WO2021057018A1 - 一种电控共轨式重油喷油器 - Google Patents

一种电控共轨式重油喷油器 Download PDF

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Publication number
WO2021057018A1
WO2021057018A1 PCT/CN2020/086383 CN2020086383W WO2021057018A1 WO 2021057018 A1 WO2021057018 A1 WO 2021057018A1 CN 2020086383 W CN2020086383 W CN 2020086383W WO 2021057018 A1 WO2021057018 A1 WO 2021057018A1
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WIPO (PCT)
Prior art keywords
nozzle
guide sleeve
oil
needle valve
hole
Prior art date
Application number
PCT/CN2020/086383
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English (en)
French (fr)
Inventor
刘洋
陈超
张朝磊
刘惠娥
高浪
栗东民
林小雪
许强
Original Assignee
重庆红江机械有限责任公司
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Application filed by 重庆红江机械有限责任公司 filed Critical 重庆红江机械有限责任公司
Priority to FI20215086A priority Critical patent/FI130836B1/en
Priority to GB2018634.2A priority patent/GB2596882B8/en
Priority to DE112020000639.5T priority patent/DE112020000639T5/de
Publication of WO2021057018A1 publication Critical patent/WO2021057018A1/zh

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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
    • F02M53/00—Fuel-injection apparatus characterised by having heating, cooling or thermally-insulating means
    • F02M53/04—Injectors with heating, cooling, or thermally-insulating means
    • F02M53/043—Injectors with heating, cooling, or thermally-insulating means with cooling means other than air cooling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/025—Hydraulically actuated valves draining the chamber to release the closing pressure
    • 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
    • F02M51/0614—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of electromagnets or fixed armature
    • 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
    • F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
    • 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
    • F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
    • F02M61/182—Discharge orifices being situated in different transversal planes with respect to valve member direction of movement
    • 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
    • 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
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
    • F02M63/0036—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat with spherical or partly spherical shaped valve member ends
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/03—Fuel-injection apparatus having means for reducing or avoiding stress, e.g. the stress caused by mechanical force, by fluid pressure or by temperature variations
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/05—Fuel-injection apparatus having means for preventing corrosion
    • 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
    • F02M65/00—Testing fuel-injection apparatus, e.g. testing injection timing ; Cleaning of fuel-injection apparatus
    • F02M65/007—Cleaning
    • F02M65/008—Cleaning of injectors only

Definitions

  • the invention relates to a high-pressure common rail engine, in particular to an electronically controlled common rail injector.
  • the low-speed diesel engine in the prior art requires hydraulic drive for exhaust valve control, and is designed with a dedicated servo oil passage for driving oil. Therefore, heavy oil fuel injection relies on the addition of an additional servo oil driver outside the injector to perform remote hydraulic control of the injector. ⁇ Force control.
  • the application of servo oil prevents heavy oil and electronic components from contacting each other.
  • the pressure of servo oil is much lower than that of fuel.
  • the volume of the booster structure in the servo oil drive is large, which makes the external servo oil drive occupy a relatively large space and difficult to arrange. .
  • multiple injectors on the same cylinder can often only share one servo oil driver, which causes the fuel injection between the injectors to be unable to be independent of each other, and there is interference.
  • the movement of the exhaust valve causes the servo oil pressure to fluctuate, which in turn affects the work response of the servo oil driver, and indirectly affects the consistency of each injection of the injector.
  • the servo oil driver needs to be located farther away from the injector due to its large size, which causes a large delay in control.
  • the electronically controlled common rail fuel system is a fuel injection system based on mechanical, hydraulic and electrical technologies.
  • This system uses a common rail pipe with a certain volume between the fuel supply pump and the fuel injectors to accumulate fuel to suppress pressure fluctuations, and then deliver it to each fuel injector through the fuel pipe.
  • the fuel injection is controlled by the action of the solenoid valve of the fuel injector.
  • the opening and closing of the device This system has the advantages of stable fuel injection pressure, controllable fuel injection pressure and fuel injection process. Therefore, it is of great significance to study a new type of electronically controlled common rail heavy fuel injector that can put electromagnetic components inside the injector and reduce high temperature and heavy fuel pollution.
  • the present invention proposes an electronically controlled common rail type heavy oil injector.
  • the electromagnetic element is placed inside the injector, and the forced cooling structure is designed to effectively avoid thermal damage to the electronic components.
  • the oil sealing structure is designed to prevent the cooling oil from being polluted by heavy oil. Prevent heavy oil from corroding electromagnetic components and save installation space.
  • An electronically controlled common rail type heavy fuel injector includes: an injector body, an electro-hydraulic control component and a nozzle component.
  • An electronic interface is arranged in the middle of the top of the injector body of the injector, and the top is circumferentially arranged with an oil inlet interface, a circulating oil interface, a cooling oil inlet interface, a cooling oil outlet interface, an oil return interface, and a mixed oil interface.
  • the interfaces are respectively connected with the solenoid wire end, the oil inlet channel, the circulating oil channel, the cooling oil inlet channel, the cooling oil return channel, the fuel return channel, and the mixed oil drain channel.
  • the electro-hydraulic control component includes an electromagnet, a control valve return spring, an armature, a sleeve, a guide sleeve, a control valve core, a ball valve seat guide sleeve, a ball valve seat, a steel ball and a measuring orifice plate; the measuring orifice plate is arranged on Between the injector body and the nozzle component, there are oil inlet and outlet holes; the control valve core and the guide sleeve are matched together, and the hole in the guide sleeve can guide the control valve core for axial sliding;
  • the ball valve seat is arranged in the ball valve seat guide sleeve; the electromagnet, the sleeve, the guide sleeve, and the ball valve seat guide sleeve are assembled in the hole of the injector body from top to bottom, and are pressed on the measuring orifice plate by the compression nut ;
  • the control valve core, the ball valve seat, and the steel ball are in contact in
  • the circulating oil oil passage and the oil inlet oil passage lead into the nozzle component through the injector body and the orifice plate.
  • the nozzle component includes a needle valve guide sleeve, a needle valve, a needle valve return spring, a pressure regulating gasket, a body tightening cap, a needle valve body, a nozzle locking nut and a nozzle; the needle valve guide sleeve, The needle valve is matched with the needle valve body as a coupler.
  • the upper and lower sliding surfaces of the needle valve can respectively slide axially in the middle hole of the needle valve body and the middle hole of the needle valve guide sleeve; the two ends of the needle valve return spring are respectively pressed
  • the needle valve guide sleeve and the needle valve make the top of the needle valve guide sleeve pressed against the lower plane of the measuring orifice plate, and the lower cone surface of the needle valve abuts against the cone surface of the hole in the needle valve body;
  • the bottom cylindrical surface of the needle valve body passes through the nozzle counterbore Fit, the nozzle has a spray hole for injecting fuel;
  • the body tight cap connects the nozzle member to the fuel injector body, and presses the top surface of the needle valve body against the bottom end of the orifice plate; the circulating oil passage,
  • the oil inlet passage leads into the middle hole of the needle valve body through the injector body and the orifice plate.
  • the measuring orifice plate, the needle valve guide sleeve, and the needle valve are surrounded to form a pressure control chamber, which communicates with the outside through the oil inlet and outlet holes;
  • the fuel return passage is on the injector body and is connected to the oil outlet.
  • the measuring holes are separated by steel balls;
  • the mixed oil drain channel is connected to the ring cavity enclosed by the ring groove in the middle of the guide sleeve and the sealing ring;
  • the cooling oil inlet channel and the cooling oil return channel are connected by the electromagnet,
  • the oil cavity enclosed by the guide sleeve and the sealing ring is communicated with each other through the slot hole on the sleeve.
  • the nozzle includes a nozzle body and an ejector rod matched with the nozzle body; the nozzle body is interference-installed on the needle valve body, and the ejector rod is rigidly connected to the needle valve head or processed with the needle valve head.
  • the ejector rod has a central longitudinal hole and a horizontal hole, which connect the upper cavity of the nozzle with the lower cavity of the nozzle, and the nozzle hole on the nozzle body is located within the width of the middle cavity of the nozzle; when the injector is in the spraying state, the nozzle body and the ejector rod
  • the lower tight fitting surface is staggered to make the nozzle lower cavity communicate with the nozzle middle cavity.
  • the length of the nozzle is greater than or equal to 19 mm.
  • the needle valve body and the nozzle body are combined with a nozzle lock nut on the outer jacket.
  • the upper end of the nozzle lock nut is threadedly connected with the needle valve body.
  • the inner wall of the tight cap tightly covers the needle valve body and the nozzle body.
  • the lower end of the tightening cap has a taper angle. And the thickness is designed to match the cone angle of the installation seat surface required by the injector and the length of the nozzle extending into the cylinder.
  • a ring groove is opened on the outer side of the middle of the guide sleeve, and a transverse through hole in the middle of the groove passes through the hole of the guide sleeve; there are sealing ring grooves on both sides of the ring groove; the diameter of the bottom end of the control valve core is larger than the guide section, and the guide section has three channels The ring groove and the second ring groove are communicated with the transverse through hole in the middle of the guide sleeve.
  • the control valve core, the guide sleeve and the sealing ring divide the hole in the injector body into three chambers.
  • the electromagnetic element is directly designed into the injector, and the servo oil driver of the old heavy fuel fuel system is eliminated, which saves space.
  • the electronic control system can change the working law of a single injector at any time. Different injectors are different from each other. Affected.
  • the internal part of the fuel injector is divided into three chambers through the electro-hydraulic control component.
  • the electromagnetic element directly contacts the cooling oil, and the cooling oil circuit is isolated from the fuel oil circuit by means of dynamic sealing, static sealing and drainage.
  • the technical scheme disclosed in the present invention can be applied to a high-pressure common rail system using heavy oil as fuel, and can effectively avoid the corrosion and thermal damage of the electromagnetic element caused by the heavy oil.
  • the electro-hydraulic control component adopts the ball valve as the control valve, which has good self-alignment.
  • the top of the orifice plate is provided with a sink groove for installing the ball valve seat guide sleeve to install the ball valve seat guide sleeve.
  • the guide sleeve has a certain ability to guide the axial movement of the ball valve seat, preventing the steel ball from deflecting laterally due to the inclined installation angle of the injector, and further improving the working stability.
  • the ball valve seat guide sleeve and the ball valve seat can be directly removed from the orifice plate as a single piece, which is convenient for the replacement of wear and damage due to the needs of the injector control valve lift adjustment.
  • the improved nozzle structure can keep the injector needle valve sealing seat surface away from gas and high temperature environments, which can effectively reduce the damage to the injector needle valve seat surface in high temperature environments and inferior fuel, and save installation space.
  • the two close-fitting surfaces of the nozzle and the ejector pin divide the nozzle into three cavities. This cooperation reduces the cavity volume in the nozzle, thereby reducing the phenomenon of oil dripping, and further reducing the impact of insufficient combustion on the life of low-speed diesel engines.
  • the nozzle hole on the nozzle body can be located within the width of the nozzle cavity, so that the design position space of the fuel injection hole is larger.
  • it has the advantages of A certain modification potential makes the nozzle easy to modify and apply to other forms of low-speed diesel injectors.
  • Figure 1 is a schematic diagram of the structure of the present invention
  • Figure 2 is a schematic diagram of the electrical and hydraulic interface of the present invention.
  • Figures 3 and 3a are enlarged views of the ball valve seat and ball valve guide sleeve of the present invention.
  • Figure 4 is a schematic diagram of the nozzle component of the present invention.
  • FIGS. 5 and 5a are schematic diagrams of the electro-hydraulic control component of the present invention.
  • FIG. 6 is a schematic diagram of the cooling structure of the present invention.
  • FIG. 7 is a schematic diagram of the cooling oil pollution prevention structure of the present invention.
  • Fig. 8 is a schematic diagram of the structure of the nozzle part of the present invention.
  • Figure 1 shows an electronically controlled common rail heavy fuel injector with a specific structure, which includes three parts: an injector body, an electro-hydraulic control component, and a nozzle component.
  • an electronic interface (23) is arranged in the middle of the top of the injector body (1) of the injector, and an oil inlet (24) and a circulating oil interface (25) are arranged circumferentially on the top.
  • the oil passage (101), the cooling oil inlet passage (107), the cooling oil return passage (108), the fuel return passage (105), and the mixed oil drain passage (106) are connected.
  • the structure of the electro-hydraulic control component can be seen in conjunction with Figure 1, Figure 5, Figure 6 and Figure 7, which includes a compression nut (2), an electromagnet (3), a control valve return spring (4), and a nut (5) , Armature (6), sleeve (7), guide sleeve (8), control valve core (9), sealing ring (10), ball valve seat guide sleeve (11), ball valve seat (12), steel ball (13) ), orifice plate (14).
  • the metering orifice plate (14) is located between the injector body (1) and the nozzle member, and is provided with an oil inlet metering hole (103) and an oil metering hole (105) inside, and the lower end is in contact with the nozzle member.
  • the control valve core (9) and the guide sleeve (8) are mated parts, and the middle hole of the guide sleeve (8) can guide the control valve core (9) for axial sliding.
  • the ball valve seat (12) is arranged in the ball valve seat guide sleeve (11).
  • the electromagnet (3), the sleeve (7), the guide sleeve (8), and the ball valve seat guide sleeve (11) are assembled in the middle hole of the injector body (1) in sequence, and are pressed in by the compression nut (2) On the measuring orifice plate (14).
  • the armature (6) and the top thread of the control valve core (9) are fixed with a nut (5).
  • control valve core (9), the ball valve seat (12), and the steel ball (13) are in contact with each other in sequence, and the control valve return spring (4) located in the hole in the electromagnet (3) is pressed against the sealing cone of the measuring orifice (14) Block the oil outlet hole (105); the sealing ring (10) is sleeved in the sealing ring groove on the outer side of the guide sleeve (8).
  • the needle valve guide (15) and the needle valve (16) are both matched with the needle valve body (20).
  • the two sliding surfaces of the needle valve (16) can respectively be in the hole and the needle valve body (20).
  • the guide sleeve (15) slides axially in the hole; both ends of the needle valve return spring (17) respectively press the needle valve guide sleeve (15) and the needle valve (16), so that the top of the needle valve guide sleeve (15) is pressed tightly On the lower plane of the orifice plate (14), the cone surface of the lower end of the needle valve (16) can resist the cone surface of the hole in the needle valve body (20).
  • the pressure regulating gasket (18) adjusts the pressing force; the cylindrical surface of the bottom end of the needle valve body (20) is in interference fit with the counterbore of the nozzle (22), which is further fixed by the nozzle lock nut (21), and the nozzle (22) It has spray holes to inject fuel.
  • the body tightening cap (19) connects the nozzle component to the fuel injector body (1) and presses the top surface of the needle valve body (20) against the bottom end of the orifice plate (14).
  • the circulating oil oil passage (101) and the oil inlet oil passage (102) lead into the middle hole of the needle valve body (20) via the injector body (1) and the orifice plate (14).
  • the measuring orifice plate (14), the needle valve guide sleeve (15), and the needle valve (16) surround the pressure control chamber (104), which communicates with the outside through the oil inlet hole (103) and the oil outlet hole (105).
  • the fuel oil return passage (106) is on the injector body (1), and is separated from the oil metering hole (105) by a steel ball (13).
  • the mixed oil drain channel (107) is connected to the ring cavity enclosed by the central ring groove of the guide sleeve (8) and the sealing ring (10).
  • the cooling oil inlet passage (108) and the cooling oil return passage (109) are connected to the oil cavity enclosed by the electromagnet (3), the guide sleeve (8) and the sealing ring (10), and pass through the sleeve (7).
  • the slots on) communicate with each other.
  • a ring groove (110) is opened on the outer side of the middle of the guide sleeve (8), and a transverse through hole in the middle of the groove passes through the hole of the guide sleeve (8); there are sealing ring grooves on both sides of the ring groove.
  • the diameter of the bottom end of the control valve core (9) is larger than that of the guide section, and the guide section is provided with three ring grooves (111) and the second ring groove is communicated with the transverse through hole in the middle of the guide sleeve (8).
  • the control valve core (9), the guide sleeve (8) and the sealing ring (10) divide the middle hole of the injector body (1) into three chambers.
  • Fig. 3 and Fig. 3a it can be seen that there is a countersink in the middle of the top end of the orifice plate (14).
  • the ball valve seat guide sleeve (11) can be inserted into the countersink of the measuring orifice plate (14); the upper half of the hole in the ball valve seat guide sleeve (11) is larger than the lower half, and the lower half is in clearance fit with the ball seat (12),
  • the lower half of the middle hole of the guide sleeve (11) has a certain guiding ability for the axial movement of the ball valve seat (12); a cross milling groove is opened at the top, and three milling grooves are evenly distributed on the guiding surface of the ball valve seat (12).
  • the upper chamber of the steel ball (13) is connected with the fuel oil return passage (105).
  • the nozzle (22) used in this embodiment includes a nozzle body (222) and an ejector rod (221) matched with it; the nozzle body (222) and the needle valve body pass through the nozzle interference assembly surface (223). ) Interference installation, the ejector rod is rigidly connected to the needle valve head of the injector to which the nozzle is applied or processed as a whole with the needle valve head.
  • the length of the fuel injection nozzle is greater than 19mm, and the nozzle body (222) and the ejector rod (221) are both arranged below the sealing seat surface of the needle valve assembly.
  • the two small diameter surfaces in the middle of the nozzle body (222) are radially matched with the ejector rod (221) to form two close fitting surfaces, namely the upper nozzle tight fitting surface (225) and the nozzle lower tight fitting surface (227) .
  • the clearance between the ejector rod (221) and the nozzle body (222) on the tightly fitting surface is very small, which has a guiding effect on the ejector rod and has a better sealing ability.
  • the upper fitting surface (225) of the nozzle and the lower fitting surface (226) of the nozzle divide the oil cavity between the nozzle body (222) and the ejector rod (221) into the nozzle upper cavity (224), the nozzle middle cavity (226) and the nozzle There are three parts of the lower cavity (228).
  • the ejector rod (221) is provided with a central longitudinal hole (2210) and a transverse hole (2211), which communicates the nozzle upper cavity (224) with the nozzle lower cavity (228).
  • the spray holes (229) are all arranged in the nozzle cavity (226).
  • the working principle of the nozzle is as follows:
  • the conical surface on the needle valve and the seat surface on the needle valve body form a sealing effect, and the high-pressure fuel to be injected accumulates above the sealing seat surface.
  • the needle valve In the injection state, the needle valve is lifted by the mechanical force or hydraulic pressure provided by the control end of the fuel injector, the sealing seat surface opens, and the needle valve drives the ejector rod (221), the nozzle body (222) and the ejector rod (221)
  • the lower fitting surface (227) is staggered so that the nozzle lower cavity (228) is communicated with the nozzle middle cavity (226).
  • the high-pressure fuel above the sealing seat surface flows into the nozzle middle cavity (226) through the sealing seat surface, the nozzle upper cavity (224), the transverse hole (2211), the longitudinal hole (2210) and the nozzle lower cavity (228), and finally from The nozzle hole (229) arranged in the nozzle center cavity (226) is injected into the cylinder to participate in combustion.
  • the control end of the fuel injector does not provide force, and the needle valve falls under the action of spring force or other kinds of restoring force, and is re-pressed on the sealing seat surface, and the high-pressure fuel is sealed on the sealing seat surface.
  • the nozzle body (222) and the lower tight fitting surface (227) of the ejector rod (221) are reattached to each other, so that the lower nozzle cavity (228) and the nozzle middle cavity (226) are disconnected.
  • the upper nozzle fitting surface (225) and the nozzle lower fitting surface (227) separate the nozzle upper cavity (224) and the nozzle lower cavity (228) from the nozzle middle cavity (226), respectively, and are located in the nozzle upper cavity (224) And the residual oil in the lower cavity (228) of the nozzle cannot flow to the nozzle hole (229), and the fuel injection stops. At this time, the exhaust gas after combustion in the cylinder can only contact the nozzle cavity (226) through the nozzle hole (229), and will not corrode the sealing seat surface of the needle valve assembly.
  • the needle valve assembly It can be arranged in a cylinder head that is far away from the cylinder and has a relatively good cooling condition, which can effectively reduce the damage to the needle valve sealing seat surface of the injector in a high-temperature environment and inferior fuel. Since the diameter of the nozzle is smaller than the diameter of the needle valve body, the required installation hole can be appropriately reduced, saving installation space for the cylinder wall measurement, and providing room for other arrangements such as air valves that need to be installed on the cylinder wall measurement equipment.
  • the nozzle body is made of corrosion-resistant and heat-resistant materials with a small thermal expansion coefficient, which can reduce the thermal deformation of the nozzle body when heated, and indirectly stabilize the gap width between the nozzle body and the ejector rod, and ensure stable operation.
  • the heavy oil fuel flows into the middle hole of the needle valve body (20) through the oil inlet port (24) and the oil inlet oil passage (103), and then flows into the pressure control chamber ( 104).
  • the control valve core (9) presses the ball valve seat (12) to make the steel ball (13) abut the oil outlet (105).
  • the fuel pressure in the pressure control chamber (104) is equal to the pressure in the hole in the needle valve body (20).
  • Both ends of the needle valve (16) are subjected to the fuel pressure and the spring force transmitted by the needle valve return spring (17), the direction of the needle valve (16) is downward to maintain the seated state, and the lower end cone of the needle valve (16) can resist the needle valve Body (20) injection end.
  • the hydraulic pressure in the pressure control chamber (104) gradually decreases, and the hydraulic pressure difference between the two sides of the needle valve (16) increases.
  • the needle valve (16) moves upwards and opens the seal with the needle valve body (20).
  • the nozzle (22) sprays out and the fuel injection process starts.
  • the high-pressure oil part of the fuel injector connects the circulating oil passage (101) with the circulating oil interface (25), and provides an oil passage for installing an external circulating oil valve.
  • the function of the circulating fuel valve is that when the fuel injector is working normally, the circulating fuel valve is closed and does not affect the normal operation of the fuel injector; when the fuel system is about to shut down, the system changes to a certain low-pressure cleaner fuel to flow into the fuel injector. At this time, the circulating oil valve is opened due to the low pressure, and the fuel can flow in the injector at a certain speed to clean the remaining heavy oil and prevent the remaining heavy oil with many impurities from cooling and making the mating parts sticky and clogging the pores.
  • the cooling oil inlet passage (108) and the cooling oil return passage (109) are connected to the oil cavity enclosed by the electromagnet (3), the guide sleeve (8) and the sealing ring (10), and pass through the sleeve (7).
  • the slots on) communicate with each other. Forced cooling through the flow of cooling oil takes away heat, avoiding thermal damage to electronic components caused by high temperature caused by heavy oil.
  • the control valve core (9), the guide sleeve (8) and the sealing ring (10) divide the middle hole of the injector body (1) into three chambers.
  • the upper cooling oil cavity, the lower heavy oil return cavity, the middle is statically sealed by the sealing ring (10) and the planes of each part, and the control spool (9) has three ring grooves (111) on the guide section to strengthen and guide the sleeve Dynamic sealing between the cylinders (8).
  • the second ring groove on the guide section of the control spool (9) is connected with the transverse through hole in the middle of the guide sleeve (8), and the heavy oil and the cooling oil are separated from each other.
  • first and third ring grooves leak into the second ring groove, they pass through the middle ring groove (110) of the guide sleeve (8) and the mixed oil drain channel (107), and finally from the mixed oil interface (29) Lead out to further reduce the hydraulic pressure at the second ring groove of the guide section of the control valve core (9).
  • the cooling oil pressure in the third ring groove above and the lower mixed oil pressure at the second ring groove form a downward direction.
  • the pressure difference prevents heavy oil from being squeezed by the guide surface and leaking upward.
  • the cooling oil circuit is isolated from the fuel oil circuit by means of static sealing, dynamic sealing and drainage. This technical solution can effectively avoid the pollution of the heavy oil to the cooling oil, and further avoid the corrosion of the electromagnetic components.
  • the electro-hydraulic control component adopts a ball valve as the control valve, and the ball valve has good self-alignment.
  • the guide sleeve has a certain guiding ability for the axial movement of the ball valve seat, preventing the steel ball (13) from lateral deviation due to the inclined installation angle of the fuel injector, and further improving the working stability.
  • the ball valve seat guide sleeve and the ball valve seat can be directly removed from the orifice plate as a single piece, which is convenient for the replacement of wear and damage due to the needs of the injector control valve lift adjustment.

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Abstract

电控共轨式重油喷油器，包括：喷油器体（1）、电液控制构件、喷嘴构件，电液控制构件中导向套筒（8）外侧中部开有环槽（110），环槽（110）中部有横向通孔直通导向套筒（8）中孔，环槽（110）两边有密封圈（10），将喷油器体（1）内部分成三个腔室。控制阀芯（9）导向段上开有三道环槽（111），且第二道环槽（111）与导向套筒（8）中部横向通孔连通。电磁元件与冷却油接触，通过动密封、静密封、引流的方式，使冷却油路与燃油油路相隔离，能够有效避免重油对电子元件的腐蚀与热损伤；量孔板（14）顶端中间开有沉槽，球阀座导向套（11）能够套入量孔板（14）沉槽内，并与球阀座（12）间隙配合，对球阀座（12）轴向运动具有一定导向能力。

Description

一种电控共轨式重油喷油器 技术领域
本发明涉及高压共轨发动机，具体涉及电控共轨式喷油器。
背景技术
随着航运企业运输成本不断攀升，利用重油(可燃用劣质燃油)作为燃油的发动机在成本压缩上具有独到的优势。重油由于其杂质多，对零件具有一定的腐蚀性，易产生粘滞，对于电子元件也有一定腐蚀性，同时重油黏性大，使用时需要高温加热，过高的油温会导致电子元件寿命缩短。对于如何改善这一问题，是提高重油柴油机使用寿命的重要热点。
现有技术的低速柴油机由于其排气阀控制需要液压驱动，设计有专门输送驱动用油的伺服油道，于是重油燃油喷射依靠在喷油器外部额外增加伺服油驱动器对喷油器进行远程液力控制。伺服油的应用使重油与电子元件间不会互相接触，然而伺服油压力比燃油压力低很多，伺服油驱动器内增压结构体积大，致使外置的伺服油驱动器占据空间比较大，空间布置困难。因此同一气缸上的多个喷油器经常只能共用一个伺服油驱动器，导致各喷油器间燃油喷射无法互相独立，存在干涉。同时排气阀运动引起伺服油压力波动，进而影响伺服油驱动器的工作响应，间接影响喷油器各次喷射一致性。再者伺服油驱动器由于体积过大需布置在喷油器较远处，控制上产生延迟较大。
电控共轨燃油系统是建立在机、液、电技术基础之上的一种喷油系统。这种系统采用设置在供油泵和喷油器之间的具有一定容积的共轨管蓄积燃油以平抑压力波动，再通过油管输送至各个喷油器，由喷油器电磁阀的动作控制喷油器的启闭。这种系统具有喷油压力稳定、喷油压力与喷油过程可控等优点。因此，研究一种能将电磁元件置于喷油器内部还能够减少高温、重油污染的新型电控共轨式重油喷油器具有其重要意义。
发明内容
本发明提出一种电控共轨式重油喷油器，将电磁元件置于喷油器内部，通过设计强制冷却结构有效避免电子元件的热损伤，同时通过设计封 油结构防止冷却油被重油污染防止重油对电磁元件的腐蚀，节省安装空间。
本发明的技术方案如下：
一种电控共轨式重油喷油器，包括：喷油器体、电液控制构件和喷嘴构件。
所述喷油器的喷油器体顶端中间布置有电子接口，顶端成周向布置有进油接口、循环油接口、冷却进油接口、冷却出油接口、回油接口、混合油接口，这些接口分别与电磁铁电线端、进油油道、循环油油道、冷却油进油道、冷却油回油道、燃油回油道、混合油排油道相连接。
所述电液控制构件包括电磁铁、控制阀复位弹簧、衔铁、套筒、导向套筒、控制阀芯，球阀座导向套、球阀座、钢球和量孔板；所述量孔板设置在喷油器体与喷嘴构件之间，其内部设置进油量孔和出油量孔；控制阀芯与导向套筒为偶件配合，导向套筒中孔能够导向控制阀芯作轴向滑动；球阀座布置于球阀座导向套中；电磁铁、套筒、导向套筒、球阀座导向套从上到下依次装配于喷油器体中孔，由压紧螺帽压紧在量孔板上；控制阀芯、球阀座、钢球依次接触，由位于电磁铁中孔的控制阀复位弹簧压紧在量孔板密封锥面上，堵住出油量孔；导向套筒通过外侧两个密封圈槽安装密封圈进行密封。
所述量孔板顶端中间开有沉槽，球阀座导向套套入所述沉槽内；球阀座导向套中孔上半段开口大于下半段，下半段与球阀座间隙配合，对球阀座轴向运动具有一定导向能力。球阀座导向套顶端开有十字铣槽，球阀座的导向面上均布有三个铣槽。通过球阀座与球阀座导向套上的铣槽，使钢球上方腔室与燃油回油道相连通。。
所述循环油油道、进油油道经由喷油器体、量孔板通入喷嘴构件。
进一步地，所述喷嘴构件包括针阀导套、针阀、针阀复位弹簧、调压垫片、器体紧帽、针阀体、喷嘴锁紧螺帽和喷嘴；所述针阀导套、针阀均与针阀体作偶件配合，针阀的上下两个滑动面分别能够在针阀体中孔与针阀导套中孔中作轴向滑动；针阀复位弹簧两端分别压住针阀导套与针阀，使针阀导套顶端压紧在量孔板下平面，针阀下端锥面抵住针阀体中孔锥面；针阀体底端圆柱面与喷嘴沉孔过盈配合，喷嘴上具有喷孔用以喷射燃 油；器体紧帽将喷嘴构件连接于喷油器体，并使针阀体顶端面压紧于量孔板底端；所述循环油油道、进油油道经由喷油器体、量孔板通入针阀体中孔。
进一步地，所述量孔板、针阀导套、针阀包围形成压力控制室，通过进油量孔和出油量孔与外界连通；燃油回油道在喷油器体上，与出油量孔间由钢球相隔开；混合油排油道连通于由导向套筒中部环槽和密封圈围成的环腔；冷却油进油道、冷却油回油道连通于由电磁铁、导向套筒与密封圈围成的油腔，并通过套筒上的槽孔互相连通。
进一步地，所述喷嘴包括喷嘴体和与之相配合的顶杆；所述喷嘴体过盈安装于所述针阀体上，顶杆刚性连接在针阀头部或与针阀头部加工为一体；所述喷嘴体和与之相配合的顶杆间存在上下两个紧密配合面，将喷嘴体与顶杆间的油腔分为喷嘴上腔、喷嘴中腔和喷嘴下腔三个部分，顶杆上具有中心纵向孔与横向孔，将喷嘴上腔与喷嘴下腔连通，喷嘴体上的喷孔位于喷嘴中腔宽度范围内；当喷油器处于喷射状态时，喷嘴体与顶杆的下部紧配面错开，使喷嘴下腔与喷嘴中腔连通，当喷油器处于停喷状态时，喷嘴体与顶杆的下部紧配面互相贴合，使喷嘴下腔与喷嘴中腔断开。
所述喷嘴的长度大于等于19mm。
在针阀体与喷嘴体结合的部位外套装有喷嘴锁紧螺帽，喷嘴锁紧螺帽上端与针阀体螺纹连接，紧帽内壁紧套住针阀体与喷嘴体，紧帽下端锥角和厚度则与喷油器需要的安装座面锥角和喷嘴伸入气缸长度相配合设计。
进一步地，导向套筒中部外侧开有环槽，槽中部有横向通孔直通导向套筒中孔；环槽两边有密封圈槽；控制阀芯底端直径大于导向段，导向段上开有三道环槽且第二道环槽与导向套筒中部横向通孔连通。控制阀芯、导向套筒和密封圈将喷油器体中孔分成三个腔室。
本发明有益技术效果为：
1)将电磁元件直接设计进入喷油器中，取消了旧式重油燃油系统的伺服油驱动器，节省了空间，运用电控系统可随时改变单个喷油器的工作规律，不同喷油器间相互不受影响。
2)通过电液控制构件将喷油器体内部分成三个腔室，电磁元件直接与冷却油接触，通过动密封、静密封、引流的方式，使冷却油路与燃油油路 相隔离。本发明公开的技术方案能够应用于以重油为燃油的高压共轨系统中，能够有效避免重油对电磁元件的腐蚀与热损伤。
3)电液控制构件采用球阀为控制阀，有较好的自找正性。量孔板顶端中间开有安装球阀座导向套的沉槽，以安装球阀座导向套。导向套对球阀座轴向运动具有一定导向能力，防止因喷油器倾斜安装角度问题使钢球侧向偏移，进一步提高工作稳定性。同时，球阀座导向套与球阀座作为单件可直接从量孔板上取下，方便因喷油器控制阀升程调整需要而进行配磨和损坏后的更换。
4)采用改进的喷嘴结构，可以使喷油器针阀密封座面远离燃气与高温环境，能够有效减少高温环境及劣质燃油对喷油器针阀密封座面的损伤，节省安装空间。同时喷嘴与顶杆的两个紧密配合面将喷嘴分成了三个腔，这种配合减少了喷嘴内空腔容积，由此减少了滴油现象，进一步减小燃烧不充分对低速柴油机寿命的影响。并且由于喷油嘴的上中下三腔设计，使得喷嘴体上的喷孔可以位于喷嘴中腔宽度范围内，使喷油孔的设计位置空间更大，对于生产设计厂家而言，其具有了一定的改装潜力，使该喷嘴便于改装应用在其他形式的低速柴油机喷油器上。
附图说明
图1是本发明的结构示意图；
图2是本发明的电、液接口示意图；
图3和图3a是本发明的球阀座、球阀导向套放大图；
图4是本发明的喷嘴构件示意图；
图5和图5a是本发明的电液控制构件示意图；
图6是本发明的冷却结构的示意图；
图7是本发明的防冷却油污染结构的示意图；
图8为本发明的喷嘴部分的结构示意图。
其中，1-喷油器体、2-压紧螺帽、3-电磁铁、4-控制阀复位弹簧、5-螺母、6-衔铁、7-套筒、8-导向套筒、9-控制阀芯、10-密封圈、11-球阀座导向套、12-球阀座、13-钢球、14-量孔板、15-针阀导套、16-针阀、17-针阀复位弹簧、18-调压垫片、19-器体紧帽、20-针阀体、21-喷嘴锁紧螺帽、22-喷嘴、23-电子接口、24-进油接口、25-循环油接口、26-冷却进油 接口、27-冷却出油接口、28-回油接口、29-混合油接口、101-循环油油道、102-进油油道、103-进油量孔、104-压力控制室、105-出油量孔、106-燃油回油道、107-混合油排油道、108-冷却油进油道、109-冷却油回油道、110-导向套环槽、111-阀芯环槽、221-顶杆、222-喷嘴体。
具体实施方式
以下结合附图对本发明进行详细描述。
图1所示为一种具体结构的电控共轨式重油喷油器，其包括：喷油器体、电液控制构件、喷嘴构件三部分。
结合图1和图2可见，所述喷油器的喷油器体(1)顶端中间布置有电子接口(23)、顶端成周向布置有进油接口(24)、循环油接口(25)、冷却进油接口(26)、冷却出油接口(27)、回油接口(28)、混合油接口(29)，分别与电磁铁(3)电线端、进油油道(102)、循环油油道(101)、冷却油进油道(107)、冷却油回油道(108)、燃油回油道(105)、混合油排油道(106)相连接。
所述电液控制构件的结构结合图1、图5、图6和图7可见，其包括压紧螺帽(2)、电磁铁(3)、控制阀复位弹簧(4)、螺母(5)、衔铁(6)、套筒(7)、导向套筒(8)、控制阀芯(9)、密封圈(10)、球阀座导向套(11)、球阀座(12)、钢球(13)、量孔板(14)。其中量孔板(14)位于喷油器体(1)与喷嘴构件之间，其内部设置进油量孔(103)和出油量孔(105)，下端与喷嘴构件接触。控制阀芯(9)与导向套筒(8)为偶件配合，导向套筒(8)中孔能够导向控制阀芯(9)作轴向滑动。球阀座(12)布置于球阀座导向套(11)中。电磁铁(3)、套筒(7)、导向套筒(8)、球阀座导向套(11)依次装配于喷油器体(1)中孔，由压紧螺帽(2)压紧在量孔板(14)上。衔铁(6)与控制阀芯(9)顶端螺纹用螺母(5)固定。控制阀芯(9)、球阀座(12)、钢球(13)依次接触，由位于电磁铁(3)中孔的控制阀复位弹簧(4)压紧在量孔板(14)密封锥面上，堵住出油量孔(105)；密封圈(10)套于导向套筒(8)外侧密封圈槽中。
结合图1和图4，所述喷嘴构件针阀导套(15)、针阀(16)、针阀复位弹簧(17)、调压垫片(18)、器体紧帽(19)、针阀体(20)、喷嘴锁紧螺帽(21)、喷嘴(22)。针阀导套(15)、针阀(16)均与针阀体(20)作偶件配合，针阀(16)的两个滑动面能够分别在针阀体(20)中孔与针阀导套(15)中孔中作轴向滑动；针阀复位弹簧(17)两端分别压住针阀导套(15)与针阀(16)，使针阀导套 (15)顶端压紧在量孔板(14)下平面，针阀(16)下端锥面可抵住针阀体(20)中孔锥面。调压垫片(18)调节压紧力；针阀体(20)底端圆柱面与喷嘴(22)沉孔过盈配合，由喷嘴锁紧螺帽(21)进一步固定，喷嘴(22)上具有喷孔用以喷射燃油。器体紧帽(19)将喷嘴构件连接于喷油器体(1)，并使针阀体(20)顶端面压紧于量孔板(14)底端。
以上结构中，循环油油道(101)、进油油道(102)经由喷油器体(1)、量孔板(14)通入针阀体(20)中孔。量孔板(14)、针阀导套(15)、针阀(16)包围形成压力控制室(104)，通过进油量孔(103)和出油量孔(105)与外界连通。燃油回油道(106)在喷油器体(1)上，与出油量孔(105)间由钢球(13)相隔开。混合油排油道(107)连通于由导向套筒(8)中部环槽和密封圈(10)围成的环腔。冷却油进油道(108)、冷却油回油道(109)连通于由电磁铁(3)、导向套筒(8)与密封圈(10)围成的油腔，并通过套筒(7)上的槽孔互相连通。
参见图5和图5a，导向套筒(8)中部外侧开有环槽(110)，槽中部有横向通孔直通导向套筒(8)中孔；环槽两边有密封圈槽。控制阀芯(9)底端直径大于导向段，导向段上开有三道环槽(111)且第二道环槽与导向套筒(8)中部横向通孔连通。控制阀芯(9)、导向套筒(8)和密封圈(10)将喷油器体(1)中孔分成三个腔室。
结合图3和图3a可见，量孔板(14)顶端中间开有沉槽。球阀座导向套(11)能够套入量孔板(14)沉槽内；球阀座导向套(11)中孔上半段开口大于下半段，下半段与球阀座(12)间隙配合，导向套(11)中孔下半段对球阀座(12)轴向运动具有一定导向能力；顶端开有十字铣槽，球阀座(12)导向面上均布有三个铣槽。通过球阀座(12)与球阀座导向套(11)上的铣槽，使钢球(13)上方腔室与燃油回油道(105)相连通。
参见图8所示，本实施例采用的喷嘴(22)包括喷嘴体(222)和与之相配合的顶杆(221)；喷嘴体(222)与针阀体通过喷嘴过盈装配面(223)过盈安装，顶杆刚性连接在应用该喷嘴的喷油器的针阀头部或与针阀头部加工为一体。该喷油嘴的长度大于19mm，喷嘴体(222)与顶杆(221)皆布置于针阀偶件密封座面下方。
喷嘴体(222)中部两个直径较小面和与顶杆(221)间径向配合，形成两个紧密配合面，分别是喷嘴上部紧配面(225)和喷嘴下部紧配面 (227)。紧密配合面上顶杆(221)与喷嘴体(222)间隙很小，对顶杆有导向作用，同时有较好的密封能力。喷嘴上部紧配面(225)和喷嘴下部紧配面(226)将喷嘴体(222)与顶杆(221)间的油腔分为喷嘴上腔(224)、喷嘴中腔(226)和喷嘴下腔(228)三个部分，顶杆(221)上具有中心纵向孔(2210)与横向孔(2211)，将喷嘴上腔(224)与喷嘴下腔(228)连通。喷孔(229)则全部布置在喷嘴中腔(226)中。
该喷嘴的工作原理如下：
初始状态，针阀上的锥面与针阀体上的座面形成密封作用，待喷射的高压燃油积聚于密封座面上方。
喷射状态，针阀受到喷油器控制端提供的机械力或液压力而抬起，密封座面打开，同时针阀带动顶杆(221)，喷嘴体(222)与顶杆(221)间的下部紧配面(227)错开，使喷嘴下腔(228)与喷嘴中腔(226)连通。此时，密封座面上方的高压燃油经由密封座面、喷嘴上腔(224)、横向孔(2211)、纵向孔(2210)和喷嘴下腔(228)流入喷嘴中腔(226)，最终从布置于喷嘴中腔(226)中的喷孔(229)喷入气缸内部，参与燃烧。
停喷状态，喷油器控制端不提供力，针阀受到弹簧力或其他种类的复位力作用下落，重新压紧在密封座面，高压燃油被封于密封座面之上。此时喷嘴体(222)与顶杆(221)的下部紧配面(227)重新互相贴合，使喷嘴下腔(228)与喷嘴中腔(226)断开。喷嘴上部紧配面(225)和喷嘴下部紧配面(227)分别将、喷嘴上腔(224)和喷嘴下腔(228)与喷嘴中腔(226)隔开，位于喷嘴上腔(224)和喷嘴下腔(228)的残余剰油无法流向喷孔(229)，喷油停止。此时，气缸内燃烧后的废气仅能通过喷孔(229)与喷嘴中腔(226)接触，不会腐蚀到针阀偶件的密封座面，同时由于喷嘴本身比较长，针阀偶件可布置在远离气缸且冷却情况相对较好的缸盖中，能够有效减少高温环境及劣质燃油对喷油器针阀密封座面的损伤。由于喷嘴直径小于针阀体直径，因此所需安装孔可以适当减小，节省进气缸壁测的安装空间，为气阀等其他需安装在气缸壁测设备的布置提供余裕。
对于该喷嘴，其喷嘴体采用耐腐耐热且热膨胀系数小的材料，这样可减少喷嘴体受热而产生的热变形，间接使喷嘴体与顶杆间的间隙宽度稳 定，确保工作平稳。
以上结构电控共轨式重油喷油器的工作原理如下：
当电磁铁(3)没有通电，重油燃油通过进油接口(24)、进油油道(103)流入针阀体(20)中孔，再经进油量孔(103)流入压力控制室(104)，此时，控制阀芯(9)压紧球阀座(12)，使钢球(13)抵住出油量孔(105)。压力控制室(104)内的燃油压力与针阀体(20)中孔内压力相等。针阀(16)两端受到燃油压力以及针阀复位弹簧(17)传递的弹簧力，针阀(16)合力方向向下，维持落座状态，针阀(16)下端锥面可抵住针阀体(20)喷油端。
当电磁铁(3)通电后产生电磁力，衔铁(6)受到吸引力作用，当电磁力大于控制阀复位弹簧(4)的弹簧力，受合力影响控制阀芯(9)随同衔铁(6)向上运动至其底端大径处与导向套筒(8)底端接触。钢球(13)脱离原位，此时出油量孔(105)开启，压力控制室(104)内的高压油经出油量孔(105)上流，通过球阀座(12)导向面上均布的三个铣槽、球阀座导向套(11)中孔上半段开口及顶端通槽，最终从燃油回油道(106)、回油接口(28)流出喷油器外。此时压力控制室(104)内液压力逐渐降低，针阀(16)两侧液压力差增大，针阀(16)向上运动并打开与针阀体(20)间的密封，高压燃油从喷嘴(22)喷出，喷油过程开始。
当电磁铁(3)断电，控制阀复位弹簧(4)再次使控制阀芯(9)下落，钢球重新抵住出油量孔(105)，进油量孔(103)向压力控制室(104)补油。液压力增大。针阀(16)在液压力和针阀复位弹簧(17)的共同作用下向下运动，针阀(16)下端锥面再次抵住针阀体(20)喷油口，喷油过程结束。
喷油器高压油部分连通循环油油道(101)与循环油接口(25)，为安装外置式循环油阀提供油路。循环油阀的作用是，当喷油器正常工作时，循环油阀关闭，不影响喷油器正常工作；当燃油系统准备停机时，系统换用一定低压的较干净燃油流入喷油器内，此时循环油阀因低压而开启，燃油能够在喷油器中以一定速度流动，清洗残余重油，防止杂质多的残余重油冷却后使配合件粘滞、细孔堵塞。
冷却油进油道(108)、冷却油回油道(109)连通于由电磁铁(3)、导向套筒(8)和密封圈(10)围成的油腔，并通过套筒(7)上的槽孔互相连通。通过冷却油流动强制冷却带走热量，避免重油带来的高温对电子元件的热损伤。
控制阀芯(9)、导向套筒(8)和密封圈(10)将喷油器体(1)中孔分成三个腔室。上部冷却油腔，下部重油回油腔，中间通过密封圈(10)和各件平面压紧作静密封，控制阀芯(9)导向段上开有三道环槽(111)以加强与导向套筒(8)间的动密封。为防止长期使用后产生的轻微渗漏致使冷却油路被污染，控制阀芯(9)导向段上第二道环槽与导向套筒(8)中部横向通孔连通，重油与冷却油分别从第一、三两道环槽渗漏进第二道环槽后，通过导向套筒(8)中部环槽(110)和流入混合油排油道(107)，最终从混合油接口(29)引出，使控制阀芯(9)导向段第二环槽处液压力进一步减小，上方第三环槽中的冷却油压力与第二环槽处较低的混合油液压力形成方向向下的压力差，防止重油受导向面挤压向上渗漏。通过静密封、动密封、引流的方式，使冷却油路与燃油油路相隔离。该技术方案能够有效避免重油对冷却油的污染，进一步避免对电磁元件的腐蚀。
电液控制构件采用球阀为控制阀，球阀有较好的自找正性。同时导向套对球阀座轴向运动具有一定导向能力，防止因喷油器安装角度倾斜而导致钢球(13)侧向偏移，进一步提高工作稳定性。同时，球阀座导向套与球阀座作为单件可直接从量孔板上取下，方便因喷油器控制阀升程调整需要而进行配磨和损坏后的更换。

Claims (8)

  1. 一种电控共轨式重油喷油器，包括：喷油器体(1)、电液控制构件和喷嘴构件；其特征在于：所述喷油器体(1)顶端中间布置有电子接口(23)、顶端成周向布置有进油接口(24)、循环油接口(25)、冷却进油接口(26)、冷却出油接口(27)、回油接口(28)和混合油接口(29)，分别与电磁铁(3)的电线端、进油油道(102)、循环油油道(101)、冷却油进油道(107)、冷却油回油道(108)、燃油回油道(105)、混合油排油道(106)相连接；所述电液控制构件包括电磁铁(3)、控制阀复位弹簧(4)、衔铁(6)、套筒(7)、导向套筒(8)、控制阀芯(9)、球阀座导向套(11)、球阀座(12)、钢球(13)和量孔板(14)；所述量孔板(14)设置在喷油器体(1)与喷嘴构件之间，其内部设置进油量孔(103)和出油量孔(105)；控制阀芯(9)与导向套筒(8)为偶件配合，导向套筒(8)中孔能够导向控制阀芯(9)作轴向滑动；球阀座(12)布置于球阀座导向套(11)中；电磁铁(3)、套筒(7)、导向套筒(8)、球阀座导向套(11)从上到下依次装配于喷油器体(1)中孔，由压紧螺帽(2)压紧在量孔板(14)上；控制阀芯(9)、球阀座(12)、钢球(13)依次接触，由位于电磁铁(3)中孔的控制阀复位弹簧(4)压紧在量孔板(14)密封锥面上，堵住出油量孔(105)；导向套筒(8)通过外侧两个密封圈槽安装密封圈(10)进行密封；所述量孔板(14)顶端中间开有沉槽，球阀座导向套(11)套入所述沉槽内；球阀座导向套(11)中孔上半段开口大于下半段，下半段与球阀座(12)间隙配合，对球阀座(12)轴向运动具有一定导向能力；球阀座导向套(11)顶端开有十字铣槽，球阀座(12)导向面上均布有三个铣槽，通过球阀座(12)与球阀座导向套(11)上的铣槽，使钢球(13)上方腔室与燃油回油道(105)相连通；所述循环油油道(101)、进油油道(102)经由喷油器体(1)、量孔板(14)通入喷嘴构件。
  2. 如权利要求1所述的电控共轨式重油喷油器，其特征在于：所述喷嘴构件包括针阀导套(15)、针阀(16)、针阀复位弹簧(17)、调压垫片(18)、器体紧帽(19)、针阀体(20)和喷嘴(22)；所述针阀导套(15)、针阀(16)均与针阀体(20)作偶件配合，针阀(16)的上下两个滑动面分别能够在针阀体(20)中孔与针阀导套(15)中孔中作轴向滑动；针阀复位弹簧(17)两端分别压住 针阀导套(15)与针阀(16)，使针阀导套(15)顶端压紧在量孔板(14)下平面，针阀(16)下端锥面抵住针阀体(20)中孔锥面；针阀体(20)底端圆柱面与喷嘴(22)沉孔过盈配合，喷嘴(22)上具有喷孔用以喷射燃油；器体紧帽(19)将喷嘴构件连接于喷油器体(1)，并使针阀体(20)顶端面压紧于量孔板(14)底端；所述循环油油道(101)、进油油道(102)经由喷油器体(1)、量孔板(14)通入针阀体(20)中孔。
  3. 如权利要求2所述的电控共轨式重油喷油器，其特征在于：所述喷嘴(22)包括喷嘴体(222)和与之相配合的顶杆(221)；所述喷嘴体过盈安装于所述针阀体上，顶杆刚性连接在针阀头部或与针阀头部加工为一体；所述喷嘴体和与之相配合的顶杆间存在上下两个紧密配合面，将喷嘴体与顶杆间的油腔分为喷嘴上腔、喷嘴中腔和喷嘴下腔三个部分，顶杆上具有中心纵向孔与横向孔，将喷嘴上腔与喷嘴下腔连通，喷嘴体上的喷孔位于喷嘴中腔宽度范围内；当喷油器处于喷射状态时，喷嘴体与顶杆的下部紧配面错开，使喷嘴下腔与喷嘴中腔连通，当喷油器处于停喷状态时，喷嘴体与顶杆的下部紧配面互相贴合，使喷嘴下腔与喷嘴中腔断开。
  4. 根据权利要求2或3所述的低速柴油机用燃油喷嘴，其特征在于：所述喷嘴的长度大于等于19mm。
  5. 根据权利要求3所述的低速柴油机用燃油喷嘴，其特征在于：在针阀体与喷嘴体结合的部位外套装有喷嘴锁紧螺帽(21)，喷嘴锁紧螺帽(21)上端与针阀体螺纹连接，紧帽内壁紧套住针阀体与喷嘴体，紧帽下端锥角和厚度则与喷油器需要的安装座面锥角和喷嘴伸入气缸长度相配合设计。
  6. 如权利要求1、2或3所述的电控共轨式重油喷油器，其特征在于：所述量孔板(14)、针阀导套(15)、针阀(16)包围形成压力控制室(104)，通过进油量孔(103)和出油量孔(105)与外界连通；燃油回油道(106)在喷油器体(1)上，与出油量孔(105)间由钢球(13)相隔开；混合油排油道(107)连通于由导向套筒(8)中部外侧的环槽(110)和密封圈(10)围成的环腔；冷却油进油道(108)、冷却油回油道(109)连通于由电磁铁(3)、导向套筒(8)与密封圈(10)围成的油腔，并通过套筒(7)上的槽孔互相连通。
  7. 如权利要求1、2或3所述的电控共轨式重油喷油器，其特征在于： 所述导向套筒(8)中部外侧开有环槽(110)，槽中部有横向通孔直通导向套筒(8)中孔；环槽两边有密封圈槽；控制阀芯(9)底端直径大于导向段，导向段上开有三道环槽(111)且第二道环槽与导向套筒(8)中部横向通孔连通；控制阀芯(9)、导向套筒(8)和密封圈(10)将喷油器体(1)中孔分成三个腔室。
  8. 如权利要求1、2或3所述的电控共轨式重油喷油器，其特征在于：所述衔铁(6)与控制阀芯(9)顶端螺纹用螺母(5)固定。
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