CN115217662B - Double-valve oil injection system of diesel engine and low-rotation-speed high-pressure oil injection control method - Google Patents
Double-valve oil injection system of diesel engine and low-rotation-speed high-pressure oil injection control method Download PDFInfo
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- CN115217662B CN115217662B CN202210719363.5A CN202210719363A CN115217662B CN 115217662 B CN115217662 B CN 115217662B CN 202210719363 A CN202210719363 A CN 202210719363A CN 115217662 B CN115217662 B CN 115217662B
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- 238000002347 injection Methods 0.000 title claims abstract description 122
- 239000007924 injection Substances 0.000 title claims abstract description 122
- 238000000034 method Methods 0.000 title claims abstract description 23
- 239000003921 oil Substances 0.000 claims description 134
- 239000000446 fuel Substances 0.000 claims description 46
- 239000000295 fuel oil Substances 0.000 claims description 6
- 230000009977 dual effect Effects 0.000 claims description 4
- 239000007921 spray Substances 0.000 claims description 2
- 230000008569 process Effects 0.000 abstract description 10
- 238000007906 compression Methods 0.000 abstract description 2
- 230000001276 controlling effect Effects 0.000 description 11
- 238000002485 combustion reaction Methods 0.000 description 5
- 238000004891 communication Methods 0.000 description 3
- 230000003111 delayed effect Effects 0.000 description 3
- 238000006073 displacement reaction Methods 0.000 description 3
- 230000009286 beneficial effect Effects 0.000 description 2
- 238000005507 spraying Methods 0.000 description 2
- 230000001133 acceleration Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000007123 defense Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 239000002828 fuel tank Substances 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 239000000178 monomer Substances 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 230000008520 organization Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/30—Controlling fuel injection
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/30—Controlling fuel injection
- F02D41/38—Controlling fuel injection of the high pressure type
- F02D41/40—Controlling fuel injection of the high pressure type with means for controlling injection timing or duration
- F02D41/401—Controlling injection timing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/30—Controlling fuel injection
- F02D41/38—Controlling fuel injection of the high pressure type
- F02D41/40—Controlling fuel injection of the high pressure type with means for controlling injection timing or duration
- F02D41/406—Electrically controlling a diesel injection pump
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
The invention relates to a double-valve oil injection system of a diesel engine and a low-rotation-speed high-pressure oil injection control method, which adopts the double-valve oil injection system of a control oil injector and an electric control unit pump, wherein the pressure establishment is rapid when the pressure establishment process is changed into a closed compression process by closing an electromagnetic valve of the oil injector, and the oil injector is started after the system pressure reaches the system target pressure by phase matching between an oil supply electromagnetic valve and the electromagnetic valve of the oil injector, so that the system can rapidly enter a high-pressure injection stage under a low-speed working condition.
Description
Technical Field
The invention belongs to the technical field of fuel injection control, and particularly relates to a double-valve fuel injection system of a diesel engine and a low-rotation-speed high-pressure fuel injection control method.
Background
With the development of technology, the requirements of the high-strength diesel engine in national defense and civil use are further enhanced, and the high-strength diesel engine is required to have obviously improved performance, namely enhanced power density, in the range of small volume and mass changes. An effective way to increase the power of a diesel engine is to improve the in-cylinder combustion process of the diesel engine, wherein the fuel injection process is used as an initial stage of in-cylinder combustion, and the optimization is the most important factor for organizing good in-cylinder combustion conditions.
An electronic control unit pump (EUP) fuel injection system is taken as a second generation electronic control fuel injection system, is a typical cam-plunger type high-pressure fuel supply system and comprises an electronic control system and a mechanical hydraulic control system. The device has the advantages of small structural change to the original machine, strong environmental adaptability, high oil injection pressure, flexible control and high reliability, is commonly used for high-power diesel engines, and is widely applied to special and military diesel engines. The traditional electric control unit pump system is generally matched with a mechanical oil sprayer, and oil spraying and oil breaking are realized by controlling the establishment of the pressure of a pump end. However, since the pressure is established by pushing the plunger to squeeze the fuel through the cam, the injection pressure is directly related to the rotation speed of the cam, and the start-up pressure and the injection rule of the mechanical injector are not adjustable, the electronic control unit pump system is difficult to establish high injection pressure under the working condition of low rotation speed of the diesel engine. Therefore, in the actual use process, the injection pressure of the injection system adopting the structural form is lower under the low-speed working condition.
Disclosure of Invention
Therefore, the invention aims to provide a double-valve oil injection system of a diesel engine and a low-rotation-speed high-pressure oil injection control method, which can realize the high-pressure oil supply characteristic of an electric control unit pump oil injection system under the working condition of low rotation speed of the diesel engine.
A dual valve fuel injection system for a diesel engine, comprising:
the electric control unit pump is used for outputting fuel to the electric control fuel injector;
the low-pressure oil way is used for inputting fuel into the plunger cavity of the electric control unit pump;
the oil supply cam is used for pushing the plunger of the electric control unit pump to move;
the electric control fuel injector is used for injecting fuel;
the high-pressure oil pipe is connected with the electric control unit pump and the electric control oil injector and is used for conveying the fuel oil output by the electric control unit pump to the electric control oil injector;
a pump end electromagnetic valve (40) which is arranged in the electric control unit pump and is used for controlling the on-off of the low-pressure oil way;
the oil injection electromagnetic valve (60) is arranged in the electric control oil injector and is used for controlling the electric control oil injector to spray oil;
and the electronic control unit is used for controlling the opening and closing of the pump end electromagnetic valve (40) and the oil injection electromagnetic valve (60).
A low-rotation-speed high-pressure oil injection control method of a double-valve oil injection system of a diesel engine comprises the following steps:
step one, initially, opening a pump end electromagnetic valve (40) and closing an oil injection electromagnetic valve (60);
step two, after starting, controlling the oil supply cam to rotate according to a set rotating speed; when the camshaft of the oil supply cam (3) rotates to a certain angle position, the electromagnetic valve (40) at the pump end is closed, the pressure in the cavity of the plunger pump is monitored, and when the set target pressure is reached, the rotating angle of the camshaft at the moment is recorded, namely the opening moment of the electromagnetic valve (60) for oil injection; under the same target pressure, continuously changing the closing time of a solenoid valve (40) at the pump end, and recording the cam shaft angle when the pressure in the cavity of the plunger pump reaches the target pressure; thus, the corresponding relation between the cam shaft angle when the pump end electromagnetic valve (40) is closed and the cam shaft angle when the oil injection electromagnetic valve (60) is opened under a target pressure is obtained;
and the like, obtaining the corresponding relation between the cam shaft angle when the pump end electromagnetic valve (40) is closed and the cam shaft angle when the oil injection electromagnetic valve (60) is opened under different target pressures;
and thirdly, when oil injection is controlled, finding out the corresponding relation under the target pressure according to the set target pressure, and then finding out the cam shaft angle when the pump end electromagnetic valve (40) is closed in the corresponding relation according to the oil injection time, namely the cam shaft angle when the oil injection electromagnetic valve (60) is opened, and controlling the closing of the pump end electromagnetic valve (40) and the opening of the oil injection electromagnetic valve (60) according to the two angles.
Preferably, when the oil injection electromagnetic valve (60) is controlled to be opened, the oil injection pulse width is controlled to be below a set value.
Preferably, the oil injection electromagnetic valve (60) is controlled to carry out oil injection with different oil injection pulse widths, the maximum oil injection pulse width meeting the oil injection pressure is determined, and the oil injection pulse width of the oil injection electromagnetic valve (60) is controlled to be smaller than the maximum oil injection pulse width.
The invention has the following beneficial effects:
the invention relates to a double-valve oil injection system of a diesel engine and a low-rotation-speed high-pressure oil injection control method, which adopts a double-valve oil injection system of a control oil injector and an electric control unit pump, wherein the pressure establishment is rapid when the pressure establishment process is changed into a closed compression process by closing an electromagnetic valve of the oil injector, and the oil injector is started after the system pressure reaches the system target pressure by phase matching between an oil supply electromagnetic valve and the electromagnetic valve of the oil injector, so that the system can rapidly enter a high-pressure injection stage under a low-speed working condition;
the high-pressure oil pipe is adopted to replace a common rail cavity, so that the volume of the common rail cavity is reduced, the pressure of the electric control unit pump is synchronous with that of the electric control oil sprayer, and the response characteristic of the system is greatly improved; the high-pressure oil pipe is internally provided with instantaneous high pressure instead of continuous high pressure, so that the reliability of the system is improved; the oil supply characteristic can be quickly adjusted in each working cycle, and the dynamic acceleration characteristic of the vehicle is met; the electromagnetic valves used for generating high pressure and the electromagnetic valves used for oil injection are independently controlled by the electronic control unit, the working time sequence of the electromagnetic valves is adjusted according to the oil injection requirement, the starting pressure can be flexibly adjusted, the high pressure can be generated at a very low rotating speed, the starting characteristic of the liquid fuel engine can be greatly improved, and the emission in the starting process is reduced; the large fuel injection quantity can be realized in a short time under the working condition of high rotating speed and high load, thereby being more beneficial to the organization of the combustion process; one monomer pump supplies oil to multiple cylinders, so that the cost of the system can be greatly reduced;
the low-speed high-pressure oil supply characteristic is taken as a target, and the high-pressure injection under different rotating speeds and target pressure can be realized through the matching control of the working phases of the oil injection electromagnetic valves of the double-valve system.
Drawings
FIG. 1 is a schematic diagram of a dual valve fuel injection system of the present invention;
FIG. 2 is a graph of plunger lift curve and plunger movement speed for a constant velocity cam of the present invention;
FIG. 3 is a graph of system pump end pressure with a mechanical fuel injector and a fuel injector kept off, respectively;
FIG. 4 is a graph of injection pressure curves and corresponding needle valve displacement for different target pressures in accordance with the present invention;
FIG. 5 is a graph of injection pressure and corresponding needle displacement for achieving the same target pressure, different injection pulsewidths in accordance with the present invention;
FIG. 6 is a graph of the present invention for the valve control MAP for the nozzle side and pump side at various target injection pressures. The device comprises a 1-oil tank, a 2-low pressure oil way, a 3-oil supply cam, a 4-electric control unit pump, a 5-high pressure oil way, a 6-electric control oil sprayer, a 7-electronic control unit, a 40-pump end electromagnetic valve, a 41-plunger and a 60-oil spraying electromagnetic valve.
Detailed Description
The invention will now be described in detail by way of example with reference to the accompanying drawings.
Example 1:
the invention provides a double-valve oil injection system, which is shown in figure 1 and comprises an oil tank 1, a low-pressure oil way 2, an oil supply cam 3, an electric control unit pump 4, a high-pressure oil way 5, an electric control oil injector 6 and an electronic control unit 7. Wherein, the electric control unit pump 4 comprises a plunger 41 and a solenoid valve 40 for controlling the on-off of a low-pressure oil circuit. In addition, a solenoid valve 60 for controlling the injection state is also included in the electronically controlled fuel injector 6.
One end of the low-pressure oil way 2 is connected with the oil tank 1, and the other end is connected with the electric control unit pump 4. Typically, the low pressure fuel line 2 is in fluid communication with an electronically controlled unit pump 4, and low pressure fuel is delivered from the fuel tank 1 to the electronically controlled unit pump 4. When the solenoid valve 40 between the low-pressure oil passage 2 and the electric unit pump 4 is in a closed state, the communication is cut off.
When the electric control unit pump works, the oil supply cam 3 rotates at a certain speed under the drive of the driving system, and when the oil supply cam rotates to a certain angle, the bulge on the oil supply cam 3 contacts with the plunger 41 of the electric control unit pump 4, so that the plunger 41 is pushed to move upwards, and fuel in a plunger cavity is extruded. The oil supply cam 3 rotates continuously, so that the plunger 41 is driven by the cam 3 to reciprocate up and down continuously to perform linear motion, and further the electric control unit pump 4 is driven to work. When the plunger 41 descends, the plunger cavity is filled with oil; and when the vehicle goes upward, the fuel oil is extruded. When the plunger 41 moves upward and the solenoid valve 40 is closed, the high-pressure oil passage 5 is disconnected from the low-pressure oil passage 2, and the plunger 41 compresses the closed space to establish a high pressure in the high-pressure oil passage 5. The opening and closing of the solenoid valve 40 of the electronically controlled unit pump 4 is controlled by the electronic control unit 7.
The high-pressure fuel reaches the electric fuel injector 6 through the high-pressure fuel passage 5. As shown in fig. 1, the electronic control unit 7 may adjust the injection timing of the electronically controlled injector 6 by controlling the solenoid valve 60. The electronic control unit 7 transmits an opening instruction to the oil control injector 6 according to the ignition sequence of the engine and the requirement of the oil injection advance angle, so that flexible control of the oil injection advance angle and the oil injection pulse width is realized.
After the solenoid valve 60 of the electronically controlled fuel injector 6 is activated, fuel injection is started, and a fuel injection process is completed. After the oil injection is finished, the electromagnetic valve 60 of the electronic control oil injector 6 and the electromagnetic valve 40 in the electronic control unit pump 4 are controlled to be powered off successively by the electronic control unit 7, so that the high-pressure oil circuit 5, the electronic control unit pump 4 and the low-pressure oil circuit 2 are communicated, and the high-pressure fuel in the high-pressure oil circuit 5 is leaked back to the low-pressure oil circuit 2.
The working process of the double-valve oil injection system is as follows:
fuel oil is input into a plunger cavity of the electric control unit pump 4 through the low-pressure oil way 2;
when the oil supply cam 3 pushes the plunger 41 of the electric control unit pump 4 to move upwards and the oil injection electromagnetic valve 41 in the electric control unit pump 4 is closed, the communication between the low-pressure oil path 2 and the plunger cavity of the electric control unit pump 4 is cut off, the plunger 41 is pushed by the cam 3 so as to squeeze fuel oil to generate high pressure, and the high-pressure fuel oil is transmitted to the electric control oil injector 6 through the high-pressure oil pipe 5;
the oil injection electromagnetic valve 60 of the electric control oil injector 6 is opened at fixed time according to the combustion demand of the engine, and the oil injection process is completed once.
Example 2:
the embodiment also provides an oil injection method of the double-valve oil injection system.
FIG. 2 is a constant velocity cam plunger lift profile and plunger movement velocity profile for use in a fuel injection system wherein the cam working segment plunger 41 velocity is a constant value. FIG. 3 is a plot of pump end pressures for the pump end solenoid valve 40 at 5 CA, 8 CA, 11 CA, respectively, at a camshaft speed of 100r/min, during which the injector 6 is not open. Wherein, the rotating speed of the cam shaft is 100r/min and corresponds to the rotating speed of the engine is 200r/min. It can be seen that the control of the injector 6 to be closed can lead to the internal pressure of the system to be built up in advance, and the control of the injection solenoid valve 60 to be opened after the pressure in the high pressure oil pipe 5 reaches the target pressure can realize the high pressure oil supply characteristic at low rotation speed. Further fixing the injection timing, i.e. controlling the injection solenoid 60 of the injection nozzle 6 to open at regular time, the injection pressure profile and the injection solenoid 60 displacement are shown in fig. 4. It can be seen that when the injection time is the same, the pump end electromagnetic valve 40 is closed earlier, and the higher the injection pressure is, the peak pressures are 89.2MPa, 65MPa and 39.8MPa respectively.
FIG. 5 is a graph of injection pressure at 65MPa peak pressure for different injection pulsewidths. It can be seen that after the injection pulse width exceeds 1.2 ° CA, the injection pressure drops rapidly, which is insufficient to meet the high pressure injection requirement, and thus the injection pulse width is controlled to be within the range of 1.2 ° CA.
As is apparent from the above description, in order to achieve low-speed high-pressure injection, it is necessary to first close the pump-side solenoid valve 40 to establish pressure, the closing timing is determined according to the injection timing and the requirement of the target pressure, and the injection solenoid valve 60 is opened after the target pressure is reached. In order to realize the adjustment of the injection time, the establishment process of the pressure at the pump end needs to be controlled, namely the adjustment of the pressure establishment time is realized by controlling the closing time of the electromagnetic valve at the pump end, namely when the early oil injection is needed, the electromagnetic valve 40 at the pump end needs to be closed in advance, so that the pressure of the system is established earlier; when the oil injection is required to be delayed, the working phase of the pump end can be regulated to be late, so that the system pressure building process is delayed, the time for the system to reach the target pressure is delayed, and the flexible and adjustable oil injection advance angle is realized. FIG. 6 shows the control method, wherein the solenoid valves at the mouth end and the pump end control MAP under different target pressures obtained under the working condition of 100r/min, so as to guide the solenoid valve switching time of the electric control unit pump system under different target pressures.
In summary, the above embodiments are only preferred embodiments of the present invention, and are not intended to limit the scope of the present invention. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (3)
1. A low-rotation-speed high-pressure oil injection control method of a double-valve oil injection system of a diesel engine comprises the following steps:
the electric control unit pump is used for outputting fuel to the electric control fuel injector;
the low-pressure oil way is used for inputting fuel into the plunger cavity of the electric control unit pump;
the oil supply cam is used for pushing the plunger of the electric control unit pump to move;
the electric control fuel injector is used for injecting fuel;
the high-pressure oil pipe is connected with the electric control unit pump and the electric control oil injector and is used for conveying the fuel oil output by the electric control unit pump to the electric control oil injector;
a pump end electromagnetic valve (40) which is arranged in the electric control unit pump and is used for controlling the on-off of the low-pressure oil way;
the oil injection electromagnetic valve (60) is arranged in the electric control oil injector and is used for controlling the electric control oil injector to spray oil;
and the electronic control unit is used for controlling the opening and closing of the pump end electromagnetic valve (40) and the oil injection electromagnetic valve (60).
The control method is characterized by comprising the following steps:
step one, initially, opening a pump end electromagnetic valve (40) and closing an oil injection electromagnetic valve (60);
step two, after starting, controlling the oil supply cam to rotate according to a set rotating speed; when the camshaft of the oil supply cam (3) rotates to a certain angle position, the electromagnetic valve (40) at the pump end is closed, the pressure in the cavity of the plunger pump is monitored, and when the set target pressure is reached, the rotating angle of the camshaft at the moment is recorded, namely the opening moment of the electromagnetic valve (60) for oil injection; under the same target pressure, continuously changing the closing time of a solenoid valve (40) at the pump end, and recording the cam shaft angle when the pressure in the cavity of the plunger pump reaches the target pressure; thus, the corresponding relation between the cam shaft angle when the pump end electromagnetic valve (40) is closed and the cam shaft angle when the oil injection electromagnetic valve (60) is opened under a target pressure is obtained;
and the like, obtaining the corresponding relation between the cam shaft angle when the pump end electromagnetic valve (40) is closed and the cam shaft angle when the oil injection electromagnetic valve (60) is opened under different target pressures;
and thirdly, when oil injection is controlled, finding out the corresponding relation under the target pressure according to the set target pressure, and then finding out the cam shaft angle when the pump end electromagnetic valve (40) is closed in the corresponding relation according to the oil injection time, namely the cam shaft angle when the oil injection electromagnetic valve (60) is opened, and controlling the closing of the pump end electromagnetic valve (40) and the opening of the oil injection electromagnetic valve (60) according to the two angles.
2. A method of controlling low rotational speed high pressure injection of a dual valve injection system for a diesel engine as claimed in claim 1 wherein the injection solenoid valve (60) is controlled to open while controlling its injection pulse width to be below a set value.
3. A low rotational speed high pressure fuel injection control method of a dual valve fuel injection system of a diesel engine as claimed in claim 2, characterized in that the fuel injection solenoid valve (60) is controlled to inject fuel with different fuel injection pulse widths, and a maximum fuel injection pulse width satisfying the fuel injection pressure is determined, and the fuel injection pulse width of the fuel injection solenoid valve (60) is controlled to be smaller than the maximum fuel injection pulse width.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210719363.5A CN115217662B (en) | 2022-06-23 | 2022-06-23 | Double-valve oil injection system of diesel engine and low-rotation-speed high-pressure oil injection control method |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210719363.5A CN115217662B (en) | 2022-06-23 | 2022-06-23 | Double-valve oil injection system of diesel engine and low-rotation-speed high-pressure oil injection control method |
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| Publication Number | Publication Date |
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| CN115217662A CN115217662A (en) | 2022-10-21 |
| CN115217662B true CN115217662B (en) | 2023-12-05 |
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| CN202210719363.5A Active CN115217662B (en) | 2022-06-23 | 2022-06-23 | Double-valve oil injection system of diesel engine and low-rotation-speed high-pressure oil injection control method |
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Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100756635B1 (en) * | 2006-08-08 | 2007-09-07 | 현대자동차주식회사 | Two-valves electronic unit injector device having function of fail safety |
| CN101806266A (en) * | 2010-03-04 | 2010-08-18 | 哈尔滨工程大学 | Double-valve fuel injecting device with electric-control monoblock pump and electric-control fuel injector |
| CN109236526A (en) * | 2018-07-26 | 2019-01-18 | 哈尔滨工程大学 | Pressure accumulation type bivalve electric-controlled fuel injector |
| CN109252999A (en) * | 2018-07-26 | 2019-01-22 | 哈尔滨工程大学 | Piezoelectricity-electromagnetism bivalve electric-controlled fuel injector |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102425516B (en) * | 2011-11-03 | 2014-04-16 | 北京理工大学 | Multi-valve oil spraying system and multi-valve oil spraying method |
-
2022
- 2022-06-23 CN CN202210719363.5A patent/CN115217662B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100756635B1 (en) * | 2006-08-08 | 2007-09-07 | 현대자동차주식회사 | Two-valves electronic unit injector device having function of fail safety |
| CN101806266A (en) * | 2010-03-04 | 2010-08-18 | 哈尔滨工程大学 | Double-valve fuel injecting device with electric-control monoblock pump and electric-control fuel injector |
| CN109236526A (en) * | 2018-07-26 | 2019-01-18 | 哈尔滨工程大学 | Pressure accumulation type bivalve electric-controlled fuel injector |
| CN109252999A (en) * | 2018-07-26 | 2019-01-22 | 哈尔滨工程大学 | Piezoelectricity-electromagnetism bivalve electric-controlled fuel injector |
Non-Patent Citations (1)
| Title |
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| 高压双电磁阀燃油系统特性分析;仇滔;刘兴华;刘福水;胡建村;;农业机械学报(第11期);第7-9页 * |
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| CN115217662A (en) | 2022-10-21 |
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