CN117869087A - Methanol diesel double-nozzle double-direct injection engine and control method thereof - Google Patents
Methanol diesel double-nozzle double-direct injection engine and control method thereof Download PDFInfo
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- CN117869087A CN117869087A CN202311852906.1A CN202311852906A CN117869087A CN 117869087 A CN117869087 A CN 117869087A CN 202311852906 A CN202311852906 A CN 202311852906A CN 117869087 A CN117869087 A CN 117869087A
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- OKKJLVBELUTLKV-UHFFFAOYSA-N Methanol Chemical compound OC OKKJLVBELUTLKV-UHFFFAOYSA-N 0.000 title claims abstract description 499
- 238000002347 injection Methods 0.000 title claims abstract description 79
- 239000007924 injection Substances 0.000 title claims abstract description 79
- 238000000034 method Methods 0.000 title claims abstract description 13
- 239000002283 diesel fuel Substances 0.000 claims abstract description 68
- 238000002485 combustion reaction Methods 0.000 claims description 38
- 239000000446 fuel Substances 0.000 claims description 20
- 238000001914 filtration Methods 0.000 claims description 13
- 239000007921 spray Substances 0.000 claims description 11
- LFQSCWFLJHTTHZ-UHFFFAOYSA-N Ethanol Chemical compound CCO LFQSCWFLJHTTHZ-UHFFFAOYSA-N 0.000 claims description 9
- 238000013459 approach Methods 0.000 claims description 3
- 230000006835 compression Effects 0.000 claims description 3
- 238000007906 compression Methods 0.000 claims description 3
- ZYBWTEQKHIADDQ-UHFFFAOYSA-N ethanol;methanol Chemical compound OC.CCO ZYBWTEQKHIADDQ-UHFFFAOYSA-N 0.000 claims 1
- 239000003344 environmental pollutant Substances 0.000 abstract description 2
- 231100000719 pollutant Toxicity 0.000 abstract description 2
- 239000007789 gas Substances 0.000 description 11
- 238000009792 diffusion process Methods 0.000 description 8
- 239000002828 fuel tank Substances 0.000 description 4
- 230000006872 improvement Effects 0.000 description 4
- 238000005507 spraying Methods 0.000 description 4
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 description 3
- WSFSSNUMVMOOMR-UHFFFAOYSA-N Formaldehyde Chemical compound O=C WSFSSNUMVMOOMR-UHFFFAOYSA-N 0.000 description 3
- 238000000889 atomisation Methods 0.000 description 3
- 229910052799 carbon Inorganic materials 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 239000000203 mixture Substances 0.000 description 3
- 238000006467 substitution reaction Methods 0.000 description 3
- 238000009834 vaporization Methods 0.000 description 3
- 230000008016 vaporization Effects 0.000 description 3
- 238000006243 chemical reaction Methods 0.000 description 2
- 238000013461 design Methods 0.000 description 2
- 230000009977 dual effect Effects 0.000 description 2
- 239000001257 hydrogen Substances 0.000 description 2
- 229910052739 hydrogen Inorganic materials 0.000 description 2
- 239000003595 mist Substances 0.000 description 2
- TVMXDCGIABBOFY-UHFFFAOYSA-N octane Chemical compound CCCCCCCC TVMXDCGIABBOFY-UHFFFAOYSA-N 0.000 description 2
- MYMOFIZGZYHOMD-UHFFFAOYSA-N Dioxygen Chemical compound O=O MYMOFIZGZYHOMD-UHFFFAOYSA-N 0.000 description 1
- UFHFLCQGNIYNRP-UHFFFAOYSA-N Hydrogen Chemical compound [H][H] UFHFLCQGNIYNRP-UHFFFAOYSA-N 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 229910001882 dioxygen Inorganic materials 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 239000003502 gasoline Substances 0.000 description 1
- 150000002431 hydrogen Chemical class 0.000 description 1
- 239000012535 impurity Substances 0.000 description 1
- 239000002440 industrial waste Substances 0.000 description 1
- 238000002156 mixing Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000006386 neutralization reaction Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 239000002994 raw material Substances 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 239000004071 soot Substances 0.000 description 1
- 230000002194 synthesizing effect Effects 0.000 description 1
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Abstract
The invention discloses a methanol diesel oil double-nozzle double-direct injection engine and a control method thereof, which belong to the technical field of engines and solve the technical problems of low heat efficiency and high emission of harmful pollutants in the existing methanol engine.
Description
Technical Field
The invention relates to the technical field of engines, in particular to a methanol diesel double-nozzle double-direct injection engine and a control method thereof.
Background
The methanol has higher octane number and vaporization latent heat, and the flame propagation speed is higher than that of gasoline, so that the knocking is restrained and the heat efficiency is improved; the molecular oxygen content of the methanol reaches 50%, and the combustion process hardly generates soot. As the largest global methanol producing country and consuming country, methanol has long been the dominant energy project in our country. Along with the rapid development of renewable energy sources in China, renewable energy sources such as wind energy, solar energy and the like are utilized to generate electricity to prepare green hydrogen, and then the green hydrogen is synthesized with CO2 obtained in an industrial waste gas mode to prepare safe and convenient-to-transport methanol fuel, and the methanol fuel can be used as a raw material for synthesizing methanol again from CO2 generated after combustion of fuel of an internal combustion engine, so that zero carbon emission of a full life cycle is realized.
Methanol is currently used in internal combustion engines, mainly alone or in admixture and combination with other fuels, to achieve ignition and combustion by the concept of spark plug or dual fuel diesel ignition. In the aspect of a spark ignition engine, as the methanol has high octane number, large vaporization latent heat and high flame propagation speed, pure methanol combustion can obviously improve antiknock performance and improve thermal efficiency and emission, but also has the problems of difficult cold start, poor combustion stability under small load, limited thermal efficiency improvement due to knocking and the like. In the aspect of igniting a methanol engine by dual-fuel diesel, the method mainly comprises premixing a methanol air passage/manifold and direct diesel injection ignition at present, wherein the combustion mode can achieve the thermal efficiency equivalent to that of a diesel engine, but the methanol substitution rate is affected by knocking and is reduced along with the increase of load, and the carbon neutralization target cannot be achieved due to the lower ratio of the methanol substitution rate.
The methanol diesel double direct injection engine has a combustion principle similar to that of a diesel engine, forms an ignition source by spraying a trace amount of diesel, and then sprays high-pressure methanol to mix with high-temperature high-pressure air to form a combustible mixed gas. When the mixed gas encounters a micro ignition source, the mixed gas ignites by itself and expands rapidly, and the piston is pushed to do work downwards. In the whole process, the diesel oil is used for providing an ignition source, and the methanol is the main fuel, so that the substitution rate of the methanol is more than 90%. The methanol has high combustion rate and good antiknock performance, and in addition, the high-pressure injection can also increase the uniformity of the mixed gas and improve the combustion rate. Therefore, the methanol diesel double direct injection engine can realize higher thermal efficiency and lower emission than a diesel engine on the premise of not losing dynamic indexes, and is one of key routes of carbon reduction and efficient clean combustion of the internal combustion engine.
However, the existing methanol engine has the technical problems of low thermal efficiency and high emission of harmful pollutants.
Disclosure of Invention
The invention aims to solve the technical problems of the prior art, and the invention aims to provide a methanol diesel double-nozzle double-direct injection engine.
The invention also aims to provide a control method of the methanol diesel double-nozzle double-direct injection engine.
In order to achieve the above object, the present invention provides a methanol diesel dual-nozzle dual-direct injection engine, the engine is a compression ignition engine, and includes a low pressure oil pump, a diesel oil filtering component, a high pressure oil pump, a high pressure diesel oil common rail pipe, a low pressure diesel oil pump, a methanol filtering component, a high pressure methanol pump, a high pressure methanol common rail pipe, and at least one cylinder, the cylinders are respectively provided with a diesel oil injector and a methanol injector, the methanol injector and the cylinder are coaxially arranged, the diesel oil injector is inclined to extend in the axial direction of the cylinder, the axis of the diesel oil injector and the axis of the cylinder are in the same plane, the included angle between the axis of the diesel oil injector and the axis of the cylinder is 20-40 °, the low pressure oil pump is sequentially connected with the diesel oil filtering component, the high pressure oil pump, the high pressure diesel oil common rail pipe, the diesel oil injector, the methanol injector, the low pressure methanol pump are sequentially connected with the methanol filtering component, the high pressure methanol pump, the high pressure methanol common rail pipe, the methanol injector, the nozzle of the diesel oil injector and the diesel oil injector, wherein the nozzle of the diesel oil injector and the methanol injector are arranged at intervals of the diesel oil injector and the diesel oil injector.
As a further improvement, the spray holes of the methanol sprayer are arranged in an axisymmetric way.
Further, if the included angle between the axis of the diesel oil injector and the axis of the cylinder is 20-30 degrees, the spray holes of the diesel oil injector are arranged in an axisymmetric manner; otherwise, the spray holes of the diesel oil injector are arranged in a non-axisymmetric way.
Further, the diesel filter component comprises a diesel coarse filter and a diesel fine filter.
Further, the methanol filtering component comprises a methanol coarse filter and a methanol fine filter.
In order to achieve the second purpose, the invention provides a control method of a methanol diesel double-nozzle double-direct injection engine, wherein when the engine runs at medium and high load, diesel and methanol are injected for a single time; the diesel injector injects a small amount of diesel into the cylinder when the piston of the cylinder approaches 6-10 degrees CA before the top dead center, so as to form a micro ignition source; then, the methanol injector injects methanol into the cylinder within 1-4 degrees CA after diesel injection is finished to form combustible mixed gas; the diesel injection proportion accounts for less than 10% of the total fuel calorific value.
As a further improvement, when the engine is running at low load, the methanol is injected twice, and the diesel is injected once; the first injection timing of the methanol is within 25 CA before the upper dead center, and the first injection amount of the methanol accounts for 80-90% of the heat value of the total methanol fuel; the diesel injection timing is 6-9 degrees CA before the top dead center, the diesel injection proportion accounts for 10% -15% of the total fuel calorific value proportion, and the methanol second injection timing is 1-3 degrees CA after the diesel injection is finished.
Further, when the engine is started or methanol injection fails, only diesel injection is performed to achieve the pure diesel combustion mode.
Advantageous effects
Compared with the prior art, the invention has the advantages that:
1. in the invention, the methanol and the diesel oil are directly sprayed into the cylinder before the top dead center, and the high-pressure injection of the methanol can ensure that the methanol has better atomization and mixing effects, can ensure that the engine maintains the same power target as a diesel engine, and simultaneously achieves higher thermal efficiency and lower emission than the diesel engine.
The invention adopts the double direct injection system to enable the methanol to burn more fully, and compared with other methanol engines, the invention can greatly reduce the emission of formaldehyde and unburned methanol.
3. According to the invention, whether the load and the methanol system fail or not is considered, different fuel injection schemes are set, and the stable operation of the engine under all working conditions is realized.
4. According to the invention, the proportion of methanol to diesel oil and the injection time of the methanol to diesel oil can be timely adjusted according to the load and the rotating speed requirements, so that the stable operation and the efficient clean combustion of the engine under all working conditions are realized.
Drawings
FIG. 1 is a schematic view of an engine according to the present invention;
FIG. 2 is a schematic view of a bundle of methanol and diesel oil mist when the diesel injector of the present invention is tilted at a large angle;
FIG. 3 is a schematic view of a bundle of methanol and diesel oil mist at a small angle of inclination of the diesel injector of the present invention;
FIG. 4 is a graph of injection flow rates of methanol and diesel fuel for an engine operating at medium and high loads in accordance with the present invention;
fig. 5 is a graph of injection flow rates of methanol and diesel fuel for an engine operating at low load in accordance with the present invention.
Wherein: 1-cylinder liner, 2-piston, 3-methanol fuel tank, 4-low pressure alcohol pump, 5-methanol strainer, 6-methanol fine filter, 7-high pressure methanol pump, 8-exhaust valve, 9-cylinder head, 10-methanol injector, 11-diesel injector, 12-intake valve, 13-high pressure methanol common rail pipe, 14-ECU, 15-high pressure diesel common rail pipe, 16-high pressure oil pump, 17-diesel fine filter, 18-diesel strainer, 19-low pressure oil pump, 20-diesel tank, 21-cylinder, 22-diesel filter module, 23-methanol filter module, 24-oil pipe, 25-alcohol pipe, 26-diesel oil bundle, 27-methanol bundle, 28-methanol fuel tank.
Detailed Description
The invention will be further described with reference to specific embodiments in the drawings.
Referring to fig. 1 to 5, a methanol diesel dual-nozzle dual-direct injection engine is a compression ignition engine, and comprises a low-pressure oil pump 19, a diesel oil filtering component 22, a high-pressure oil pump 16, a high-pressure diesel oil common rail pipe 15, a low-pressure alcohol pump 4, a methanol filtering component 23, a high-pressure methanol pump 7, a high-pressure methanol common rail pipe 13 and at least one cylinder 21. The cylinder 21 is respectively provided with a diesel oil injector 11 and a methanol injector 10, specifically, a cylinder sleeve 1 is arranged in the cylinder 21, a piston 2 is arranged in the cylinder sleeve 1, a cylinder cover 9 is arranged at the top of the cylinder 21, and a closed space surrounded by the cylinder sleeve 1, the piston 2 and the cylinder cover 9 is a combustion chamber of the cylinder 21. The cylinders 21 are connected to the intake passage via intake valves 12 and to the exhaust passage via exhaust valves 8, the intake valves 12 being adapted to receive fresh air and the exhaust valves 8 being adapted to exhaust the exhaust gases in the combustion chamber. The low-pressure oil pump 19 is sequentially connected with the diesel oil filtering component 22, the high-pressure oil pump 16, the high-pressure diesel oil common rail pipe 15 and the diesel oil injector 11 through the oil pipe 24, the low-pressure oil pump 19 is connected with the diesel oil tank 20 through the oil pipe 24, and diesel oil sequentially passes through the diesel oil tank 20, the low-pressure oil pump 19, the diesel oil filtering component 22 and the high-pressure oil pump 16 to reach the high-pressure diesel oil common rail pipe 15 and is supplied to the diesel oil injector 11. The low-pressure alcohol pump 4 is sequentially connected with the methanol filtering component 23, the high-pressure methanol pump 7, the high-pressure methanol common rail pipe 13 and the methanol sprayer 10 through the alcohol pipe 25, the low-pressure alcohol pump 4 is connected with the methanol fuel tank 28 through the alcohol pipe 25, and methanol sequentially passes through the methanol fuel tank 3, the low-pressure alcohol pump 4, the methanol filtering component 23 and the high-pressure methanol pump 7, reaches the high-pressure methanol common rail pipe 13 and is supplied to the methanol sprayer 10. The ECU14 controls the operation of the diesel high-pressure pump 16 and the methanol high-pressure pump 7 according to the engine operation conditions to control and regulate the pressures of the high-pressure diesel common rail pipe 15, the high-pressure methanol common rail pipe 13, and to control the injection of the in-cylinder methanol injector 10 and the diesel injector 11.
The methanol injector 10 and the diesel injector 11 are both jet orifice type high-pressure common rail injectors. Single or multiple injections in a single cycle can be realized, and the injection times, the injection timing and the injection pulse width can be adjusted according to actual requirements.
The methanol injector 10 is arranged coaxially with the cylinder 21, i.e. the axis of the methanol injector 10 coincides with the axis of the cylinder 21. The diesel injector 11 extends obliquely to the axial direction of the cylinder 21, the axis of the diesel injector 11 is in the same plane with the axis of the cylinder 21, and the included angle between the axis of the diesel injector 11 and the axis of the cylinder 21 is 20-40 degrees. The nozzle of the diesel injector 11 is spaced from the nozzle of the methanol injector 10, i.e. the heads of both the methanol injector 10 and the diesel injector 11 are at a distance and are exposed to the combustion chamber of the cylinder 21. In actual operation, a portion of the diesel oil bundles 26 ejected from the diesel injector 11 interfere with the methanol bundles 27 ejected from the methanol injector 10.
The spray holes of the methanol sprayer 10 are axisymmetrically arranged, so that high-pressure methanol is sprayed out and then uniformly distributed in the cylinder 1. The direct injection diesel injector 11 is designed to spray holes according to the inclination angle, and when the inclination angle is larger, the non-axisymmetric design is adopted; when the inclination angle is smaller, an axisymmetric design is adopted.
Preferably, if the included angle between the axis of the diesel injector 11 and the axis of the cylinder 21 is 20-30 degrees, the spray holes of the diesel injector 11 are axially symmetrically arranged; otherwise, the injection holes of the diesel injector 11 are arranged non-axisymmetrically.
The diesel oil filter assembly 22 comprises a diesel oil coarse filter 18 and a diesel oil fine filter 17, the methanol filter assembly 23 comprises a methanol coarse filter 5 and a methanol fine filter 6, impurities in diesel oil and methanol can be effectively removed by two-stage filtration, the working stability of a diesel oil injection system and a methanol injection system is guaranteed, the diesel oil injection system comprises the low-pressure oil pump 19, the diesel oil filter assembly 22, a high-pressure oil pump 16, a high-pressure diesel oil common rail pipe 15 and a diesel oil injector 11, and the methanol injection system comprises the low-pressure alcohol pump 4, the methanol filter assembly 23, the high-pressure methanol pump 7, the high-pressure methanol common rail pipe 13 and the methanol injector 10.
A control method of a methanol diesel double-nozzle double-direct injection engine comprises a medium-high load diesel micro-ignition methanol diffusion combustion mode, a low-load most premixed combustion+a small part diffusion combustion mode and a pure diesel combustion mode. In order to avoid that the methanol spray hits the inner wall of the cylinder 21, the injection timing of the high pressure methanol is not too early, and the injection timing of all the methanol is within 25 ° CA before the top dead center. High pressure methanol injection is used in all dual fuel modes (i.e., medium and high duty diesel micro-pilot methanol diffusion combustion mode, low duty majority premixed combustion + minority diffusion combustion mode) to ensure better atomization and vaporization of the methanol and to ensure complete injection within the required pulse width. In the dual-fuel mode, the diesel injector 11 mainly plays a role in ignition, the injection proportion is not more than 15%, single injection is adopted, and the injection timing is 1-9 degrees CA before the top dead center; the pure diesel mode is mainly used for two conditions of starting an engine and generating faults of a methanol injection system, and can realize the switching of the methanol diesel dual-fuel mode and the pure diesel mode at any time according to requirements.
As shown in fig. 4, the medium-high load diesel micro-ignition methanol diffusion combustion mode specifically comprises: when the engine runs at medium and high load, diesel oil and methanol are injected for one time; the diesel injector 11 injects a small amount of diesel into the cylinder 21 when the piston 2 of the cylinder 21 approaches 6-10 degrees CA before the top dead center to form a micro ignition source, wherein the injection proportion of the diesel is within 10 percent of the heat value of the total fuel; subsequently, the methanol injector 10 injects methanol into the combustion chamber of the cylinder 21 within 1-4 ° CA after the end of diesel injection, and mixes with air of high temperature and high pressure to form a combustible mixture; when the mixed gas encounters a micro ignition source formed by diesel oil, the mixed gas ignites by itself and expands rapidly, the piston 2 is pushed to do work downwards, and the whole combustion process is diffusion combustion of methanol which is micro-ignited by the diesel oil.
As shown in fig. 5, the low-load most premixed combustion+less diffusion combustion mode is specifically: when the engine runs at low load, methanol adopts two injections, and diesel adopts a single injection; the first injection timing of the methanol is within 25 CA before the upper dead center, so that wall collision caused by early injection timing of the high-pressure methanol is avoided, and the first injection amount of the methanol accounts for 80-90% of the total methanol fuel calorific value; the diesel injection timing is 6-9 degrees CA before the top dead center, and the diesel injection proportion accounts for 10% -15% of the total fuel calorific value proportion so as to improve the combustion stability under low load; the method comprises the steps of spraying most of methanol into a cylinder during the first injection and quickly forming a premixed gas mixture with surrounding air, spraying diesel oil into the cylinder for quick atomization, evaporation and ignition, igniting the premixed gas mixture of the methanol formed in the last step in a high-temperature area formed by combustion, and spraying the rest methanol into the cylinder and burning at the second injection timing of the methanol of 1-3 CA after the diesel oil injection is finished to control the combustion reaction rate, so that the reaction temperature can be reduced to a certain extent, the reaction rate is controlled, the occurrence of knocking is restrained, the combustion mode at low load is the premixed combustion of most and the diffusion combustion of a small part, the thermal efficiency of the engine can be improved to the greatest extent, and meanwhile, the problems of knocking and the excessive pressure rise rate are avoided.
The foregoing is merely a preferred embodiment of the present invention, and it should be noted that modifications and improvements can be made by those skilled in the art without departing from the structure of the present invention, and these do not affect the effect of the implementation of the present invention and the utility of the patent.
Claims (8)
1. The utility model provides a two direct injection engines of methanol diesel oil double jet mouth, its characterized in that, the engine is compression ignition engine, including low pressure oil pump (19), diesel oil filter module (22), high pressure oil pump (16), high pressure diesel oil common rail pipe (15), low pressure alcohol pump (4), methyl alcohol filter module (23), high pressure methyl alcohol pump (7), high pressure methyl alcohol common rail pipe (13), at least one cylinder (21), cylinder (21) are equipped with diesel oil sprayer (11), methyl alcohol spray-up ware (10) respectively, methyl alcohol spray-up ware (10) with cylinder (21) coaxial arrangement, diesel oil sprayer (11) slope to the axis direction of cylinder (21) extends, the axis of diesel oil sprayer (11) with the axis of cylinder (21) is in the coplanar, just the axis of diesel oil sprayer (11) is 20-40 with the contained angle of the axis of cylinder (21), low pressure oil pump (19) connect gradually diesel oil filter module (22), high pressure oil pump (16), high pressure diesel oil pump (15), methyl alcohol spray-up ware (11), methyl alcohol spray-up ware (25) through high pressure common rail pipe (11), methyl alcohol spray-up ware (25) methanol oil pump (21) in proper order, the nozzles of the diesel oil injector (11) are arranged at intervals with the nozzles of the methanol injector (10), and part of diesel oil bundles (26) sprayed out of the diesel oil injector (11) interfere with methanol bundles (27) sprayed out of the methanol injector (10).
2. The methanol diesel double-nozzle double-direct injection engine according to claim 1, characterized in that the spray holes of the methanol-ethanol sprayer (10) are axisymmetrically arranged.
3. The methanol diesel double-nozzle double-direct injection engine according to claim 1, characterized in that if the included angle between the axis of the diesel injector (11) and the axis of the cylinder (21) is 20-30 degrees, the spray holes of the diesel injector (11) are axisymmetrically arranged; otherwise, the spray holes of the diesel oil injector (11) are arranged in a non-axisymmetric way.
4. The methanol diesel dual-nozzle dual-direct injection engine according to claim 1, characterized in that the diesel filter assembly (22) comprises a diesel strainer (18) and a diesel fine filter (17).
5. The methanol diesel double-nozzle double-direct injection engine according to claim 1, wherein the methanol filtering component (23) comprises a methanol coarse filter (5) and a methanol fine filter (6).
6. A control method applied to the methanol diesel double-nozzle double-direct injection engine according to any one of claims 1 to 5, characterized in that when the engine is operated at medium and high load, diesel and methanol are both injected in a single time; the diesel injector (11) injects a small amount of diesel into the cylinder (21) when the piston (2) of the cylinder (21) approaches 6-10 degrees CA before the top dead center to form a micro ignition source; then, the methanol injector (10) injects methanol into the cylinder (21) within 1-4 degrees CA after the diesel injection is finished to form a combustible mixed gas; the diesel injection proportion accounts for less than 10% of the total fuel calorific value.
7. The control method of a methanol diesel double-nozzle double-direct injection engine according to claim 6, wherein when the engine is operated at a low load, methanol is injected twice, and diesel is injected once; the first injection timing of the methanol is within 25 CA before the upper dead center, and the first injection amount of the methanol accounts for 80-90% of the heat value of the total methanol fuel; the diesel injection timing is 6-9 degrees CA before the top dead center, the diesel injection proportion accounts for 10% -15% of the total fuel calorific value proportion, and the methanol second injection timing is 1-3 degrees CA after the diesel injection is finished.
8. The control method of a methanol diesel double nozzle double direct injection engine according to claim 7, wherein when the engine is started or methanol injection is failed, only diesel injection is performed to realize a pure diesel combustion mode.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202311852906.1A CN117869087A (en) | 2023-12-29 | 2023-12-29 | Methanol diesel double-nozzle double-direct injection engine and control method thereof |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202311852906.1A CN117869087A (en) | 2023-12-29 | 2023-12-29 | Methanol diesel double-nozzle double-direct injection engine and control method thereof |
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| CN117869087A true CN117869087A (en) | 2024-04-12 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202311852906.1A Pending CN117869087A (en) | 2023-12-29 | 2023-12-29 | Methanol diesel double-nozzle double-direct injection engine and control method thereof |
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| Country | Link |
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| CN (1) | CN117869087A (en) |
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2023
- 2023-12-29 CN CN202311852906.1A patent/CN117869087A/en active Pending
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