CN110645128A - Dual-fuel injector - Google Patents

Dual-fuel injector Download PDF

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Publication number
CN110645128A
CN110645128A CN201911080952.8A CN201911080952A CN110645128A CN 110645128 A CN110645128 A CN 110645128A CN 201911080952 A CN201911080952 A CN 201911080952A CN 110645128 A CN110645128 A CN 110645128A
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CN
China
Prior art keywords
cavity
natural gas
valve
diesel oil
diesel
Prior art date
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Granted
Application number
CN201911080952.8A
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Chinese (zh)
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CN110645128B (en
Inventor
肖民
单航
徐浩
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Jiangsu University of Science and Technology
Marine Equipment and Technology Institute Jiangsu University of Science and Technology
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Jiangsu University of Science and Technology
Marine Equipment and Technology Institute Jiangsu University of Science and Technology
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Priority to CN201911080952.8A priority Critical patent/CN110645128B/en
Publication of CN110645128A publication Critical patent/CN110645128A/en
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Publication of CN110645128B publication Critical patent/CN110645128B/en
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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
    • F02M43/00—Fuel-injection apparatus operating simultaneously on two or more fuels, or on a liquid fuel and another liquid, e.g. the other liquid being an anti-knock additive
    • F02M43/04—Injectors peculiar thereto
    • 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
    • F02M21/00—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form
    • F02M21/02—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels
    • F02M21/0203—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels characterised by the type of gaseous fuel
    • F02M21/0215—Mixtures of gaseous fuels; Natural gas; Biogas; Mine gas; Landfill gas
    • 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
    • F02M21/00—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form
    • F02M21/02—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels
    • F02M21/0218—Details on the gaseous fuel supply system, e.g. tanks, valves, pipes, pumps, rails, injectors or mixers
    • F02M21/023—Valves; Pressure or flow regulators in the fuel supply or return system
    • 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
    • F02M21/00—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form
    • F02M21/02—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels
    • F02M21/0218—Details on the gaseous fuel supply system, e.g. tanks, valves, pipes, pumps, rails, injectors or mixers
    • F02M21/023—Valves; Pressure or flow regulators in the fuel supply or return system
    • F02M21/0233—Details of actuators therefor
    • 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
    • F02M21/00—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form
    • F02M21/02—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels
    • F02M21/0218—Details on the gaseous fuel supply system, e.g. tanks, valves, pipes, pumps, rails, injectors or mixers
    • F02M21/0248—Injectors
    • 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
    • F02M21/00—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form
    • F02M21/02—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels
    • F02M21/0218—Details on the gaseous fuel supply system, e.g. tanks, valves, pipes, pumps, rails, injectors or mixers
    • F02M21/0248—Injectors
    • F02M21/0251—Details of actuators therefor
    • 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
    • F02M21/00—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form
    • F02M21/02—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels
    • F02M21/0218—Details on the gaseous fuel supply system, e.g. tanks, valves, pipes, pumps, rails, injectors or mixers
    • F02M21/0248—Injectors
    • F02M21/0257—Details of the valve closing elements, e.g. valve seats, stems or arrangement of flow passages
    • F02M21/026—Lift valves, i.e. stem operated valves
    • F02M21/0263—Inwardly opening single or multi nozzle valves, e.g. needle valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • 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
    • F02M61/1893—Details of valve member ends not covered by groups F02M61/1866 - F02M61/188
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/30—Use of alternative fuels, e.g. biofuels

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • General Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Analytical Chemistry (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

The invention relates to a dual fuel injector comprising an injector housing; the diesel injection assembly is arranged in the injector shell and comprises a diesel oil return cavity, a valve cavity, a first ball valve, a diesel oil duct, a diesel oil pressure cavity, a needle valve, a control piston and a needle valve return spring; and the natural gas injection assembly is arranged in the injector shell and comprises a natural gas supply cavity, a natural gas air passage, a natural gas pressure cavity, a second ball valve, a natural gas supply channel and a natural gas inlet. The invention has the advantages that: the ejector disclosed by the invention adopts the matching among the ejector shell, the diesel oil injection assembly and the natural gas injection assembly, only one needle valve is required to be matched with one control cavity, the independent control of the injection of the diesel oil and the natural gas is realized, the structure is simplified, the number of air passages and oil passages is reduced, the structure is simpler, and the corresponding manufacturing is more convenient.

Description

Dual-fuel injector
Technical Field
The present invention relates to an injector, and more particularly to a dual fuel injector.
Background
The excessive development of petroleum resources such as diesel oil and gasoline leads to increasingly outstanding fuel contradiction, and the continuous increase of the automobile holding amount leads to increasingly serious automobile exhaust emission pollution. With the stricter international regulations and the increased environmental awareness of people, the development and utilization of clean alternative fuels are imperative. The natural gas is used as a clean energy with high efficiency and low cost, and has huge reserves, and particularly, the natural gas is bound to become a main alternative energy in the future due to the breakthrough of the shale gas exploitation technology. Meanwhile, natural gas is used as clean energy, the main component of the natural gas is methane, and the natural gas has higher heat value compared with diesel oil. However, researches show that the temperature of methane is at least 1200K when the methane is required to be spontaneously combusted within 2ms, and the temperature which can be achieved by a traditional diesel engine is only 850K to 950K, so that researchers propose a strategy for igniting natural gas by using diesel oil in an engine cylinder, and the strategy well solves the problem that the natural gas which is used as fuel only cannot be spontaneously combusted in the engine; due to space constraints in the engine cylinder head, it is desirable to use one fuel injector per cylinder to inject both fuels. This requires that the fuel injector be particularly adapted to keep the two fuels separate within the injector and to deliver each fuel independently at the appropriate time.
The engine adopting dual-fuel combustion has great advantages in aspects of dynamic property, economy, emission property and the like compared with a single-fuel engine. However, although gasoline and diesel oil injectors can be directly used for injecting high-pressure gas fuel, natural gas injection cannot form liquid film lubrication like liquid fuel due to the difference of viscosity and density properties of gas-liquid fuel, so that the lubrication effect of the natural gas injector is very poor, the impact abrasion between a needle valve and a nozzle valve body is increased, the injector is easily damaged, and the durability of the whole natural gas engine is affected. To solve this problem, the prior art has proposed ZL102105673A from western port company to provide a fuel injection valve for co-injecting a liquid fuel and a gaseous fuel into the combustion chamber of an internal combustion engine, which injects the liquid fuel and the gaseous fuel simultaneously into the cylinder after they are mixed in the same chamber inside the injector. The gas-liquid two phases can relieve the lubrication problem, but the gas-liquid two phases can bring the difficulty of fuel proportioning and mixing, and the mixed combustion in the cylinder is difficult to control.
Patent CN201780057473 discloses a dual fuel injector, which for the purpose of dual fuel asynchronous injection is arranged with two control valves, two control chambers and two needle valves, the first valve member is a common needle valve, the second valve member is designed as a hollow needle, and the first valve member is coaxially nested inside the second valve member. In the initial state, the two control chambers are filled with the first fuel, wherein the first solenoid valve controls the opening and closing of the oil return passage to realize the change of the pressure of the first fuel in the first control chamber, so as to control the opening or closing of the first valve member, and thus, the first fuel is injected from the first group of injection holes; the second solenoid valve uses the same principle to achieve the purpose of second fuel injection, and the two are independent.
Patent CN201811109506 discloses a novel dual fuel injector, which also uses a coaxial nested structure of dual needle valves, and is arranged with two control cavities and two control valves, different from the above patent, in the initial state of the invention, the air valve control cavity is filled with natural gas, and the needle valve control cavity is filled with diesel. The natural gas electromagnetic valve controls the opening and closing of natural gas, the natural gas electromagnet controls the opening and closing of the first ball valve so as to control the opening and closing of the natural gas oil return channel, thereby controlling the pressure of the gas valve control cavity and the up-and-down motion of the gas valve, and finally controlling the natural gas nozzle to realize the opening and the closing of gas injection; the diesel electromagnetic valve achieves the purpose of natural gas injection by using the same principle.
Although the fuel in the control cavity is different in the initial state in the above two patents, the two control cavities and the double-needle valve structure are adopted to realize the independent control of the injection of the diesel oil and the natural gas, and no matter whether the fuel in the control cavity is the same in the initial state or not, due to the existence of the double control cavities, the structure of the double-control cavity is necessarily more complex than that of a single control cavity, more air passages and oil passages exist, and great difficulty is brought to the manufacture.
Disclosure of Invention
The invention aims to provide a dual-fuel injector which is simple in structure and convenient to manufacture.
In order to solve the technical problems, the technical scheme of the invention is as follows: the double-fuel injector is characterized in that: comprises that
The ejector shell is in an inverted L shape, and natural gas spray holes and diesel spray holes which are distributed in a splayed shape are formed in the bottom end of the ejector shell;
the diesel injection assembly is arranged in the injector shell and comprises a diesel oil return cavity positioned at the upper part of the injector shell and a vertically arranged valve cavity positioned below the diesel oil return cavity, and the diesel oil return cavity is communicated with the valve cavity through a first oil outlet throttling hole;
the bottom end of the diesel oil return cavity is provided with a first conical groove communicated with a first oil outlet throttling hole, a first ball valve is mounted in the first conical groove, the first ball valve is driven by a first control mechanism to move up and down so as to open and close the first oil outlet throttling hole, and a diesel oil return hole extending out of the shell of the injector is formed in the side end of the diesel oil return cavity;
the diesel oil return cavity is arranged at the side of the diesel oil return cavity in the ejector shell, the top end of the diesel oil duct is provided with a diesel oil return hole extending out of the ejector shell, the bottom end of the diesel oil duct is communicated with a diesel oil pressure cavity, so that the diesel oil duct is distributed in an L shape, and the diesel oil pressure cavity is arranged below the valve cavity and is communicated with the valve cavity;
a needle valve is installed in the valve cavity, the top end of the needle valve is connected with a control piston, a cavity in the valve cavity, which is located between the control piston and the first oil outlet throttling hole, is a control cavity, a branch oil duct communicated with the control cavity is also arranged on the diesel oil duct, and a needle valve return spring is sleeved on the needle valve;
the natural gas injection assembly is arranged in the injector shell and comprises a natural gas supply cavity which is positioned at the upper part of the injector shell and is horizontally distributed with the diesel oil return cavity in parallel and a natural gas air passage which is positioned below the natural gas supply cavity, the top end of the natural gas air passage is communicated with the natural gas supply cavity through a second oil outlet throttling hole, and the bottom end of the natural gas air passage is connected with a natural gas pressure cavity, so that the natural gas air passage is Z-shaped, and the natural gas pressure cavity is positioned below the diesel pressure cavity and is communicated with the diesel pressure cavity;
the bottom of natural gas air feed chamber has a second taper groove that is linked together with second oil outlet orifice, installs the second ball valve in second taper groove, thereby the second ball valve carries out the opening and close of second oil outlet orifice by the drive of second control mechanism, the side of natural gas air feed chamber is connected with a natural gas air feed channel who communicates with it, has a natural gas import that stretches out outside the sprayer casing at natural gas air feed channel's opposite side.
Further, the first control mechanism is: a first electromagnetic valve armature is installed in the diesel oil return cavity, the bottom end of the first electromagnetic valve armature is connected with a first ball valve, a first return spring is sleeved on the outer side of the top end of the first electromagnetic valve armature, the first electromagnetic valve armature is controlled by a first electromagnetic valve to move up and down, and a first coil connector matched with the first electromagnetic valve is further installed on the ejector shell.
Furthermore, the needle valve is in a step shape and sequentially comprises a first step section, a second step section, a third step section, a fourth step section and a fifth step section with the caliber gradually reduced from top to bottom, wherein the first step section is positioned in the valve cavity, the third step section is arranged in the diesel pressure cavity, the third step section is in a circular truncated cone shape, the size of the upper end surface of the third step section is larger than that of the lower end surface, the upper part of the fifth step section is arranged in the natural gas pressure cavity, a cavity which is movably arranged at the middle lower part of the fifth step section is also arranged below the natural gas pressure cavity in the ejector shell, the natural gas spray hole and the diesel spray hole are communicated with the cavity, the bottom end of the cavity is in a cone shape, the bottom end of the fifth step section is also in a cone shape which is jointed with the bottom end of the cavity, and a needle valve diesel oil duct is also arranged in the fourth step section and the fifth step section, the needle valve diesel oil duct is of a T-shaped structure formed by a horizontal section and a vertical section, two sides of the horizontal section of the needle valve diesel oil duct extend out from two sides of the fourth step section in the horizontal direction respectively, and the vertical section of the needle valve diesel oil duct extends out from the bottom end of the fifth step section.
Further, the second control mechanism is: and a second solenoid valve armature is arranged in the natural gas supply cavity, the bottom end of the second solenoid valve armature is connected with a second ball valve, a second return spring is sleeved outside the top end of the second solenoid valve armature, the second solenoid valve armature is controlled by a second solenoid valve to move up and down, and a second coil connector matched with the second solenoid valve is further arranged on the ejector shell.
The invention has the advantages that: the ejector disclosed by the invention adopts the matching among the ejector shell, the diesel oil injection assembly and the natural gas injection assembly, only needs the matching between the single needle valve and one control cavity, simultaneously realizes the independent control of the injection of the diesel oil and the natural gas, simplifies the structure, reduces the number of air passages and oil passages, has simpler structure and is relatively convenient to manufacture correspondingly.
The invention overcomes the problem that the common gas injection ejector is lack of lubrication, and when the needle valve moves, the diesel oil in the diesel oil pressure cavity forms oil film lubrication on the needle valve, thereby reducing the injection abrasion and prolonging the service life of the ejector.
The injector provided by the invention is controlled by the double electromagnetic valves, the proportion of natural gas/diesel oil can be adjusted according to different working conditions, the power performance of the engine is improved, and the emission performance of the engine is optimized.
Drawings
The present invention will be described in further detail with reference to the accompanying drawings and specific embodiments.
FIG. 1 is a schematic diagram of a dual fuel injector of the present invention.
Fig. 2 is an enlarged schematic view of a portion a of fig. 1.
FIG. 3 is a schematic view of a needle valve of the present invention.
Detailed Description
The following examples are presented to enable one of ordinary skill in the art to more fully understand the present invention and are not intended to limit the scope of the embodiments described herein.
A dual fuel injector, as shown in fig. 1-3, includes
And the injector shell 30 is in an inverted L shape, and the bottom end of the injector shell 30 is provided with a natural gas spray hole 28 and a diesel spray hole 29 which are distributed in a splayed shape.
The diesel injection assembly is arranged in the injector housing 30 and comprises a diesel oil return cavity 36 located at the upper part of the injector housing 30 and a vertically arranged valve cavity located below the diesel oil return cavity 36, and the diesel oil return cavity 36 is communicated with the valve cavity through a first oil outlet throttling hole 9.
The bottom end of the diesel oil return cavity 36 is provided with a first conical groove communicated with the first oil outlet throttling hole 9, a first ball valve 8 is installed in the first conical groove, the first ball valve 8 is driven by a first control mechanism to move up and down so as to open and close the first oil outlet throttling hole 9, and the side end of the diesel oil return cavity 36 is provided with a diesel oil return hole 6 extending out of the injector shell 30.
The first control mechanism is: a first solenoid valve armature 4 is installed in the diesel oil return cavity 36, the first solenoid valve armature 4 is in an inverted T shape, the bottom end of the first solenoid valve armature 4 is fixedly connected with the first ball valve 8, a first return spring 3 is sleeved on the outer side of the top end of the first solenoid valve armature 4, the first solenoid valve armature 4 is controlled by a first solenoid valve 2 installed in the injector housing 30 to move up and down, and a first coil connector 1 matched with the first solenoid valve 2 is further installed on the injector housing 30.
The diesel oil return cavity 36 is arranged at one side of the injector housing 30, the diesel oil duct 7 is arranged at the top end of the diesel oil duct 7, a diesel oil return hole extending out of the injector housing 30 is formed in the top end of the diesel oil duct 7, the bottom end of the diesel oil duct 7 is communicated with a diesel oil pressure cavity 14, so that the diesel oil duct 7 is distributed in an L shape, the diesel oil pressure cavity 14 is arranged below the valve cavity and communicated with the valve cavity, and the interface of the diesel oil pressure cavity 14 is in a waist shape.
A needle valve 24 is arranged in the valve cavity, the top end of the needle valve 24 is connected with a control piston 11, a cavity between the control piston 11 and a first oil outlet throttling hole 9 in the valve cavity is a control cavity 10, an oil distributing channel communicated with the control cavity 10 is also arranged on the diesel oil channel 7, a needle valve return spring 12 is further sleeved on the needle valve 24, and a needle valve base 25 matched with the needle valve 24 is further arranged in the valve cavity.
As shown in the schematic diagram of fig. 3, the needle valve 24 is stepped, and includes a first step 31, a second step 32, a third step 33, a fourth step 34, and a fifth step 35 with gradually decreasing diameters from top to bottom, the needle valve return spring 12 is sleeved on the outer side of the first step 31, wherein the first step 31 is located in the valve cavity, the third step 33 is located in the diesel pressure chamber 14, the third step 33 is in a circular truncated cone shape, the size of the upper end surface of the third step 33 is larger than that of the lower end surface, the upper position of the fifth step 35 is located in the natural gas pressure chamber 26, a cavity is further provided in the injector housing 30 below the natural gas pressure chamber 26 for accommodating the middle and lower position of the fifth step 35, and the natural gas nozzle 28 and the diesel nozzle 29 are both communicated with the cavity, the bottom end of the cavity is in a conical shape, and the bottom end of the fifth step 35 is also in a conical shape attached to the bottom end of the cavity, a needle valve diesel oil passage 27 is further arranged in the fourth stepped section 34 and the fifth stepped section 35, the needle valve diesel oil passage 27 is of a T-shaped structure formed by a horizontal section and a vertical section, two sides of the horizontal section of the needle valve diesel oil passage 27 extend out from two sides of the fourth stepped section 34 in the horizontal direction respectively, and the vertical section of the needle valve diesel oil passage 27 extends out from the bottom end of the fifth stepped section 35.
The natural gas injection assembly is arranged in the injector shell 30 and comprises a natural gas supply cavity 37 which is positioned at the upper part of the injector shell 30 and horizontally distributed with the diesel oil return cavity 36 in parallel and a natural gas air passage 23 which is positioned below the natural gas supply cavity 37, the top end of the natural gas air passage 23 is communicated with the natural gas supply cavity 37 through a second oil outlet orifice 22, the bottom end of the natural gas air passage 23 is connected with a natural gas pressure cavity 26, so that the natural gas air passage 26 is Z-shaped, and the natural gas pressure cavity 26 is positioned below the diesel pressure cavity 14 and is communicated with the diesel pressure cavity 14.
The bottom end of the natural gas supply cavity 37 is provided with a second taper groove communicated with the second oil outlet throttling hole 22, a second ball valve 21 is installed in the second taper groove, the second ball valve 21 is driven by a second control mechanism to move up and down so as to open and close the second oil outlet throttling hole 22, the side end of the natural gas supply cavity 37 is connected with a natural gas supply channel communicated with the natural gas supply cavity, and the other side of the natural gas supply channel is provided with a natural gas inlet 20 extending out of the ejector shell 30.
The second control mechanism is: a second solenoid valve armature 19 is installed in the natural gas supply cavity 37, the second solenoid valve armature 19 is in an inverted T shape, the bottom end of the second solenoid valve armature 19 is connected with the second ball valve 21, a second return spring 18 is sleeved on the outer side of the top end of the second solenoid valve armature 19, the second solenoid valve armature 19 is controlled by the second solenoid valve 17 to move up and down, and a second coil connector 16 matched with the second solenoid valve 17 is further installed on the ejector shell 30.
The working principle is as follows: when the oil injector is actually used, the oil injector is fixed on an engine body, the high-pressure oil supply pipe is connected to the diesel oil inlet 5, the diesel oil return hole 6 is connected with the oil return pipe, the natural gas supply pipe is connected with the natural gas inlet 20, and the first coil connector 1 and the second coil connector 16 are connected with an electric connector of an engine control unit.
Pilot diesel injection phase
The closing state of the oil injector is as follows: when the oil injector is in a non-working state or the ECU does not send an injection instruction to the oil injector, the first electromagnetic valve 2 and the second electromagnetic valve 17 do not generate electromagnetic force, the first electromagnetic valve armature 4 and the second electromagnetic valve armature 19 are in a closed state under the action of the first return spring 3 and the second return spring 18, the first ball valve 8 and the second ball valve 21 are in a closed state, the first oil outlet orifice 9 and the second oil outlet orifice 22 are cut off, at the moment, the pressure of diesel oil in the control cavity 10 is equal to the pressure of a high-pressure oil pipe, hydraulic force acting downwards on the control piston 11 is generated, the force acts on the needle valve 24, the second oil outlet orifice 22 is also in a closed state, natural gas does not exist in the natural gas pressure cavity 26, the pressure is normal pressure, meanwhile, fuel oil in the diesel oil pressure cavity 14 generates upward hydraulic force on the needle valve 24, under the combined action of the two hydraulic forces in, together with the force of the needle return spring 12, the needle 24 is subjected to a total downward force, which keeps the diesel injector closed.
The fuel injector diesel oil part opening process: when the first electromagnetic valve 2 of the oil injector is electrified and the second electromagnetic valve 17 of the oil injector is not electrified, under the action of the attraction force of the electromagnet, the pre-tightening acting force of the first return spring 3 is overcome, the armature 4 of the first electromagnetic valve is attracted, so that the first ball valve 8 is opened, the first oil outlet orifice 9 is opened, the control cavity 10 is communicated with the diesel oil return hole 6, the pressure of the control cavity 10 is reduced, the second oil outlet orifice 22 is still closed, the pressure of the diesel oil pressure cavity 14 is unchanged at the moment, the oil injector needle valve 24 is lifted under the action of the resultant force applied to the oil injector needle valve 24, the diesel oil duct 7 in the needle valve 24 is communicated with the diesel oil pressure cavity 14, and the diesel oil is sprayed out through the diesel oil.
The diesel part of the fuel injector is completely opened: the first ball valve 8 is fully opened, high-pressure fuel in the control cavity 10 flows back to a fuel tank through the first fuel outlet orifice 9, the pressure of the high-pressure fuel in the control cavity 10 is rapidly reduced, meanwhile, the hydraulic pressure acting on the control piston 11 is reduced, the sum of the acting force and the acting force of the needle valve return spring 12 is smaller than the hydraulic pressure of the high-pressure fuel in the diesel oil cavity 14 acting on the needle valve 24, the needle valve 24 is lifted, if the duration of fuel injection is long, the needle valve 24 finally rises to a mechanical stop point, then the needle valve 24 is kept at a maximum lift position, the high-pressure fuel is injected into a cylinder through the diesel oil spray holes 29, and meanwhile, a small.
Closing process of diesel oil part of oil injector: when the first electromagnetic valve 2 is powered off and the second electromagnetic valve 17 is not powered on, the electromagnetic force of the first electromagnetic valve 2 of the fuel injector starts to reduce, when the electromagnetic suction force and the hydraulic pressure at the bottom of the first ball valve 8 are not enough to counteract the elastic force of the first return spring 3, the first ball valve 8 falls back to the ball valve seat, the first fuel outlet orifice 9 is closed, the pressure of the high-pressure fuel rises along with the continuous flow of the high-pressure fuel into the control cavity 10, the hydraulic pressure acting on the control piston 11 also increases along with the pressure, and when the sum of the pressure and the acting force of the needle valve return spring 12 is larger than the hydraulic pressure of the high-pressure fuel acting on the needle valve 24 in the diesel oil cavity 14, the needle valve 24 starts to fall back until the needle valve 24 falls back to the needle.
Natural gas injection stage
The natural gas part opening process of the oil sprayer: after the diesel oil injection stage is finished, the needle valve 24 is completely seated, at the moment, the first electromagnetic valve 2 of the oil injector is not electrified, the second electromagnetic valve 17 is electrified, under the action of the attraction force of the electromagnet, the pretension acting force of the second return spring 18 is overcome, the armature 19 of the second electromagnetic valve is attracted, the second ball valve 21 is opened, the second oil outlet orifice 22 is opened, natural gas enters the natural gas air channel 23 through the second oil outlet orifice 22 and reaches the natural gas pressure cavity 26, at the moment, the first oil outlet orifice 9 is still closed, diesel oil is filled in the control cavity 10 and the diesel oil pressure cavity 14, because the natural gas pressure cavity 26 generates an additional upward hydraulic pressure to the needle valve 24, the oil injector needle valve 24 is lifted under the resultant force action of the natural gas, but in the ascending process of the control piston 11, because the first ball valve 8 at the upper part of the control cavity is not opened, therefore, the needle valve 24 is lifted to a limited extent and the diesel oil duct 13 in the needle valve 24 cannot reach the height of the diesel oil pressure chamber 14, so that only the natural gas is sprayed out from the natural gas spraying holes 28 at this time, the diesel oil cannot be sprayed out, and the natural gas spraying process is completed at this time.
Partial closing process of natural gas of the oil sprayer: when the first electromagnetic valve 2 is not electrified and the second electromagnetic valve 17 is powered off, the electromagnetic force of the second electromagnetic valve 17 of the injector starts to decrease, when the electromagnetic attraction force and the hydraulic pressure at the bottom of the second ball valve 21 are not enough to counteract the elastic force of the second return spring 18, the second ball valve 21 falls back to the ball valve seat, so that the second oil outlet orifice 22 is closed, natural gas does not enter the natural gas pressure chamber 26 any more, natural gas in the natural gas pressure chamber 26 is sprayed out in the descending process of the needle valve 24, the pressure of the natural gas pressure chamber 26 gradually decreases, high-pressure diesel oil still exists in the control chamber 10 and the diesel oil pressure chamber 14, when the pressure of the natural gas pressure chamber 26 decreases to a certain degree, and the sum of the acting forces of the control chamber 10 and the needle valve return spring 12 is greater than the sum of the acting forces of the diesel oil pressure chamber 14 and the natural gas pressure chamber 26, the natural gas injection is ended.
It will be understood by those skilled in the art that the present invention is not limited to the embodiments described above, which are described in the specification and illustrated only to illustrate the principle of the present invention, but that various changes and modifications may be made therein without departing from the spirit and scope of the present invention, which fall within the scope of the invention as claimed. The scope of the invention is defined by the appended claims and equivalents thereof.

Claims (4)

1. A dual fuel injector, characterized by: comprises that
The ejector shell is in an inverted L shape, and natural gas spray holes and diesel spray holes which are distributed in a splayed shape are formed in the bottom end of the ejector shell;
the diesel injection assembly is arranged in the injector shell and comprises a diesel oil return cavity positioned at the upper part of the injector shell and a vertically arranged valve cavity positioned below the diesel oil return cavity, and the diesel oil return cavity is communicated with the valve cavity through a first oil outlet throttling hole;
the bottom end of the diesel oil return cavity is provided with a first conical groove communicated with a first oil outlet throttling hole, a first ball valve is mounted in the first conical groove, the first ball valve is driven by a first control mechanism to move up and down so as to open and close the first oil outlet throttling hole, and a diesel oil return hole extending out of the shell of the injector is formed in the side end of the diesel oil return cavity;
the diesel oil return cavity is arranged at the side of the diesel oil return cavity in the ejector shell, the top end of the diesel oil duct is provided with a diesel oil return hole extending out of the ejector shell, the bottom end of the diesel oil duct is communicated with a diesel oil pressure cavity, so that the diesel oil duct is distributed in an L shape, and the diesel oil pressure cavity is arranged below the valve cavity and is communicated with the valve cavity;
a needle valve is installed in the valve cavity, the top end of the needle valve is connected with a control piston, a cavity in the valve cavity, which is located between the control piston and the first oil outlet throttling hole, is a control cavity, a branch oil duct communicated with the control cavity is also arranged on the diesel oil duct, and a needle valve return spring is sleeved on the needle valve;
the natural gas injection assembly is arranged in the injector shell and comprises a natural gas supply cavity which is positioned at the upper part of the injector shell and is horizontally distributed with the diesel oil return cavity in parallel and a natural gas air passage which is positioned below the natural gas supply cavity, the top end of the natural gas air passage is communicated with the natural gas supply cavity through a second oil outlet throttling hole, and the bottom end of the natural gas air passage is connected with a natural gas pressure cavity, so that the natural gas air passage is Z-shaped, and the natural gas pressure cavity is positioned below the diesel pressure cavity and is communicated with the diesel pressure cavity;
the bottom of natural gas air feed chamber has a second taper groove that is linked together with second oil outlet orifice, installs the second ball valve in second taper groove, thereby the second ball valve carries out the opening and close of second oil outlet orifice by the drive of second control mechanism, the side of natural gas air feed chamber is connected with a natural gas air feed channel who communicates with it, has a natural gas import that stretches out outside the sprayer casing at natural gas air feed channel's opposite side.
2. The dual fuel injector of claim 1, wherein: the first control mechanism is: a first electromagnetic valve armature is installed in the diesel oil return cavity, the bottom end of the first electromagnetic valve armature is connected with a first ball valve, a first return spring is sleeved on the outer side of the top end of the first electromagnetic valve armature, the first electromagnetic valve armature is controlled by a first electromagnetic valve to move up and down, and a first coil connector matched with the first electromagnetic valve is further installed on the ejector shell.
3. The dual fuel injector of claim 1, wherein: the needle valve is in a step shape and sequentially comprises a first step section, a second step section, a third step section, a fourth step section and a fifth step section from top to bottom, wherein the caliber of the first step section is gradually reduced, the third step section is arranged in a diesel pressure cavity, the third step section is in a circular truncated cone shape, the size of the upper end surface of the third step section is larger than that of the lower end surface, the upper part of the fifth step section is arranged in the natural gas pressure cavity, a cavity which is movably arranged at the middle lower part of the fifth step section is also arranged below the natural gas pressure cavity in the ejector shell, simultaneously, a natural gas spray hole and a diesel spray hole are communicated with the cavity, the bottom end of the cavity is in a cone shape, the bottom end of the fifth step section is also in a shape which is attached to the bottom end of the cone-shaped cavity, and a diesel needle valve oil duct is also arranged in the fourth step section and the fifth step section, the needle valve diesel oil duct is of a T-shaped structure formed by a horizontal section and a vertical section, two sides of the horizontal section of the needle valve diesel oil duct extend out from two sides of the fourth step section in the horizontal direction respectively, and the vertical section of the needle valve diesel oil duct extends out from the bottom end of the fifth step section.
4. The dual fuel injector of claim 1, wherein: the second control mechanism is: and a second solenoid valve armature is arranged in the natural gas supply cavity, the bottom end of the second solenoid valve armature is connected with a second ball valve, a second return spring is sleeved outside the top end of the second solenoid valve armature, the second solenoid valve armature is controlled by a second solenoid valve to move up and down, and a second coil connector matched with the second solenoid valve is further arranged on the ejector shell.
CN201911080952.8A 2019-11-07 2019-11-07 Dual fuel injector Active CN110645128B (en)

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112594102A (en) * 2020-12-15 2021-04-02 江苏大学 Engine oil sprayer for realizing dual-fuel independent oil spraying
CN113294253A (en) * 2021-04-28 2021-08-24 江苏大学 Natural gas and diesel dual-fuel coaxial injection fuel injector and control method thereof
US11713740B1 (en) * 2022-02-24 2023-08-01 Harbin Engineering University High-pressure common rail fuel injector capable of achieving highly stable injection based on throttling damping accommodating effect

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Publication number Priority date Publication date Assignee Title
CN109026474A (en) * 2018-09-21 2018-12-18 英嘉动力科技无锡有限公司 A kind of novel double fuel in-cylinder direct-jet injector
CN109058013A (en) * 2018-09-21 2018-12-21 英嘉动力科技无锡有限公司 A kind of natural gas diesel injector of new control model
CN109139315A (en) * 2018-09-21 2019-01-04 英嘉动力科技无锡有限公司 A kind of novel dual fuel injector
CN210738714U (en) * 2019-11-07 2020-06-12 江苏科技大学 Dual-fuel injector

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109026474A (en) * 2018-09-21 2018-12-18 英嘉动力科技无锡有限公司 A kind of novel double fuel in-cylinder direct-jet injector
CN109058013A (en) * 2018-09-21 2018-12-21 英嘉动力科技无锡有限公司 A kind of natural gas diesel injector of new control model
CN109139315A (en) * 2018-09-21 2019-01-04 英嘉动力科技无锡有限公司 A kind of novel dual fuel injector
CN210738714U (en) * 2019-11-07 2020-06-12 江苏科技大学 Dual-fuel injector

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112594102A (en) * 2020-12-15 2021-04-02 江苏大学 Engine oil sprayer for realizing dual-fuel independent oil spraying
CN113294253A (en) * 2021-04-28 2021-08-24 江苏大学 Natural gas and diesel dual-fuel coaxial injection fuel injector and control method thereof
US11713740B1 (en) * 2022-02-24 2023-08-01 Harbin Engineering University High-pressure common rail fuel injector capable of achieving highly stable injection based on throttling damping accommodating effect

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