, wherein the fuel inlet orifice plate (4) is provided with a fuel outlet (402) communicating with the control volume chamber (602), the fuel outlet control valve assembly comprising:
an oil outlet control valve sleeve (292) and an oil outlet orifice plate (35) which are sequentially arranged from top to bottom and are integrally formed with the electromagnetic valve sleeve (29); an oil outlet orifice (351) communicated with the oil outlet hole (402), an oil outlet cavity (352) communicated with the oil outlet orifice (351) and an oil outlet pipe (353) communicated with the oil outlet cavity (352) are arranged on the oil outlet orifice plate (35); the oil outlet pipe (353) is communicated with the oil return channel (207);
A ball valve guide rod (33) installed in the oil outlet control valve housing (292), the ball valve guide rod (33) being disposed with respect to the control spool (32) and the oil outlet orifice (351);
after the electromagnetic valve (24) is electrified to drive the control valve core (32) to move upwards, the ball valve guide rod (33) moves upwards under the action of oil pressure in the control volume cavity (602) to enable the oil outlet throttle hole (351) to be communicated with the oil outlet cavity (352), and fuel oil in the control volume cavity (602) flows into the oil return channel (207) through the oil outlet hole (402), the oil outlet throttle hole (351), the oil outlet cavity (352) and the oil outlet pipe (353) in sequence;
after the electromagnetic valve spring (28) pushes the control valve core (32) to move downwards, the control valve core (32) pushes the ball valve guide rod (33) to move downwards, the outlet of the oil outlet orifice (351) is closed, and fuel oil entering the oil outlet orifice (351) is blocked from entering the oil outlet cavity (352).
6. The heavy oil electronic control oil injector for a low-speed diesel engine according to claim 5, wherein a cooling cavity (204) is formed jointly among the outer wall of the electromagnetic valve (24), the outer wall of the sleeve (25) and the inner wall of the oil injector body (22), the upper oil injector body (11) and the oil injector body (22) are sequentially perforated to form a cooling oil inlet channel (209) and a cooling oil return channel (210), and the cooling oil inlet channel (209) and the cooling oil return channel (210) are respectively communicated with the cooling cavity (204).
7. The heavy oil electronic control injector for low-speed diesel engines according to claim 6, characterized in that said sleeve (25) is provided with a cooling oil passage hole communicating with said cooling cavity (204);
a mixing oil cavity (205) is formed between the outer wall of the electromagnetic valve sleeve (29), the outer wall of the oil outlet control valve sleeve (292) and the inner wall of the oil injector body (22), the upper oil injector body (11) and the oil injector body (22) are sequentially perforated to form a mixing oil return channel (208) communicated with the mixing oil cavity (205), and a transverse oil channel (293) communicated with the mixing oil cavity (205) is arranged at the joint of the electromagnetic valve sleeve (29) and the oil outlet control valve sleeve (292);
the cooling oil in the cooling cavity (204) enters the sleeve (25) through the cooling oil through hole, sequentially passes through a gap between the sleeve (25) and the control valve core (32), a gap between the control valve core (32) and the solenoid valve sleeve (29) and the transverse oil duct (293) to flow into the mixed oil cavity (205), and the fuel entering the oil outlet cavity flows into the mixed oil cavity (205) through the gap between the ball valve guide rod (33) and the oil outlet control valve sleeve (292) and the transverse oil duct (293), and the cooling oil and the fuel flowing into the mixed oil cavity (205) are mixed and then discharged outwards through the mixed oil return duct (208).
8. The heavy oil electronic control fuel injector for a low-speed diesel engine according to claim 5, wherein the nozzle (67) is partially sleeved on the outer surface of the needle valve body (61) in an interference fit manner, the nozzle (67) and the needle valve body (61) are compressed through a nozzle tightening cap (66), and the fuel injector body (22), the fuel inlet orifice plate (4) and the needle valve body (61) are compressed through an injector body tightening cap (65).
9. The heavy oil electronic control fuel injector for a low-speed diesel engine according to claim 7, characterized in that an upper sealing ring (31) is arranged between the electromagnetic valve sleeve (29) and the inner wall of the fuel injector body (22), a lower sealing ring (34) is arranged between the oil outlet control valve sleeve (292) and the inner wall of the fuel injector body (22), and the mixed oil cavity (205) is arranged between the upper sealing ring (31) and the lower sealing ring (34).
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| Application Number | Priority Date | Filing Date | Title |
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| CN201811635342.5A CN109404189B (en) | 2018-12-29 | 2018-12-29 | Heavy oil electric control fuel injector for low-speed diesel engine |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811635342.5A CN109404189B (en) | 2018-12-29 | 2018-12-29 | Heavy oil electric control fuel injector for low-speed diesel engine |
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| CN109404189A CN109404189A (en) | 2019-03-01 |
| CN109404189B true CN109404189B (en) | 2024-02-13 |
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Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN110594061B (en) * | 2019-09-26 | 2021-02-26 | 重庆红江机械有限责任公司 | Electric control common rail type heavy oil injector |
| CN111255552B (en) * | 2020-03-18 | 2023-08-15 | 上海中船三井造船柴油机有限公司 | Fuel injector of marine low-speed diesel engine and fuel system formed by fuel injector |
| CN113464337B (en) * | 2021-06-16 | 2023-05-30 | 中船动力研究院有限公司 | Common rail fuel injector for marine diesel engine |
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| US4394962A (en) * | 1981-02-23 | 1983-07-26 | Cummins Engine Company, Inc. | Solenoid operated fuel injector and control valve |
| CN206681891U (en) * | 2017-04-28 | 2017-11-28 | 重庆红江机械有限责任公司 | A kind of low leakage super-pressure electric-controlled fuel injector |
| CN207935021U (en) * | 2017-08-31 | 2018-10-02 | 重庆红江机械有限责任公司 | A kind of micro- injection injector of automatically controlled pressure maintaining type |
| CN209671121U (en) * | 2018-12-29 | 2019-11-22 | 重庆红江机械有限责任公司 | A kind of heavy oil electric-controlled fuel injector for low-speed diesel engine |
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2018
- 2018-12-29 CN CN201811635342.5A patent/CN109404189B/en active Active
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| Publication number | Priority date | Publication date | Assignee | Title |
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| US4394962A (en) * | 1981-02-23 | 1983-07-26 | Cummins Engine Company, Inc. | Solenoid operated fuel injector and control valve |
| CN206681891U (en) * | 2017-04-28 | 2017-11-28 | 重庆红江机械有限责任公司 | A kind of low leakage super-pressure electric-controlled fuel injector |
| CN207935021U (en) * | 2017-08-31 | 2018-10-02 | 重庆红江机械有限责任公司 | A kind of micro- injection injector of automatically controlled pressure maintaining type |
| CN209671121U (en) * | 2018-12-29 | 2019-11-22 | 重庆红江机械有限责任公司 | A kind of heavy oil electric-controlled fuel injector for low-speed diesel engine |
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