A new type of dual fuel injector

Abstract

The present invention belongs to the technical field of injectors, and specifically relates to a novel dual-fuel injector. The novel dual-fuel injector comprises an injector housing, a natural gas solenoid valve, a diesel solenoid valve and a valve body, wherein the injector housing is provided with a natural gas solenoid valve, a diesel solenoid valve and a valve body, an intermediate body is provided at the connection between the valve body and the injector housing, a needle valve and an air valve are provided in the valve body, and a diesel spray hole and a natural gas spray hole are provided on the valve body corresponding to the needle valve and the air valve, respectively. The beneficial effects are: the control flexibility is large, the independent control and independent injection of diesel and natural gas dual fuels can be realized, and the wide use of natural gas in medium and heavy-duty vehicles can be realized.

Description

Technical Field

[0001] The invention belongs to the technical field of injectors, and in particular relates to a novel dual-fuel injector. Background Art

[0002] Currently, the medium and heavy-duty vehicle engines, marine engines and medium and heavy-duty engineering machinery engines on the market mainly use diesel and a small number of natural gas as fuel. In order to meet the increasingly stringent emission regulations, current internal combustion engines mainly use high-pressure direct injection technology (high-pressure common rail system) with single diesel as fuel or intake manifold injection technology with natural gas as fuel.

[0003] Internal combustion engines that use diesel as the sole fuel adopt the latest high-pressure common rail injection technology, and their combustion efficiency is basically less than 39%. The tiny particles of diesel sprayed out cannot be completely burned, and part of them are discharged in the form of particles, resulting in a large number of tiny particles in the exhaust gas of the diesel engine. A certain amount of nitrogen oxides will also be emitted, causing great air pollution. With the release of the National VI emission standards, the emission difficulty of this internal combustion engine has gradually increased, and it has also brought about an increase in post-processing costs.

[0004] The few natural gas internal combustion engines currently use port injection and ignition through spark plugs. Their combustion efficiency is less than 36%, and their unburned CH4 is directly discharged, which will cause air pollution and make it difficult to meet the gradually increasing emission requirements.

[0005] With the adjustment of the national energy structure and the improvement of emission requirements, traditional internal combustion engines that use only gasoline or diesel as combustion media will gradually decrease. Natural gas is abundant in my country and around the world and will gradually begin to be used in the automotive market as an alternative fuel to diesel.

[0006] A direct injection technology that can realize dual-fuel injection can effectively improve combustion efficiency by using compression ignition. A small amount of diesel is first injected into the combustion chamber for compression ignition to increase the temperature in the combustion chamber, and then the natural gas injected subsequently is ignited to burn and do work. This can not only increase the combustion efficiency to 42% or more, but also reduce the emission of particulates and nitrogen oxides, making it a cleaner and more economical internal combustion engine injection system. However, although the existing dual-fuel injectors can realize the injection of two fuels, their response speed is insufficient and the control accuracy is limited. At the same time, due to the cumbersome structure, the product consistency is poor and the cost is high, which brings difficulties to the system calibration and large-scale promotion of dual-fuel internal combustion engines. Summary of the invention

[0007] In order to make up for the defects of the prior art, the present invention provides a novel dual-fuel injector.

[0008] The present invention is achieved through the following technical solutions:

[0009] A novel dual-fuel injector comprises an injector housing, a natural gas solenoid valve, a diesel solenoid valve and a valve body. The injector housing is connected and fastened with the natural gas solenoid valve, the diesel solenoid valve and the valve body. An intermediate body is provided at the connection between the valve body and the injector housing. A needle valve and an air valve are provided in the valve body. A diesel high-pressure oil inlet, a natural gas high-pressure air inlet and a diesel oil return hole are provided on the injector housing. The natural gas high-pressure air inlet is connected with the corresponding natural gas storage cavity and the air valve on the valve body through the internal air channel of the housing and the internal connecting air channel of the housing through the intermediate air channel and the nozzle air channel on the intermediate body, and is controlled by the natural gas solenoid valve. The diesel high-pressure oil inlet is connected with the high-pressure oil storage cavity and the needle valve through the high-pressure oil channel on the intermediate body, and is controlled by the diesel solenoid valve. A natural gas spray hole is provided at the head of the valve body, and a diesel spray hole is provided at the head of the air valve.

[0010] Furthermore, the diesel solenoid valve is connected to the first oil channel through the first connecting channel, the diesel solenoid valve controls the second ball guide to drive the second ball valve to control the opening and closing of the needle valve through the diesel armature, and the diesel high-pressure oil inlet is connected to the third high-pressure oil channel and the fourth high-pressure oil channel on the intermediate body through the second high-pressure oil channel, so that the high-pressure oil enters the needle valve control chamber through the fourth high-pressure oil channel and the needle valve oil inlet throttle hole, and then communicates with the fourth oil channel through the needle valve oil outlet throttle hole, and the fourth oil channel is connected to the first oil channel through the second oil channel, and finally the diesel solenoid valve controls the opening and closing of the diesel injection, and the flow of the needle valve oil inlet throttle hole and the needle valve oil outlet throttle hole of the needle valve control chamber affects the pressure change speed in the chamber. The diesel solenoid valve end is connected to the return oil channel through the diesel return oil channel.

[0011] Furthermore, the air valve is provided with a fourth high-pressure oil chamber, the needle valve is provided with a needle valve guide sleeve, the air valve is provided with an air valve sleeve, the fourth high-pressure oil chamber is connected with the high-pressure pressure storage chamber, the high-pressure pressure storage chamber is connected with the pressure storage ring belt on the needle valve through the oil hole, the pressure storage ring belt is connected with the high-pressure oil storage chamber through the oil passage, when the needle valve rises, the high-pressure oil storage chamber is connected with each diesel spray hole on the air valve, and injection is performed through each diesel spray hole.

[0012] Furthermore, the valve body and the intermediate body are respectively provided with a plurality of intermediate body air channels, one end of each intermediate body air channel is connected to the natural gas high-pressure air inlet through the internal air channel of the shell and the internal connecting air channel of the shell, and the other end is connected to the natural gas storage cavity through the natural gas channel. When the gas valve rises, the natural gas storage cavity is connected to the injection cavity, and a plurality of natural gas spray holes are formed on the valve body of the injection cavity.

[0013] Furthermore, the natural gas solenoid valve is connected with the third oil channel through the second connecting channel, the third oil channel is connected with the gas valve oil outlet throttle hole and the gas valve control chamber through the fifth oil channel, and the high-pressure joint is connected with the gas valve control chamber through the second high-pressure oil channel and the sixth oil channel via the gas valve oil inlet throttle hole, thereby finally realizing the control of the natural gas solenoid valve on the opening and closing of the natural gas injection, and the flow rate through the gas valve oil inlet throttle hole and the gas valve oil outlet throttle hole of the gas valve control chamber affects the pressure change speed in the chamber, and the natural gas solenoid valve end is connected with the oil return channel through the diesel oil return channel.

[0014] Furthermore, the inner side of the needle valve guide sleeve and the outer side of the needle valve are precisely ground and matched, and the sealing and throttling effects are achieved by controlling the matching gap. The needle valve control chamber is composed of the needle valve, the needle valve guide sleeve and the lower end surface of the injector housing after being matched.

[0015] Furthermore, the inner side of the air valve sleeve and the outer side of the air valve are precisely ground and matched, and a sealing and throttling effect is achieved by controlling the matching gap. The air valve control chamber is composed of the air valve and the air valve sleeve matched with the needle valve, the needle valve guide sleeve and the lower end surface of the injector housing.

[0016] The beneficial effects of the present invention are: great control flexibility, capable of realizing independent control and independent injection of diesel and natural gas dual fuels; fast response speed, high control accuracy, capable of realizing separate control of diesel and natural gas fuels; simple structure during implementation, increased product consistency and thus reduced costs, ultimately capable of improving the combustion efficiency of internal combustion engines, and realizing the widespread use of natural gas in medium and heavy-duty vehicles. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] The present invention will be further described below in conjunction with the accompanying drawings.

[0018] Attached Figure 1 It is a structural schematic diagram of the present invention;

[0019] Attached Figure 2 It is a partial schematic diagram of the valve body of the present invention;

[0020] Attached Figure 3 It is a schematic diagram of the structure of the natural gas solenoid valve and the diesel solenoid valve of the present invention;

[0021] Attached Figure 4 A partial diagram of the air passage distribution inside the ejector housing and the intermediate body of the present invention;

[0022] Attached Figure 5 It is a partial cross-sectional view of each oil passage in the needle valve guide sleeve area of ​​the present invention;

[0023] Attached Figure 6 It is a partial cross-sectional view of the natural gas passage and oil passage inside the injection location of the present invention;

[0024] Attached Figure 7 It is a partial cross-sectional view of the natural gas intake passage of the present invention.

[0025] In the figure, 1 is a natural gas solenoid valve, 2 is a natural gas armature, 3 is a first ball guide, 4 is a first ball valve, 5 is a second connecting channel, 6 is a diesel solenoid valve, 7 is a diesel armature, 8 is a second ball guide, 9 is a second ball valve, 10 is a first oil channel, 11 is a natural gas high-pressure air inlet, 12 is a diesel oil return channel, 13 is an injector housing, 14 is a second oil channel, 15 is a third oil channel, 16 is an oil return channel, 17 is a diesel high-pressure oil inlet, 18 is a second high-pressure oil channel, 19 is a third high-pressure oil channel, 20 is a fourth high-pressure oil channel, 21 is a fourth oil channel, 22 is a needle valve oil inlet throttle hole, 23 is a needle valve oil outlet throttle hole, 24 is a housing internal air channel, 25 is a housing Internally connected air passage, 26 nozzle air passage, 27 air valve control chamber, 28 oil passage, 29 fourth high-pressure oil chamber, 30 intermediate body, 31 valve body, 32 air valve, 33 needle valve, 34 air valve sleeve, 35 needle valve guide sleeve, 36 natural gas chamber, 37 injection chamber, 38 natural gas spray hole, 39 diesel spray hole, 40 intermediate body air passage, 41 air valve oil outlet throttle hole, 42 fifth oil passage, 43 sixth oil passage, 44 pressure storage ring belt, 45 first connecting passage, 46 high-pressure pressure storage chamber, 47 oil passage, 48 air valve oil inlet throttle hole, 49 natural gas passage, 50 needle valve control chamber, 51 high-pressure oil storage chamber. DETAILED DESCRIPTION

[0026] The novel dual-fuel injector 6 of the present invention is further described below in conjunction with an embodiment.

[0027] Attached Figure 1-7 This is a specific embodiment of the present invention. The invention is a new dual-fuel injector, including an injector housing 13, a natural gas solenoid valve 1, a diesel solenoid valve 6 and a valve body 31. The injector housing 13 is connected and fastened with the natural gas solenoid valve 1, the diesel solenoid valve 6 and the valve body 31. An intermediate body 30 is provided at the connection between the valve body 31 and the injector housing 13. A needle valve 33 and an air valve 32 are provided in the valve body 31. The injector housing 13 is provided with a diesel high-pressure oil inlet 17, a natural gas high-pressure air inlet 11 and a diesel oil return channel 16. The natural gas high-pressure air inlet 11 passes through the housing. The internal air passage 24 and the shell internal communicating air passage 25 are connected with the corresponding natural gas chamber 36 and the air valve 32 on the valve body 31 through the intermediate body air passage 40 and the nozzle air passage 26 on the intermediate body 30, and are controlled by the natural gas solenoid valve 1. The diesel high-pressure oil inlet 17 is connected with the high-pressure oil storage chamber 51 and the needle valve 33 through the third high-pressure oil passage 19 on the intermediate body 30, and is controlled by the diesel solenoid valve 6. A natural gas spray hole 38 is provided on the valve body 31 for the air valve 32, and a diesel spray hole 39 is provided on the air valve 32 for the needle valve 33.

[0028] Further, the diesel solenoid valve 6 is connected with the first oil channel 10 through the first connecting channel 45, and the diesel solenoid valve 6 controls the second ball guide 8 through the diesel armature 7 to drive the second ball valve 9 to control the opening and closing of the needle valve 33. The diesel high-pressure oil inlet 17 is connected with the third high-pressure oil channel 19 and the fourth high-pressure oil channel 20 on the intermediate body 30 through the second high-pressure oil channel 18, so that the high-pressure oil enters the needle valve control chamber 50 through the fourth high-pressure oil channel 20 and the needle valve oil inlet throttling hole 22, and then communicates with the fourth oil channel 21 through the needle valve oil outlet throttling hole 23. The fourth oil channel 21 is connected with the first oil channel 10 through the second oil channel 14. The flow rates of the needle valve oil inlet throttling hole 22 and the needle valve oil outlet throttling hole 23 of the needle valve control chamber 50 affect the pressure change speed in the chamber.

[0029] Furthermore, the air valve 32 is provided with a fourth high-pressure oil chamber 29, the needle valve 33 is provided with a needle valve guide sleeve 35, the air valve 32 is provided with an air valve sleeve 34, the fourth high-pressure oil chamber 29 is connected with the high-pressure pressure storage chamber 46, the high-pressure pressure storage chamber 46 is connected with the pressure storage ring belt 44 on the needle valve 33 through the oil hole 47, the pressure storage ring belt 44 is connected with the high-pressure oil storage chamber 51 through the oil channel 28, when the needle valve 33 rises, the high-pressure oil storage chamber 51 is connected with each diesel spray hole 39 on the air valve 32, and injection is performed through each diesel spray hole 39.

[0030] Furthermore, a plurality of intermediate body air passages 40 are respectively provided on the valve body 31 and the intermediate body 30. One end of each intermediate body air passage 40 is connected to the natural gas high-pressure air inlet 11 through the shell internal air passage 24 and the shell internal connecting air passage 25, and the other end is connected to the natural gas chamber 36 through the natural gas passage 49. When the needle valve 32 rises, the natural gas chamber 36 is connected to the injection chamber 37. The valve body 31 is provided with a plurality of natural gas spray holes 38 on the forming surface of the injection chamber 37.

[0031] Furthermore, the natural gas solenoid valve 1 is connected to the third oil channel 15 through the second connecting channel 5, the third oil channel 15 is connected to the valve control chamber 27 through the fifth oil channel 42 and the valve oil outlet throttling hole 41, the high-pressure joint 17 is connected to the valve control chamber 27 through the second high-pressure oil channel 18 and the sixth oil channel 43 via the valve oil inlet throttling hole 48, the flow of the valve oil inlet throttling hole 48 and the valve oil outlet throttling hole 41 of the valve control chamber 27 affects the speed of pressure change in the cavity, and the natural gas solenoid valve 1 is connected to the oil return channel 16 through the diesel oil return channel 12.

[0032] Furthermore, the inner side of the needle valve guide sleeve 35 and the outer side of the needle valve 33 are precisely ground and matched, and the sealing and throttling effects are achieved by controlling the matching gap. The needle valve control chamber 50 is composed of the lower end surface of the injector housing 13 after the needle valve 33 and the needle valve guide sleeve 35 are matched.

[0033] Furthermore, the inner side of the air valve sleeve 34 and the outer side of the air valve 32 are precisely ground and matched, and the sealing and throttling effects are achieved by controlling the matching gap. The air valve control chamber 27 is composed of the air valve 32 and the air valve sleeve 34, which are matched with the needle valve 33, the needle valve guide sleeve 35 and the lower end surface of the injector housing 13.

[0034] Further, the natural gas solenoid valve 1 controls the opening and closing of natural gas, the natural gas solenoid 1 controls the opening and closing of the first ball valve 4, controls the pressure of the valve control chamber 27 and the up and down movement of the valve 32, and finally controls the natural gas nozzle 38 to open or close the jet. The control of the diameter of the valve oil inlet throttle hole 48 and the valve oil outlet throttle hole 41 can effectively adjust the response speed of opening and closing. When in use, the natural gas solenoid 1 controls the rise and fall of the natural gas armature 2. After power is turned on, an electromagnetic force is generated to attract the natural gas armature 2 to rise. After power is turned off, in the absence of electromagnetic force, the natural gas armature 2 falls under the action of the spring force. The rise and fall of the natural gas armature 2 will control the rise and fall of the first ball guide 3 and the first ball valve 4. The rise and fall of the first ball valve 4 will cause the opening and closing of the second connecting channel 5. The opening and closing of the second connecting channel 5 will affect the pressure of the third oil channel 15 and the fifth oil channel 42. When the second connecting channel 5 is opened, the pressure of the fifth oil channel 42 decreases, and when the second connecting channel 5 is closed, the pressure of the fifth oil channel 42 increases.

[0035] Furthermore, the pressure in the valve control chamber 27 will affect the rise and fall of the valve 32. When the pressure in the control chamber 27 drops, the valve 32 rises, and when the pressure in the valve control chamber 27 rises, the valve 32 drops. The high-pressure oil passes through the diesel high-pressure connector 17 through the second high-pressure oil passage 18 and the sixth oil passage 43, and enters the valve control chamber 27 through the valve oil inlet throttling hole 48, and then communicates with the fifth oil passage 42 through the valve oil outlet throttling hole 41. The flow rates of the valve oil inlet throttling hole 48 and the valve oil outlet throttling hole 41 of the valve control chamber 27 affect the speed of pressure change in the chamber. The larger the flow ratio, the faster the pressure relief, and the larger the flow rate of the valve oil inlet throttling hole 48, the faster the pressure increase.

[0036] Furthermore, natural gas enters the injector housing 13 through the natural gas high-pressure inlet 11, flows into the intermediate body air channel 40 and the nozzle air channel 26 through the internal air channel 24 of the housing and the internal connecting air channel 25 of the housing, and the natural gas is distributed in the nozzle natural gas chamber 36 at a certain pressure.

[0037] Further, when the natural gas electromagnet 1 is energized, causing the first ball valve 4 to rise, causing the second connecting channel 5 to open and the pressure of the fifth oil channel 42 to drop, the pressure in the gas valve control chamber 27 to drop, the gas valve 32 to rise, and the natural gas flows from the volume chamber 36 into the injection chamber 37, and finally is sprayed through the natural gas spray hole 38. The flow ratio of the gas valve oil inlet throttle hole 48 and the gas valve oil outlet throttle hole 41 affects the injection timing and injection amount of the natural gas. Conversely, when the natural gas electromagnet 1 is de-energized, causing the first ball valve 4 to drop, causing the second connecting channel 5 to close and the pressure of the fifth oil channel 42 to rise, the pressure in the gas valve control chamber 27 to rise, the gas valve 32 to drop, the natural gas in the natural gas volume chamber 36 is disconnected from the injection chamber 37, and the natural gas stops spraying. The rising height of the gas valve 32 can affect the throttling effect of the seat sealing area, thereby affecting the maximum natural gas injection amount.

[0038] Furthermore, the diesel solenoid valve 6 controls the opening and closing of the second ball valve 9, controls the pressure of the needle valve control chamber 50 and the up and down movement of the needle valve 33, and the upward and downward movement of the needle valve 33 controls the diesel nozzle 39 to open and close the injection. The control of the diameter of the diesel inlet throttling hole 22 and the diameter of the diesel outlet throttling hole 23 can effectively adjust the opening and closing response speed.

[0039] Furthermore, the diesel solenoid valve 6 controls the rise and fall of the diesel armature 7. After power is turned on, an electromagnetic force is generated to attract the diesel armature 7 to rise. After power is turned off, in the absence of the electromagnetic force, the diesel armature 7 falls under the action of the spring force. The rise and fall of the diesel armature 7 will control the rise and fall of the second ball guide 8 and the second ball valve 9. The rise and fall of the second ball valve 9 will affect the opening and closing of the first connecting channel 45. The opening and closing of the first connecting channel 45 will affect the pressures of the first oil channel 10, the second oil channel 14 and the fourth oil channel 21. When the first connecting channel 45 is opened, the pressure of the fourth oil channel 21 drops. When the first connecting channel 45 is closed, the pressure of the fourth oil channel 21 rises. The pressure of the needle valve control chamber 50 will affect the rise and fall of the needle valve 33. When the pressure of the needle valve control chamber 50 drops, the needle valve 33 rises. When the pressure of the needle valve control chamber 50 rises, the needle valve 33 falls.

[0040] Furthermore, high-pressure oil passes through the diesel high-pressure oil inlet 17, the second high-pressure oil channel 18 and the fourth high-pressure oil channel 20, and the needle valve oil inlet throttling hole 22 into the needle valve control chamber 50, and then communicates with the fourth oil channel 21 through the needle valve oil outlet throttling hole 23. The flow rates of the needle valve oil inlet throttling hole 22 and the needle valve oil outlet throttling hole 23 of the needle valve control chamber 50 affect the pressure change speed in the needle valve control chamber 50. The larger the flow ratio, the faster the pressure relief, the larger the flow rate of the needle valve oil inlet throttling hole 22, and the faster the pressure increase. At the same time, high-pressure oil passes through the diesel high-pressure oil inlet 17, the second high-pressure oil channel 18 and the third high-pressure oil channel 19 into the fourth high-pressure oil chamber 29. The high-pressure oil in the fourth high-pressure oil chamber 29 enters the high-pressure pressure storage chamber 46, and then enters the pressure storage ring belt 44 through the oil hole 47. The high-pressure oil in the pressure storage ring belt 44 enters the high-pressure oil storage chamber 51 through the oil passage 28.

[0041] Further, when the diesel solenoid valve 6 is powered on, causing the second ball valve 9 to rise, causing the first connecting channel 45 to open and the pressure of the fourth oil channel 21 to drop, the pressure in the needle valve control chamber 50 to drop, the needle valve 33 to rise, and the high-pressure diesel is sprayed from the high-pressure oil storage chamber 51 through the diesel spray hole 39. Conversely, when the diesel solenoid valve 6 is powered off, causing the second ball valve 9 to drop, causing the first connecting channel 45 to close and the pressure of the fourth oil channel 21 to rise, the pressure in the needle valve control chamber 50 to rise, the needle valve 33 to drop to form a seal, the high-pressure oil storage chamber 51 is separated from the diesel spray hole 39, and the diesel stops spraying. The rising height of the needle valve 33 can affect the throttling effect of the seat surface sealing area, thereby affecting the maximum diesel injection amount.

[0042] The present invention is not limited to the above-mentioned embodiments. Anyone should know that any technical solution identical or similar to the present invention made under the inspiration of the present invention shall fall within the protection scope of the present invention.

[0043] The techniques, shapes, and structural parts not described in detail in the present invention are all well-known techniques.

Claims

1. A novel dual-fuel injector, comprising an injector housing, a natural gas solenoid valve, a diesel solenoid valve and a valve body, characterized in that: The injector housing is connected and fastened with the natural gas solenoid valve, the diesel solenoid valve and the valve body. An intermediate body is provided at the connection between the valve body and the injector housing. A needle valve and an air valve are provided in the valve body. A diesel high-pressure oil inlet, a natural gas high-pressure air inlet and a diesel oil return hole are provided on the injector housing. The natural gas high-pressure air inlet is connected with the corresponding natural gas storage cavity and the air valve on the valve body through the internal air channel of the housing and the internal connecting air channel of the housing through the intermediate air channel and the nozzle air channel on the intermediate body, and is controlled by the natural gas solenoid valve. The diesel high-pressure oil inlet is connected with the high-pressure oil storage cavity and the needle valve through the high-pressure oil channel on the intermediate body, and is controlled by the diesel solenoid valve. A natural gas spray hole is provided at the head of the valve body, and a diesel spray hole is provided at the head of the air valve. A plurality of intermediate air channels are provided on the intermediate body. One end of each intermediate air channel is connected with the natural gas high-pressure air inlet through the internal air channel of the housing and the internal connecting air channel of the housing, and the other end is connected with the natural gas storage cavity and the injection cavity through the natural gas channel, so that a plurality of natural gas spray holes are provided on the valve body forming the injection cavity; The diesel solenoid valve is connected with the first oil channel through the first connecting channel, and the diesel solenoid valve controls the second ball guide to drive the second ball valve through the diesel armature to control the opening and closing of the needle valve. The diesel high-pressure oil inlet is connected with the third high-pressure oil channel and the fourth high-pressure oil channel on the intermediate body through the second high-pressure oil channel, so that the high-pressure oil enters the needle valve control chamber through the fourth high-pressure oil channel and the needle valve oil inlet throttling hole, and then communicates with the fourth oil channel through the needle valve oil outlet throttling hole. The fourth oil channel is connected with the first oil channel through the second oil channel, and finally realizes the control of the diesel solenoid valve on the opening and closing of the diesel injection. The flow of the needle valve oil inlet throttling hole and the needle valve oil outlet throttling hole of the needle valve control chamber affects the pressure change speed in the chamber. The diesel solenoid valve end is connected with the return oil channel through the diesel return oil channel; The air valve is provided with a fourth high-pressure oil chamber, a needle valve guide sleeve is provided on the needle valve, an air valve sleeve is provided on the air valve, the fourth high-pressure oil chamber is connected with the high-pressure pressure storage chamber, the high-pressure pressure storage chamber is connected with the pressure storage ring belt on the needle valve through the oil hole, the pressure storage ring belt is connected with the high-pressure oil storage chamber through the oil channel, when the needle valve rises, the high-pressure oil storage chamber is connected with each diesel injection hole on the air valve, and the diesel is sprayed through each diesel injection hole; The natural gas solenoid valve is connected to the third oil channel through the second connecting channel, the third oil channel is connected to the gas valve oil outlet throttle hole and the gas valve control chamber through the fifth oil channel, the diesel high-pressure oil inlet is connected to the gas valve oil inlet throttle hole and the gas valve control chamber through the second high-pressure oil channel and the sixth oil channel, and finally the natural gas solenoid valve controls the opening and closing of the natural gas injection. The flow of the gas valve oil inlet throttle hole and the gas valve oil outlet throttle hole of the gas valve control chamber affects the pressure change speed in the chamber, and the natural gas solenoid valve end is connected to the oil return channel through the diesel oil return channel; The inner side of the needle valve guide sleeve and the outer side of the needle valve are precisely ground and matched, and the matching gap is controlled to have a sealing and throttling effect. The needle valve control chamber is composed of the lower end surface of the intermediate body after the needle valve and the needle valve guide sleeve are matched. The inner side of the air valve sleeve and the outer side of the air valve are precisely ground and matched, and the sealing and throttling effects are achieved by controlling the matching gap. The air valve control chamber is composed of the air valve and the air valve sleeve matched with the needle valve, the needle valve guide sleeve and the lower end surface of the intermediate body.

Images