CN116753093A - EGR control system of natural gas engine - Google Patents

EGR control system of natural gas engine Download PDF

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Publication number
CN116753093A
CN116753093A CN202310930796.XA CN202310930796A CN116753093A CN 116753093 A CN116753093 A CN 116753093A CN 202310930796 A CN202310930796 A CN 202310930796A CN 116753093 A CN116753093 A CN 116753093A
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CN
China
Prior art keywords
engine
egr
exhaust gas
pipeline
branch
Prior art date
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Pending
Application number
CN202310930796.XA
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Chinese (zh)
Inventor
赵艳婷
刘贝
罗亚妮
米娇
刘子豪
胡崴
陈丽丽
魏国龙
郑懿铭
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Dongfeng Commercial Vehicle Co Ltd
Original Assignee
Dongfeng Commercial Vehicle Co Ltd
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Application filed by Dongfeng Commercial Vehicle Co Ltd filed Critical Dongfeng Commercial Vehicle Co Ltd
Priority to CN202310930796.XA priority Critical patent/CN116753093A/en
Publication of CN116753093A publication Critical patent/CN116753093A/en
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/02—EGR systems specially adapted for supercharged engines
    • F02M26/04—EGR systems specially adapted for supercharged engines with a single turbocharger
    • F02M26/06—Low pressure loops, i.e. wherein recirculated exhaust gas is taken out from the exhaust downstream of the turbocharger turbine and reintroduced into the intake system upstream of the compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B43/00—Engines characterised by operating on gaseous fuels; Plants including such engines
    • F02B43/10—Engines or plants characterised by use of other specific gases, e.g. acetylene, oxyhydrogen
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D21/00—Controlling engines characterised by their being supplied with non-airborne oxygen or other non-fuel gas
    • F02D21/06—Controlling engines characterised by their being supplied with non-airborne oxygen or other non-fuel gas peculiar to engines having other non-fuel gas added to combustion air
    • F02D21/08—Controlling engines characterised by their being supplied with non-airborne oxygen or other non-fuel gas peculiar to engines having other non-fuel gas added to combustion air the other gas being the exhaust gas of engine
    • 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
    • F02D41/0002—Controlling intake air
    • F02D41/0007—Controlling intake air for control of turbo-charged or super-charged engines
    • 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
    • F02D41/0025—Controlling engines characterised by use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
    • F02D41/0047—Controlling exhaust gas recirculation [EGR]
    • F02D41/0077—Control of the EGR valve or actuator, e.g. duty cycle, closed loop control of position
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D9/00—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits
    • F02D9/02—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits concerning induction conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/02—EGR systems specially adapted for supercharged engines
    • F02M26/04—EGR systems specially adapted for supercharged engines with a single turbocharger
    • F02M26/07—Mixed pressure loops, i.e. wherein recirculated exhaust gas is either taken out upstream of the turbine and reintroduced upstream of the compressor, or is taken out downstream of the turbine and reintroduced downstream of the compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/38—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with two or more EGR valves disposed in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/42—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories having two or more EGR passages; EGR systems specially adapted for engines having two or more cylinders
    • F02M26/44—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories having two or more EGR passages; EGR systems specially adapted for engines having two or more cylinders in which a main EGR passage is branched into multiple passages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/52—Systems for actuating EGR valves
    • F02M26/64—Systems for actuating EGR valves the EGR valve being operated together with an intake air throttle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B43/00—Engines characterised by operating on gaseous fuels; Plants including such engines
    • F02B43/10—Engines or plants characterised by use of other specific gases, e.g. acetylene, oxyhydrogen
    • F02B2043/103—Natural gas, e.g. methane or LNG used as a fuel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D9/00—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits
    • F02D9/02—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits concerning induction conduits
    • F02D2009/0201—Arrangements; Control features; Details thereof
    • F02D2009/0276—Throttle and EGR-valve operated together
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D21/00—Controlling engines characterised by their being supplied with non-airborne oxygen or other non-fuel gas
    • F02D21/06—Controlling engines characterised by their being supplied with non-airborne oxygen or other non-fuel gas peculiar to engines having other non-fuel gas added to combustion air
    • F02D21/08—Controlling engines characterised by their being supplied with non-airborne oxygen or other non-fuel gas peculiar to engines having other non-fuel gas added to combustion air the other gas being the exhaust gas of engine
    • F02D2021/083—Controlling engines characterised by their being supplied with non-airborne oxygen or other non-fuel gas peculiar to engines having other non-fuel gas added to combustion air the other gas being the exhaust gas of engine controlling exhaust gas recirculation electronically
    • 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
    • F02D41/0002—Controlling intake air
    • F02D2041/0017—Controlling intake air by simultaneous control of throttle and exhaust gas recirculation

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Exhaust-Gas Circulating Devices (AREA)

Abstract

The application relates to a natural gas engine EGR control system, comprising: an engine air inlet pipeline, an EGR mixing pipeline, an engine exhaust pipeline and an exhaust gas recovery pipeline, wherein a throttle valve and an engine body which are sequentially arranged along the gas flow direction are arranged on the engine air inlet pipeline; the EGR mixing pipeline is communicated with the engine air inlet pipeline and is used for mixing air and exhaust gas so as to be sent to the engine air inlet pipeline; a turbine is arranged on the exhaust pipe of the engine; the exhaust gas recovery pipeline is connected with the EGR mixing pipeline and the engine exhaust pipeline, and is provided with a high-pressure EGR valve and a low-pressure EGR valve; and, when the high pressure EGR valve is opened, the exhaust gas recovery line sends the exhaust gas before being treated by the turbine to the EGR mixing line; when the low-pressure EGR valve is opened, the exhaust gas recovery line sends the exhaust gas treated by the turbine to the EGR mixing line. According to the application, the throttle valve controls fresh air inflow, the high-pressure EGR valve and the low-pressure EGR valve can inhibit knocking and detonation pressure of the engine body, and the economy of the engine body is improved.

Description

EGR control system of natural gas engine
Technical Field
The application relates to the field of natural gas engines, in particular to an EGR control system of a natural gas engine.
Background
The principle of EGR (exhaust gas recirculation) is to reintroduce cooled recirculated exhaust gas into the combustion chamber with little impact on the heat load while reducing the effective air-fuel ratio. The main purpose of the application is to reduce the NOx emission of a diesel engine through combustion optimization, reduce the detonation pressure and detonation of natural gas, and realize the aim of reducing the concentration of oxygen in the inlet gas by introducing the exhaust gas from an exhaust pipe into an inlet pipe. The EGR system of the prior art is controlled separately from the other components of the air system, in particular the throttle valve. The natural gas engine is quantity-regulated, namely, the quantity of mixed gas (such as mixed gas of natural gas and air) is controlled through a throttle valve to change the load of the engine, the load of the engine is directly controlled by the throttle valve, namely, the opening degree of the throttle valve is smaller during the small-load working condition of the engine so as to control the fresh air inflow, the smaller air inflow is matched with the smaller natural gas supply quantity to realize the power torque of the small-load working condition of the engine, and meanwhile, the knocking of the natural gas engine is controlled through an EGR system. However, in the above-described technique, since the throttle opening is small, the intake throttle loss is large, which is disadvantageous to the economy of the engine.
Disclosure of Invention
The embodiment of the application provides an EGR control system of a natural gas engine, which aims to solve the problems of small throttle opening and large intake throttling loss in the prior art when the engine is under a small-load working condition, and is unfavorable for the economy of the engine.
In order to achieve the above purpose, the present application provides the following technical solutions: an natural gas engine EGR control system comprising: the engine exhaust system comprises an engine air inlet pipeline, an EGR (exhaust gas recirculation) mixing pipeline, an engine exhaust pipeline and an exhaust gas recovery pipeline, wherein a throttle valve and an engine body which are sequentially arranged along the gas flow direction are arranged on the engine air inlet pipeline; the EGR mixing pipeline is communicated with the engine air inlet pipeline and is used for mixing air and exhaust gas so as to be sent to the engine air inlet pipeline; a turbine is arranged on the engine exhaust pipe; the exhaust gas recovery pipeline is connected with the EGR mixing pipeline and the engine exhaust pipeline, and a high-pressure EGR valve and a low-pressure EGR valve are arranged on the exhaust gas recovery pipeline; and, when the high pressure EGR valve is open, the exhaust gas recovery line sends exhaust gas before being treated by the turbine to the EGR mixing line; when the low-pressure EGR valve is opened, the exhaust gas recovery line sends the exhaust gas treated by the turbine to the EGR mixing line.
In some embodiments, the exhaust pipe of the engine is further provided with an after-treatment system, the turbine and the after-treatment system are sequentially arranged along the gas flow direction, and when the low-pressure EGR valve is opened, the exhaust gas recovery pipeline sends the exhaust gas treated by the after-treatment system to the EGR mixing pipeline.
In some embodiments, the EGR control system further includes: and the exhaust gas recovery pipeline is communicated with the EGR mixing pipeline through the intercooler assembly, and the EGR mixing pipeline is communicated with the engine air inlet pipeline through the intercooler assembly.
In some embodiments, the intercooler assembly includes an air-to-air intercooler, and the exhaust gas recovery line and the EGR mixing line both pass through the air-to-air intercooler.
In some embodiments, the exhaust gas recovery pipeline is further provided with an EGR cooler; when the high-pressure EGR valve is opened, the exhaust gas recovery pipeline sends the exhaust gas before being treated by the turbine to the EGR mixing pipeline after being treated by the EGR cooler; when the low-pressure EGR valve is opened, the exhaust gas recovery pipeline sends the exhaust gas treated by the turbine to the EGR mixing pipeline after being treated by the EGR cooler.
In some embodiments, the engine exhaust pipeline comprises a first branch and a second branch, the first branch is connected with the engine body and the turbine, and the second branch is connected with the engine body and the turbine, so that exhaust gas discharged by the engine body is divided into two paths, and the two paths are respectively sent to the turbine for treatment through the first branch and the second branch.
In some embodiments, the high-pressure EGR valve includes a first high-pressure EGR valve and a second high-pressure EGR valve, a third branch where the first high-pressure EGR valve is located is connected to the first branch and the EGR cooler, and a fourth branch where the second high-pressure EGR valve is located is connected to the second branch and the EGR cooler; when the first high-pressure EGR valve is opened, the exhaust gas discharged by the engine body is sent to an EGR cooler for treatment along a first branch and a third branch; when the second high-pressure EGR valve is closed, exhaust gas discharged from the engine body is sent to the EGR cooler for treatment along the second branch and the fourth branch.
In some embodiments, the waste gas recovery pipeline is further provided with a dehydrator.
In some embodiments, the EGR mixing pipe is provided with an EGR mixer and a compressor, which are arranged in sequence along the gas flow direction, the EGR mixer is used for mixing air and exhaust gas to be sent to the compressor, and the compressor is used for compressing air and exhaust gas to be sent to the engine air inlet pipe.
In some embodiments, the engine air inlet pipeline is further provided with a natural gas injector, and the throttle valve, the natural gas injector and the engine body are sequentially arranged along the gas flow direction.
The technical scheme provided by the application has the beneficial effects that:
the embodiment of the application provides a natural gas engine EGR control system, which can control fresh air inflow (namely, realize that an engine body runs at low load) by utilizing a throttle valve, is provided with a high-pressure EGR valve and a low-pressure EGR valve which are matched with each other, and supplements the EGR flow through the low-pressure EGR valve, so that a large amount of air flows to the high-pressure EGR valve when the opening degree of the high-pressure EGR valve is overlarge due to the fact that the high-pressure EGR valve is singly used is avoided, the influence of the arranged waste gas recovery pipeline on turbine acting on the basis that enough EGR flow flows to an EGR mixing pipeline is met, the knocking and explosion pressure of the engine body can be restrained, the throttle loss is reduced, and the economy of the engine body can be improved.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present application, the drawings required for the description of the embodiments will be briefly described below, and it is apparent that the drawings in the following description are only some embodiments of the present application, and other drawings may be obtained according to these drawings without inventive effort for a person skilled in the art.
FIG. 1 is a schematic system diagram of a single-gas-take high-pressure EGR valve provided by an embodiment of the present application;
FIG. 2 is a schematic diagram of a system of a dual-bleed high pressure EGR valve provided in an embodiment of the present application;
FIG. 3 is a pressure wave diagram of a two-way EGR take-off provided by an embodiment of the present application;
fig. 4 is a schematic diagram of a control method according to an embodiment of the present application.
In the figure: 1. an EGR mixing line; 10. an EGR mixer; 11. a compressor;
2. an engine air intake line; 20. a throttle valve; 21. a natural gas injector; 22. an engine body;
3. an engine exhaust line; 30. a turbine; 31. a post-processing system; 32. a first branch; 33. a second branch;
4. an exhaust gas recovery line; 40. a high pressure EGR valve; 400. a first high pressure EGR valve; 401. a second high pressure EGR valve; 41. a low pressure EGR valve; 42. an EGR cooler; 43. a water remover;
5. an air line;
6. an air-air intercooler.
Detailed Description
For the purpose of making the objects, technical solutions and advantages of the embodiments of the present application more apparent, the technical solutions of the embodiments of the present application will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present application, and it is apparent that the described embodiments are some embodiments of the present application, but not all embodiments of the present application. All other embodiments, which can be made by those skilled in the art based on the embodiments of the application without making any inventive effort, are intended to be within the scope of the application.
Referring to fig. 1 to 4, the embodiment of the application provides an EGR control system for a natural gas engine, which can solve the problems of smaller throttle opening and larger intake throttling loss in the small-load working condition of the engine in the related art and is unfavorable for the economy of the engine.
The principle of EGR (exhaust gas recirculation) is to reintroduce cooled recirculated exhaust gas into the combustion chamber with little impact on the heat load while reducing the effective air-fuel ratio. The main purpose of its application is to reduce diesel NOx emissions by combustion optimisation by introducing exhaust gases from the engine exhaust line into the engine intake line to reduce the intake oxygen concentration. Among the main reasons for EGR to reduce NOx emissions are:
1. thermal effect: CO in exhaust gas 2 H and H 2 O can improve the specific heat capacity of the charge in the cylinder of the engine, thereby reducing the combustion temperature;
2. dilution effect: exhaust gas introduction reduces in-cylinder O of engine 2 Concentration, decrease in oxide concentration, decrease in activity, results in decrease in combustion reaction rate;
3. chemical effect: CO in exhaust gas 2 And H 2 O enters the cylinder of the engine and then undergoes dissociation reaction, so that the combustion process and NOx generation are changed, and particularly the endothermic decomposition reaction of water vapor directly reduces combustionFlame temperature.
The prior art EGR system is controlled separately from the other components of the air system, particularly the throttle 20. The natural gas engine is quantity-regulated, the load of the engine is directly controlled by the throttle valve 20, namely, the opening of the throttle valve 20 is smaller under the working condition of small load of the engine so as to control the fresh air inflow, and the smaller air inflow is matched with the smaller natural gas supply quantity to realize the power torque of the working condition of small load of the engine. And meanwhile, the knocking of the natural gas engine is controlled by matching with an EGR system. However, in the above technique, since the throttle valve 20 is small in opening, the intake throttle loss is large, which is disadvantageous in the economy of the engine.
The method aims to solve the problems that in the related art, the opening of the throttle valve 20 is smaller, the air inlet throttling loss is larger and the economy of the engine is not facilitated under the small-load working condition of the engine. The embodiment of the application provides a natural gas engine EGR control system, which comprises the following components: an engine air inlet pipeline 2, an EGR mixing pipeline 1, an engine exhaust pipeline 3 and an exhaust gas recovery pipeline 4, wherein a throttle valve 20 and an engine body 22 which are sequentially arranged along the gas flow direction are arranged on the engine air inlet pipeline 2; the EGR mixing pipe 1 communicates with the engine intake pipe 2 and is used to mix air with exhaust gas to send to the engine intake pipe 2; a turbine 30 is arranged on the engine exhaust pipeline 3; the exhaust gas recovery pipeline 4 is connected with the EGR mixing pipeline 1 and the engine exhaust pipeline 3, and a high-pressure EGR valve 40 and a low-pressure EGR valve 41 are arranged on the exhaust gas recovery pipeline 4; and, when the high-pressure EGR valve 40 is opened, the exhaust gas recovery pipe 4 sends the exhaust gas before being treated by the turbine 30 to the EGR mixing pipe 1; when the low-pressure EGR valve 41 is opened, the exhaust gas recovery pipe 4 sends the exhaust gas treated by the turbine 30 to the EGR mixing pipe 1.
The gas flow direction as used in the present application means a direction in which gas flows from the exhaust port of the engine block 22 to the intake port of the engine block 22.
In the application, the throttle valve 20 is utilized to realize the control of fresh air inflow (namely, the operation of the engine body 22 at low load) and the high-pressure EGR valve 40 and the low-pressure EGR valve 41 are arranged to be matched with each other, the EGR flow is supplemented by the low-pressure EGR valve 41, so that when the opening of the high-pressure EGR valve 40 is overlarge due to the independent use of the high-pressure EGR valve 40, a large amount of gas flows to the high-pressure EGR valve 40, the influence of the arranged waste gas recovery pipeline 4 on the work of the turbine 30 is reduced on the basis of meeting the sufficient EGR flow to the EGR mixing pipeline 1, the knocking and explosion pressure of the engine body 22 can be restrained, the throttling loss is reduced, and the economy of the engine body 22 can be improved.
The engine air inlet pipeline 2 is also provided with a natural gas injector 21, and the throttle valve 20, the natural gas injector 21 and the engine body 22 are sequentially arranged along the gas flow direction, so that EGR gas enters the EGR mixing pipeline 1 to be mixed with fresh air and then enters the engine air inlet pipeline 2, and the opening degree of the throttle valve 20 is used for controlling the load of the engine body 22; after passing through the throttle valve 20, the mixed gas is mixed with the natural gas sprayed by the natural gas sprayer 21, and finally enters the engine body 22 to do work through combustion; part of the exhaust gas generated by the combustion work of the engine body 22 is pushed by the turbine 30 to be discharged after acting through the engine exhaust pipeline 3, and the other part of the exhaust gas is recycled into the EGR mixing pipeline 1 through the exhaust gas recycling pipeline 4.
Wherein, since the turbine 30 is provided on the engine exhaust line 3, the turbine 30 divides the engine exhaust line 3 into a front section and a rear section: the waste gas generated by the combustion and working of the engine body 22 passes through the front section, pushes the turbine 30 to do work and then is discharged from the rear section;
the exhaust gas recovery pipeline 4 comprises a high-pressure branch and a low-pressure branch, a high-pressure EGR valve 40 is arranged on the high-pressure branch, a low-pressure EGR valve 41 is arranged on the low-pressure branch, wherein the high-pressure branch is connected with the front section and the EGR mixing pipeline 1, and the low-pressure branch is connected with the rear section and the EGR mixing pipeline 1;
if only the high-pressure EGR valve 40 is provided, when the opening degree of the high-pressure EGR valve 40 is small, there is a risk that the flow rate of the exhaust gas sent from the exhaust gas recovery pipe 4 to the EGR mixing pipe 1 is insufficient, and it is difficult to suppress knocking and knocking pressure of the engine body 22; when the opening of the high-pressure EGR valve 40 is large, the flow rate of exhaust gas pushing the turbine 30 to perform work decreases, which affects the work performed by the turbine 30 and, at that time, affects the fuel consumption of the engine body 22. After the low-pressure branch is provided to communicate with the rear stage, when the low-pressure EGR valve 41 is opened, the exhaust gas treated by the turbine 30 can be sent to the EGR mixing pipe 1, and at this time, it is not necessary to adjust the opening degree of the high-pressure EGR valve 40 too much, and it is possible to satisfy a sufficient EGR flow rate (exhaust gas flow rate) to flow to the EGR mixing pipe 1.
On the basis of the above embodiment, in this embodiment, the engine exhaust line 3 is further provided with an aftertreatment system 31, the turbine 30 and the aftertreatment system 31 are sequentially arranged along the gas flow direction, and when the low-pressure EGR valve 41 is opened, the exhaust gas recovery line 4 sends the exhaust gas treated by the aftertreatment system 31 to the EGR mixing line 1.
In this embodiment, the turbine 30 and the aftertreatment system 31 are disposed on the engine air intake pipe 2, so that the exhaust gas enters the aftertreatment system 31 for treatment after passing through the turbine 30 to reduce the content of corrosive substances in the exhaust gas, at this time, the turbine 30 and the aftertreatment system 31 divide the engine air intake pipe 2 into a front section, a middle section and a rear section, the high-pressure branch is connected with the front section and the EGR mixing pipe 1, the low-pressure branch is connected with the rear section and the EGR mixing pipe 1, and at this time, the exhaust gas passing through the rear section is treated by the aftertreatment system 31.
The EGR mixing pipe 1 is provided with an EGR mixer 10 and a compressor 11 which are arranged in sequence along the gas flow direction, the EGR mixer 10 is used for mixing air and exhaust gas to be sent to the compressor 11, and the compressor 11 is used for compressing air and exhaust gas to be sent to the engine air inlet pipe 2.
The EGR mixer 10 includes two air inlets, one of which is connected with an air pipe 5 to inject fresh air into the EGR mixer 10, and the other of which is connected with an exhaust gas recovery pipe 4 to inject exhaust gas into the EGR mixer 10, the fresh air and the exhaust gas are uniformly mixed through the EGR mixer 10, and the mixture is sent to a compressor 11 to be compressed and then enter a cylinder of an engine body 22 to be added with a combustion process, so as to increase the exhaust gas charge, improve the air density, increase the air intake quantity, and reduce the knocking and the detonation pressure.
On the basis of the above embodiment, in this implementation, the EGR control system further includes: the intercooler assembly, exhaust gas recovery pipeline 4 communicates with EGR hybrid line 1 through the intercooler assembly, EGR hybrid line 1 communicates with engine air intake line 2 through the intercooler assembly.
The energy of the exhaust gas discharged from the engine body 22 is used for driving the air compressor 11 to pump air to the air inlet pipe of the engine body 22, so that the density and the pressure of the air inlet are improved, and the fuel is combusted more fully. Then, the temperature of the pressurized gas is very high due to the influence of the high temperature of the compressor 11, and the pressurizing effect is greatly influenced; therefore, in order to further improve the supercharging efficiency, the supercharging technology is perfected, and the gas after being supercharged by the compressor 11 is sent to the intercooler assembly for cooling, so that the density of the inlet air is improved.
In this embodiment, the gas is cooled by adopting a multi-stage cooling mode, specifically, the intercooler assembly includes an air-air intercooler 6, and the exhaust gas recovery pipeline 4 and the EGR mixing pipeline 1 both pass through the air-air intercooler 6:
namely, the exhaust gas entering the exhaust gas recovery pipeline 4 passes through the air cooler 6 and then enters the EGR mixer 10 for mixing treatment, and then the mixed gas passes through the compressor 11, is cooled again by the air cooler 6 and then is sent to the engine body 22. By providing an air-to-air intercooler 6 for cooling the exhaust gases entering the EGR mixing line 1 and the exhaust gases entering the engine intake line 2, the system arrangement is made more compact and the volume of the system is reduced.
On the basis of the above embodiment, in this embodiment, in order to further reduce the temperature of the exhaust gas entering the EGR mixing pipe 1, the exhaust gas recovery pipe 4 is further provided with an EGR cooler 42; when the high-pressure EGR valve 40 is opened, the exhaust gas recovery pipe 4 sends the exhaust gas before being treated by the turbine 30 to the EGR mixing pipe 1 after being treated by the EGR cooler 42; when the low-pressure EGR valve 41 is opened, the exhaust gas recovery pipe 4 sends the exhaust gas treated by the turbine 30 to the EGR mixing pipe 1 after being treated by the EGR cooler 42.
Specifically, the high-pressure branch and the low-pressure branch communicate with the EGR cooler 42: when the high-pressure EGR valve 40 is opened, the high-pressure branch takes gas before (in front of) the turbine 30, and the exhaust gas enters the EGR cooler 42 through the high-pressure branch for cooling, then enters the air cooler 6 for cooling again, and finally enters the EGR mixer 10; when the low-pressure EGR valve 41 is opened, the low-pressure branch is taken after (in the latter stage of) the aftertreatment system 31, and the exhaust gas passes through the low-pressure branch to be cooled in the EGR cooler 42, then to be cooled again in the air cooler 6, and finally to be introduced into the EGR mixer 10. Further, the exhaust gas passing through the low-pressure branch and the exhaust gas passing through the high-pressure branch are mixed after passing through the EGR cooler 42, and are introduced into the air cooler 6 together.
The EGR rate (exhaust gas rate), that is, the flow rate of exhaust gas, is controlled by the opening degree of the high-pressure EGR valve 40 and the low-pressure EGR valve 41; the exhaust gas is primarily cooled by the EGR cooler 42, and in this embodiment, at a predetermined point in the engine block 22 (the condition of maximum power that the engine block 22 can achieve), the gas temperature at the outlet of the EGR cooler 42 is approximately 130 ℃, and after the exhaust gas is secondarily cooled by the air cooler 6, the gas temperature at the outlet of the air cooler 6 is approximately 45 ℃.
In this embodiment, as shown in fig. 1, the high-pressure branch gas extraction is a single gas extraction, and the EGR cooler 42 is an integrated two-channel cooler (one channel is connected to the high-pressure branch, and one channel is connected to the low-pressure branch).
In other embodiments, as shown in FIG. 2, the high pressure branch is taken as a dual take, the high pressure branch includes a third branch and a fourth branch, and the EGR cooler 42 is an integrated three-channel cooler (one channel connected to the third branch, one channel connected to the fourth branch, and one channel connected to the low pressure branch) to maximize pulse energy retention.
Specifically, the engine exhaust pipeline 3 includes a first branch 32 and a second branch 33, the first branch 32 is connected with the engine intake pipeline 2 and the turbine 30, and the second branch 33 is connected with the engine intake pipeline 2 and the turbine 30, so that the exhaust gas discharged from the engine intake pipeline 2 is divided into two paths, and is sent to the turbine 30 for treatment through the first branch 32 and the second branch 33 respectively.
The high-pressure EGR valve 40 is provided to comprise a first high-pressure EGR valve 400 and a second high-pressure EGR valve 401, wherein a third branch where the first high-pressure EGR valve 400 is positioned is connected with the first branch 32 and the EGR cooler 42, and a fourth branch where the second high-pressure EGR valve 401 is positioned is connected with the second branch 33 and the EGR cooler 42; when the first high-pressure EGR valve 400 is opened, the exhaust gas discharged from the engine intake line 2 is sent to the EGR cooler 42 along the first branch 32 and the third branch for treatment; when the second high-pressure EGR valve 401 is opened, the exhaust gas discharged from the engine intake line 2 is sent to the EGR cooler 42 along the second branch 33 and the fourth branch for treatment.
In this embodiment, the engine body 22 is a six-cylinder engine, in fig. 2, the engine body 22 is respectively 1 cylinder, 2 cylinder, 3 cylinder, 4 cylinder, 5 cylinder, and 6 cylinder from left to right, the first branch 32 takes air from 1 cylinder, 2 cylinder, and 3 cylinder of the engine body 22, and the second branch 33 takes air from 4 cylinder, 5 cylinder, and 6 cylinder of the engine body 22. For the reason of the firing order of the engine body 22, for example, a six-cylinder engine, the firing order thereof is 1 cylinder, 5 cylinders, 3 cylinders, 6 cylinders, 2 cylinders, and 4 cylinders, and as shown in fig. 3, the exhaust pulse pressure fluctuation shape has 6 peaks corresponding to each of the firing cylinders.
If a double gas taking mode is adopted, the wave crest charge can be kept all the time, the wave crest pressure is higher, more gas can be brought, and a higher EGR rate (exhaust gas rate) is obtained. The gas of the third branch and the fourth branch can keep higher pressure unaffected all the time (the gas taking of the left three cylinders 1, 2 and 3 is not affected by the gas taking of the right three cylinders 4, 5 and 6; the gas taking of the right three cylinders 4, 5 and 6 is not affected by the gas taking of the left three cylinders 1, 2 and 3), for example: the left three cylinders can always keep the maximum pressure of 5.5bar, and the right three cylinders can keep the maximum pressure of 5.5bar;
in contrast, if a single air taking mode is adopted, the wave crests and the wave troughs are mutually overlapped and influenced, the wave crests are pulled down to fill the wave troughs, and then waste gas is reduced. Specifically, if the pressure of the left three cylinders and the right three cylinders are affected by each other by taking gas from a single path, the maximum pressure of the gas in the third branch and the fourth branch is less than 5.5bar, the pressure range is 4-4.5 bar after the pressure of the gas in the third branch and the fourth branch is averaged, and compared with the maximum pressure of 5.5bar, the pressure at the moment is less than 1-1.5 bar, and the gas driving capability is less than 1-1.5 bar.
Since the third and fourth branch gas take-off capacities are related to the pressure difference (i.e. the pressure at the inlet of the third and fourth branch is greater than the pressure at the inlet of the EGR mixing pipe 1): when the pressure difference exists, the third branch and the fourth branch can take gas, and the gas of the exhaust gas recovery pipeline 4 can flow into the EGR mixer 10; when there is no pressure difference, the third branch and the fourth branch cannot take out gas, and the gas in the exhaust gas recovery line 4 does not flow into the EGR mixer 10. Therefore, more exhaust gas can be obtained by the double gas taking mode.
In this embodiment, a water trap 43 is further provided on the exhaust gas recovery line 4. The exhaust gas from the exhaust gas recovery line 4 passes through the air cooler 6, enters the water trap 43 for water removal, and then enters the EGR mixer 10. The exhaust gas is dehydrated through the dehydrator 43, so that the downstream blades of the compressor 11 can be protected from being corroded by water vapor; at the same time due to natural gas CH 4 Component and oxygen O in air 2 The extremely easily produced water of the components enters the cylinders of the engine block 22, particularly, the first cylinder through which the gas passes, and this causes the intake of each cylinder to be uneven, so that the difference in the exhaust temperature of the outlets of each cylinder of the engine block 22 before the turbine 30 is large, the reliability is affected, and the knocking and economy of the engine block 22 are affected, and therefore, the above-mentioned problems can be ameliorated by adding the water trap 43.
The comparison of the high load condition and the low load condition in the prior art with the high load condition and the low load condition of the application is shown in the following table:
in the present application, the opening degree of the throttle valve 20 is slightly increased, and at the same time, the opening degrees of the EGR valves (the high-pressure EGR valve 40 and the low-pressure EGR valve 41) are increased, and the load of the intake air amount is reduced by the cooperation of the throttle valve 20 and the EGR valve: the EGR valve controls EGR flow, the throttle valve 20 controls air inflow, and the EGR valve and the throttle valve 20 are matched together to realize the small-load working condition to reduce throttling loss and improve the economy of the engine body 22. The specific values of the opening amounts of the throttle valve 20 and the EGR valve are determined by calibration.
Control of the high-pressure EGR valve 40 and the low-pressure EGR valve 41: the opening of the high pressure EGR valve 40 needs to be calibrated to achieve optimal economy. There are various combinations to achieve the same EGR rate during calibration: for example, the EGR flow rate of 80% + of the opening degree of the high-pressure EGR valve 40 and 20% = 200kg/h of the opening degree of the low-pressure EGR valve 41; EGR flow rate of 40% + opening degree of the high-pressure EGR valve 40 and 50% =200 kg/h opening degree of the low-pressure EGR valve 41. Although both opening degree adjustment modes can achieve the same EGR flow rate, both can control knocking of the engine body 22 within the limit value range. However, since the pumping loss of the engine body 22 is reduced (benefit: pumping loss can be represented by the pressure value before the turbine 30, when the pressure is high, pumping loss is large, and when pumping loss is large, the work of the engine body 22 is consumed on the exhaust gas, so that the effective work of the engine body 22 is reduced, the oil consumption is increased), and at the same time, the efficiency of the turbine 30 is reduced (disadvantage) due to the reduction of the exhaust gas flowing to the turbine 30, an optimal combination of the opening of the high-pressure EGR valve 40 and the opening of the low-pressure EGR valve 41 after weighing needs to be found, so that the opening of the high-pressure EGR valve 40 and the opening of the low-pressure EGR valve 41 need to be calibrated. The aim of calibration is as follows: and taking the knock limit value as a boundary, and optimizing the specific gas consumption. The calibration in the application is manual calibration.
The calibration method comprises the following steps:
101: scanning the opening of the high-pressure EGR valve 40 and the opening of the low-pressure EGR valve 41 under the opening condition by taking the initial value of the opening of the throttle valve 20 as a basic value, and selecting the working condition with optimal economical efficiency under the knock limit value from the arrangement and combination results of the opening of the high-pressure EGR valve 40 and the opening of the low-pressure EGR valve 41 on the basis of the same EGR flow;
102: increasing the opening degree of the throttle valve 20, scanning the opening degree of the high-pressure EGR valve 40 and the opening degree of the low-pressure EGR valve 41 under the opening degree condition, and selecting the working condition with optimal economical efficiency under the knocking limit value from the arrangement and combination results of the opening degree of the high-pressure EGR valve 40 and the opening degree of the low-pressure EGR valve 41 on the basis of the same EGR flow rate;
103: until the knocking exceeds the limit, any condition is not within the knocking limit, and then the maximum value of the opening of the throttle valve 20 before the knocking exceeds the limit is determined, and the final opening of the high-pressure EGR valve 40 and the low-pressure EGR valve 41 is determined according to the condition that the economy corresponding to the maximum value is optimal.
The engine body 22 is optimized in terms of specific fuel consumption and economy by determining the final opening of the high-pressure EGR valve 40, the low-pressure EGR valve 41, and the opening of the throttle valve 20.
As shown in fig. 4, A1 represents a throttle valve 20 opening basic value, and B1 represents a throttle valve 20 opening limit value; a2 represents a high-pressure EGR valve 40 opening basic value, and B2 represents a high-pressure EGR valve 40 opening limit value; a3 represents a low-pressure EGR valve 41 opening basic value, and B3 represents a low-pressure EGR valve 41 opening limit value.
An ECU (Electronic Control Unit electronic control unit) on the automobile senses the speed and fuel values through sensors, namely the rotational speed and natural gas quantity of the engine body 22, and also the operating point of the engine body 22. In the working condition corresponding to the rotational speed and the natural gas amount of the engine body 22, it is necessary to determine the opening degree of the throttle valve 20, the opening degree of the high-pressure EGR valve 40, and the opening degree of the low-pressure EGR valve 41 in the working condition. Therefore, first, a base value is given to the opening degree of the throttle valve 20, the opening degree of the high-pressure EGR valve 40, and the opening degree of the low-pressure EGR valve 41, respectively: taking the throttle valve 20 opening as an example, the opening value of the throttle valve 20 (the value is within the throttle valve 20 opening limit value) is stabilized by the PID controller 1 based on the throttle valve 20 opening base value; then, the opening value of the throttle valve 20 at the moment is output, and the ECU obtains the oil consumption and detonation pressure detonation condition of the engine body 22 at the moment by matching the opening of the high-pressure EGR valve 40 and the low-pressure EGR valve 41 at the moment; after the experimental data are retained, the opening of the throttle valve 20 is adjusted to increase the opening value of the throttle valve 20 or decrease the opening value of the throttle valve 20, and the new oil consumption and detonation pressure detonation condition of the engine body 22 can be obtained by matching the opening of the high-pressure EGR valve 40 and the opening value of the low-pressure EGR valve 41, the steps of retaining the experimental data and adjusting the opening of the throttle valve 20 are repeated, and the optimal combination is selected from the arrangement and combination results of the opening of the throttle valve 20, the opening of the high-pressure EGR valve 40 and the opening of the low-pressure EGR valve 41, wherein the combination is the working condition that the economy under the detonation limit value is optimal on the basis of the same EGR flow.
In the description of the present application, it should be noted that the azimuth or positional relationship indicated by the terms "upper", "lower", etc. are based on the azimuth or positional relationship shown in the drawings, and are merely for convenience of describing the present application and simplifying the description, and are not indicative or implying that the apparatus or element in question must have a specific azimuth, be constructed and operated in a specific azimuth, and thus should not be construed as limiting the present application. Unless specifically stated or limited otherwise, the terms "mounted," "connected," and "coupled" are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, and can be communication between two elements. The specific meaning of the above terms in the present application can be understood by those of ordinary skill in the art according to the specific circumstances.
It should be noted that in the present application, relational terms such as "first" and "second" and the like are used solely to distinguish one entity or action from another entity or action without necessarily requiring or implying any actual such relationship or order between such entities or actions. Moreover, the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, method, article, or apparatus. Without further limitation, an element defined by the phrase "comprising one … …" does not exclude the presence of other like elements in a process, method, article, or apparatus that comprises the element.
The foregoing is only a specific embodiment of the application to enable those skilled in the art to understand or practice the application. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the generic principles defined herein may be applied to other embodiments without departing from the spirit or scope of the application. Thus, the present application is not intended to be limited to the embodiments shown herein but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.

Claims (10)

1. An EGR control system for a natural gas engine, comprising:
an engine air inlet pipeline (2), wherein a throttle valve (20) and an engine body (22) which are sequentially arranged along the air flow direction are arranged on the engine air inlet pipeline (2);
an EGR mixing line (1), the EGR mixing line (1) communicating with the engine intake line (2) and for mixing air with exhaust gas for delivery to the engine intake line (2);
an engine exhaust line (3), wherein a turbine (30) is arranged on the engine exhaust line (3);
an exhaust gas recovery pipeline (4), wherein the exhaust gas recovery pipeline (4) is connected with the EGR mixing pipeline (1) and the engine exhaust pipeline (3), and a high-pressure EGR valve (40) and a low-pressure EGR valve (41) are arranged on the exhaust gas recovery pipeline (4);
and, when the high-pressure EGR valve (40) is opened, the exhaust gas recovery line (4) sends the exhaust gas before being treated by the turbine (30) to the EGR mixing line (1);
when the low-pressure EGR valve (41) is opened, the exhaust gas recovery line (4) sends the exhaust gas treated by the turbine (30) to the EGR mixing line (1).
2. The natural gas engine EGR control system according to claim 1, wherein:
the exhaust pipeline (3) of the engine is also provided with an after-treatment system (31), the turbine (30) and the after-treatment system (31) are sequentially arranged along the gas flow direction, and when the low-pressure EGR valve (41) is opened, the exhaust gas recovery pipeline (4) sends the exhaust gas treated by the after-treatment system (31) to the EGR mixing pipeline (1).
3. The natural gas engine EGR control system of claim 1, further comprising:
and the exhaust gas recovery pipeline (4) is communicated with the EGR mixing pipeline (1) through the intercooler assembly, and the EGR mixing pipeline (1) is communicated with the engine air inlet pipeline (2) through the intercooler assembly.
4. A natural gas engine EGR control system as defined in claim 3, wherein: the intercooler assembly comprises an air-air intercooler (6), and the exhaust gas recovery pipeline (4) and the EGR mixing pipeline (1) pass through the air-air intercooler (6).
5. A natural gas engine EGR control system as claimed in claim 1, characterized in that the exhaust gas recovery line (4) is further provided with an EGR cooler (42);
when the high-pressure EGR valve (40) is opened, the exhaust gas recovery pipeline (4) sends the exhaust gas before being treated by the turbine (30) to the EGR mixing pipeline (1) after being treated by the EGR cooler (42);
when the low-pressure EGR valve (41) is opened, the exhaust gas recovery line (4) sends the exhaust gas treated by the turbine (30) to the EGR mixing line (1) after being treated by the EGR cooler (42).
6. The natural gas engine EGR control system according to claim 5, wherein: the engine exhaust pipeline (3) comprises a first branch (32) and a second branch (33), the first branch (32) is connected with the engine body (22) and the turbine (30), and the second branch (33) is connected with the engine body (22) and the turbine (30) so that exhaust gas discharged by the engine body (22) is divided into two paths, and the two paths are respectively sent to the turbine (30) for treatment through the first branch (32) and the second branch (33).
7. The natural gas engine EGR control system of claim 6, wherein: the high-pressure EGR valve (40) comprises a first high-pressure EGR valve (400) and a second high-pressure EGR valve (401), a third branch where the first high-pressure EGR valve (400) is positioned is connected with the first branch (32) and the EGR cooler (42), and a fourth branch where the second high-pressure EGR valve (401) is positioned is connected with the second branch (33) and the EGR cooler (42);
when the first high-pressure EGR valve (400) is opened, the exhaust gas discharged by the engine body (22) is sent to an EGR cooler (42) for treatment along a first branch (32) and a third branch;
when the second high-pressure EGR valve (401) is closed, exhaust gas discharged from the engine body (22) is sent to an EGR cooler (42) for treatment along a second branch (33) and a fourth branch.
8. The natural gas engine EGR control system according to claim 1, wherein: and a dehydrator (43) is further arranged on the waste gas recovery pipeline (4).
9. The natural gas engine EGR control system according to claim 1, wherein: the EGR mixing pipeline (1) is provided with an EGR mixer (10) and a gas compressor (11) which are sequentially arranged along the gas flow direction, the EGR mixer (10) is used for mixing air and exhaust gas to be sent to the gas compressor (11), and the gas compressor (11) is used for compressing the air and the exhaust gas to be sent to the engine air inlet pipeline (2).
10. The natural gas engine EGR control system according to claim 1, characterized in that the engine intake line (2) is further provided with a natural gas injector (21), and the throttle valve (20), the natural gas injector (21), and the engine body (22) are arranged in this order in the gas flow direction.
CN202310930796.XA 2023-07-27 2023-07-27 EGR control system of natural gas engine Pending CN116753093A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202310930796.XA CN116753093A (en) 2023-07-27 2023-07-27 EGR control system of natural gas engine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202310930796.XA CN116753093A (en) 2023-07-27 2023-07-27 EGR control system of natural gas engine

Publications (1)

Publication Number Publication Date
CN116753093A true CN116753093A (en) 2023-09-15

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