CN110145405A - The double injected petrol lean-combustion engines of perforated plate type atomizer - Google Patents
The double injected petrol lean-combustion engines of perforated plate type atomizer Download PDFInfo
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- CN110145405A CN110145405A CN201910329198.0A CN201910329198A CN110145405A CN 110145405 A CN110145405 A CN 110145405A CN 201910329198 A CN201910329198 A CN 201910329198A CN 110145405 A CN110145405 A CN 110145405A
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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
- F02D41/02—Circuit arrangements for generating control signals
- F02D41/14—Introducing closed-loop corrections
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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
- F02D41/02—Circuit arrangements for generating control signals
- F02D41/18—Circuit arrangements for generating control signals by measuring intake air flow
- F02D41/182—Circuit arrangements for generating control signals by measuring intake air flow for the control of a fuel injection device
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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
- F02D41/3011—Controlling fuel injection according to or using specific or several modes of combustion
- F02D41/3017—Controlling fuel injection according to or using specific or several modes of combustion characterised by the mode(s) being used
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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
- F02D41/3011—Controlling fuel injection according to or using specific or several modes of combustion
- F02D41/3064—Controlling fuel injection according to or using specific or several modes of combustion with special control during transition between modes
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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
- F02D41/3094—Controlling fuel injection the fuel injection being effected by at least two different injectors, e.g. one in the intake manifold and one in the cylinder
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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
- F02D41/32—Controlling fuel injection of the low pressure type
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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
- F02D41/32—Controlling fuel injection of the low pressure type
- F02D41/34—Controlling fuel injection of the low pressure type with means for controlling injection timing or duration
- F02D41/345—Controlling injection timing
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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
- F02D41/38—Controlling fuel injection of the high pressure type
- F02D41/3809—Common rail control systems
- F02D41/3818—Common rail control systems for petrol engines
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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
- F02D41/38—Controlling fuel injection of the high pressure type
- F02D41/3809—Common rail control systems
- F02D41/3836—Controlling the fuel pressure
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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
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
- F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
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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
- F02D41/38—Controlling fuel injection of the high pressure type
- F02D2041/389—Controlling fuel injection of the high pressure type for injecting directly into the cylinder
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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
- F02D2200/00—Input parameters for engine control
- F02D2200/02—Input parameters for engine control the parameters being related to the engine
- F02D2200/04—Engine intake system parameters
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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
- F02D2200/00—Input parameters for engine control
- F02D2200/02—Input parameters for engine control the parameters being related to the engine
- F02D2200/06—Fuel or fuel supply system parameters
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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
- F02D2200/00—Input parameters for engine control
- F02D2200/02—Input parameters for engine control the parameters being related to the engine
- F02D2200/06—Fuel or fuel supply system parameters
- F02D2200/0618—Actual fuel injection timing or delay, e.g. determined from fuel pressure drop
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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
- F02D2200/00—Input parameters for engine control
- F02D2200/02—Input parameters for engine control the parameters being related to the engine
- F02D2200/10—Parameters related to the engine output, e.g. engine torque or engine speed
- F02D2200/101—Engine speed
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Abstract
The present invention provides a kind of double injected petrol lean-combustion engines of perforated plate type atomizer, comprising: acquires crankshaft position data, camshaft position data, charge flow rate and the cooling water temperature of engine；Engine speed is calculated according to crankshaft position data and camshaft position data；The tables of data prestored is inquired according to engine speed, charge flow rate and cooling water temperature, obtains the ideal burning parameter of current working；By ideal burning Parameter Switch at engine control amount；Signal is pressed according to the cylinder of cylinder, calculates current Actual combustion parameter；According to Actual combustion parameter and ideal burning parameter, engine control amount is modified.By the time for spraying, injection pulse width and the ratio that optimize intake port injection and direct-injection system, realize the feedback control to combustion phase and burn rate, so that this kind layering lean burn ability that is existing with the comparable minimum discharge of homogeneous charging ignition, and can making engine that there is the work of full load range.
Description
Technical field
The present invention relates to technical field of engines, and in particular, to the double injected petrol lean-combustion engines of perforated plate type atomizer.
Background technique
With gradually implementing for six emission regulation of state, increasingly depleted and new-energy automobile the impact of petroleum resources, respectively
Big Automobile Enterprises and research institution all reduce the effective way of emissions from engines under the premise of finding and keeping original dynamic property.
The combustion mode of conventional gasoline machine is pre-mixing combustion: i.e. fuel has been adequately mixed with air before starting igniting, by saving
The aperture and control of engine speed of valve enter the air capacity of cylinder, air intake duct nozzle or cylinder inner nozzle and pass through the sky of calculating
Throughput is injected in the fuel near chemically correct fuel.Based on the characteristic that gasoline is explosive, the compression ratio of conventional gasoline machine is much smaller than
Diesel engine, generally near 10；Simultaneously in sub-load, throttle opening is smaller to will lead to pumping loss increase, causes to pass
The thermal efficiency of system gasoline engine can not be compared with diesel engine.The combustion mode of conventional diesel engine is diffusion combustion: i.e. fuel and air
Mixing and burning carry out simultaneously, the burn rate of diffusion combustion is determined by mixing rate.Conventional diesel engine is due to air
It causes gaseous mixture uneven with fuel oil incorporation time too short-range missile, high temperature area locally occurs and generate a large amount of soots, while can also go out
Now many high-temperature oxygen-enriched areas, caused nitrogen oxides emissions are higher.Based on fuel characteristic, the compression ratio of conventional diesel engine is far high
In conventional gasoline machine, therefore improving compression ratio is the effective way for improving the thermal efficiency.
By the retrieval discovery to existing technical literature, in the patented technology of double jet engines, Chinese patent application
Number CN200680008764.9, patent name: dual-injector fuel injection engine, the patented technology provide a kind of double injections
Engine mockup proposes and fuel is sprayed to the thinking to air intake duct and cylinder respectively, but its model is established based on V-shaped machine
, the parameters such as fuel injector position, angle are difficult to directly be transformed on in-line type and use, while the patented technology do not refer to it is dilute
Thin burning relevant issues, so can not fundamentally change petrol engine combustion mode.
Summary of the invention
For the defects in the prior art, the object of the present invention is to provide a kind of double injected petrol lean-burn hairs of perforated plate type atomizer
Motivation.
A kind of double injected petrol lean-combustion engines of the perforated plate type atomizer provided according to the present invention, comprising:
Sensor, acquire the crankshaft position data of engine, camshaft position data, charge flow rate, cooling water temperature and
Cylinder presses signal；
Engine speed is calculated according to crankshaft position data and camshaft position data in electronic control unit, according to
Engine speed, charge flow rate and cooling water temperature inquire the tables of data prestored, obtain the ideal burning parameter of current working, will
Ideal burning Parameter Switch presses signal at engine control amount, according to the cylinder of cylinder, calculates current Actual combustion ginseng
Number, according to Actual combustion parameter and ideal burning parameter, is modified engine control amount.
Preferably, the ideal burning parameter and the Actual combustion parameter include: combustion phase and combustion duration.
Preferably, the control amount of the engine includes: that dual fuel injection ratio, dual fuel injection moment, air throttle are opened
Degree and exhaust gas control valve aperture.
Preferably, further include: the first fuel tank, the second fuel tank, in-cylinder direct-jet mechanism, intake port injection mechanism and electronics
Control unit；
First fuel tank connects the cylinder by the in-cylinder direct-jet mechanism, and second fuel tank is logical
Cross the air intake duct that the intake port injection mechanism connects the cylinder；
The electronic control unit connects the in-cylinder direct-jet mechanism and the intake port injection mechanism, and stores the number
According to table.
Preferably, the in-cylinder direct-jet mechanism includes: high pressure fuel pump, direct-jet high pressure fuel rail and direct-injection fuel injector, institute
The both ends for stating direct-jet high pressure fuel rail are separately connected the high pressure fuel pump and the direct-injection fuel injector, the high pressure fuel pump
The other end is connected with first fuel tank, and the direct-injection fuel injector is mounted on cylinder head, the direct-injection fuel injector and institute
The control terminal for stating high pressure fuel pump is connected by conducting wire with the electronic control unit；
The intake port injection mechanism includes: low-pressure fuel pump, intake port injection low-voltage fuel rail and intake port injection spray
Oily device,
The both ends of the intake port injection low-voltage fuel rail are separately connected the low-pressure fuel pump and the intake port injection
Fuel injector, the other end of the low-pressure fuel pump are connected with second fuel tank, the intake port injection fuel injector installation
In the inlet manifold of the cylinder, the inlet valve of cylinder described in face, the intake port injection fuel injector and the low pressure are fired
The control terminal of oil pump is connected by conducting wire with the electronic control unit.
Preferably, the direct-injection fuel injector and the intake port injection fuel injector include perforated plate type atomizer.
Compared with prior art, the present invention have it is following the utility model has the advantages that
Engine is improved by the feedback control of combustion phase using the combination of intake port injection and inner cylinder direct injection
Engine emission is reduced while the thermal efficiency.Also, this starts function steadily to switch under different combustion modes, and satisfaction is started
Demand under machine different load.
Perforated plate type atomizer proposed by the present invention uses the multiple orifice nozzle with high flow area, high diffusivity degree, and is
And the oil pump that multiple orifice nozzle matches using high supply capability, injection rate can be effectively improved, fuel injection pulsewidth is made to contract
Atomization ability that is short and enhancing fuel oil, obtains mixed Daqu more rapidly, more evenly.To realize on the engine high efficiency,
The purpose of low emission.
Double injection feedback controls proposed by the present invention refer to after reading and calculating the data of in-cylinder combustion, adjust double injections
Injection timing, injection pressure and the injection pulse width of system, to realize that the combustion phase of control engine under which loading is most
Excellent phase.Double ejecting system includes intake port injection system and cylinder injection system.Intake port injection system is in the intake stroke
Fuel is sprayed, fuel forms homogeneous mixture after entering cylinder.Cylinder injection system is then in cylinder inner direct, only in fire
Small range is formed at Hua Sai and does gaseous mixture, is convenient for spark ignitor, forms layering lean burn.The direct shadow of the injection strategy of the two
Ringing the combustion characteristics of gaseous mixture in cylinder, it is therefore desirable to the injection strategy for adjusting two systems optimizes the injection proportion of two systems,
Reach the feedback control to combustion phase.
The present invention combines perforated plate type atomizer with double injection feedback controls, not only can be with the improvement fuel spray of high degree
Change effect, can also use under the collective effect of intake port injection system and in-cylinder direct-jet system two ways to combustion phase
Carry out feedback control.By the injection pulse width of the time for spraying of optimization direct-injection and intake port injection system, two sets of spraying systems with
And the ratio of two sets of spraying system the amount of injection, the feedback control to combustion phase and burn rate is realized, so that this kind of thin combustion
The existing and comparable minimum discharge of homogeneous charge combustion ignition is burnt, and it is complete that the engine operated under the combustion mode can be made to have
The ability of load range work.
Detailed description of the invention
Upon reading the detailed description of non-limiting embodiments with reference to the following drawings, other feature of the invention,
Objects and advantages will become more apparent upon:
Fig. 1 is work flow diagram of the invention；
Fig. 2 is the structural schematic diagram of the embodiment of the present invention.
Specific embodiment
The present invention is described in detail combined with specific embodiments below.Following embodiment will be helpful to the technology of this field
Personnel further understand the present invention, but the invention is not limited in any way.It should be pointed out that the ordinary skill of this field
For personnel, without departing from the inventive concept of the premise, several changes and improvements can also be made.These belong to the present invention
Protection scope.
As shown in Figure 1, a kind of homogeneity compression-ignition control method provided by the invention, comprising steps of
S1: crankshaft position data, camshaft position data, charge flow rate and the cooling water temperature of engine are acquired；
S2: engine speed is calculated according to crankshaft position data and camshaft position data；
S3: the tables of data prestored is inquired according to engine speed, charge flow rate and cooling water temperature, obtains current working
Ideal burning parameter；
S4: by ideal burning Parameter Switch at engine control amount；
S5: signal is pressed according to the cylinder of cylinder, calculates current Actual combustion parameter；
S6: according to Actual combustion parameter and ideal burning parameter, engine control amount is modified.
Wherein, ideal burning parameter and Actual combustion parameter include: combustion phase and combustion duration.The control of engine
Amount includes: dual fuel injection ratio, dual fuel injection moment, throttle opening and exhaust gas control valve aperture.
As shown in Fig. 2, the present invention also provides a kind of homogeneity compression-ignition engines, comprising:
High-octane rating fuel tank 1, high cetane number fuel tank 9, in-cylinder direct-jet mechanism, intake port injection mechanism, exhaust gas are again
The circulatory system, air throttle 14, electronic control unit 32, intake flow sensor 11, cooling-water temperature sensor, cylinder pressure sensor
28, crankshaft position sensor.
The in-cylinder direct-jet mechanism includes: high pressure fuel pump 8, direct-jet high pressure fuel rail 7 and direct-injection fuel injector 18,
In: 7 both ends of direct-jet high pressure fuel rail are separately connected high pressure fuel pump 8 and direct-injection fuel injector 18,8 other end of high pressure fuel pump and height
Cetane number fuel tank 9 is connected, and direct-injection fuel injector 18 is mounted in cylinder head, and nozzle is located at cylinder head.Direct-injection spray
The control terminal of oily device 18 and high pressure fuel pump 8 is connected by pilot with electronic control unit 32.
The intake port injection mechanism includes: low-pressure fuel pump 2, intake port injection low-voltage fuel rail 3 and air intake duct spray
Penetrate fuel injector 16, in which: 3 both ends of intake port injection low-voltage fuel rail are separately connected low-pressure fuel pump 2 and intake port injection oil spout
Device 16,2 other end of low-pressure fuel pump is connected with high-octane rating fuel tank 1, and intake port injection fuel injector 16 is mounted on cylinder
Inlet manifold on, nozzle face inlet valve.The control terminal of intake port injection fuel injector 16 and low-pressure fuel pump 2 passes through control
Conducting wire is connected with electronic control unit 32.
The direct-injection fuel injector 18 and the intake port injection fuel injector 16 include perforated plate type atomizer.
The gas recirculation system includes EGR control valve 12,12 both ends of EGR control valve difference
Connect air inlet pipe and exhaust pipe.The control terminal of EGR control valve 12 is connected by pilot with electronic control unit 32
It connects.
The acquisition of electronic control unit 32 is passed from intake flow sensor 11, cooling-water temperature sensor, cylinder pressure
Sensor 28, crankshaft position sensor, CMPS Camshaft Position Sensor and throttle position sensor signal, through calculating, driving
High pressure fuel pump 8, direct-injection fuel injector 18, low-pressure fuel pump 2, intake port injection fuel injector 16, EGR control valve 12 and
Throttle motor executes corresponding movement.
It is fired in the high-octane rating fuel tank 1 filled with gasoline or high-octane rating additive gasoline or other high-octane ratings
Oil.Filled with polyoxy methyl dimethoxy ether or high cetane number additive gasoline or other height in the high cetane number fuel tank 9
Cetane fuels.
The compression ratio of homogeneity compression-ignition engine is 13 to 15.
At work, electronic control unit 32 is sensed homogeneity compression-ignition engine by crankshaft position sensor, camshaft location
Device signal, calculates engine speed, obtains charge flow rate by intake flow sensor 11, is obtained by cooling-water temperature sensor
Cooling water temperature is looked by revolving speed, charge flow rate, cooling water temperature and the tables of data being stored in inside electronic control unit 32 is taken to obtain
These parameters are converted to dual fuel injection ratio, spray by the parameters such as required combustion phase, combustion duration under current working
The control amounts such as moment, throttle angle degree, exhaust gas control valve aperture are penetrated, direct-injection fuel injector 18, intake port injection oil spout are driven
Device 16, high pressure fuel pump 8, low-pressure fuel pump 2, EGR control valve 12 and throttle motor execute corresponding movement,
At the same time, electronic control unit 32 presses signal using the cylinder that cylinder pressure sensor 28 acquires, and calculates current combustion phase, combustion
The duration is burnt, compared with the ideal parameters found, to dual fuel injection ratio, time for spraying, throttle angle degree, exhaust gas
The control amounts such as control valve opening are modified, and realize the closed-loop control of bump combustion chamber process.
Engine fuel supply mode is split into two parts of intake port injection system and in-cylinder direct-jet system by the present invention,
Allow to control under the collective effect of two ways to burning.Pass through optimization intake port injection and direct-injection system
The ratio of time for spraying, the injection pulse width of two sets of spraying systems and two sets of spraying system the amount of injection, realize to combustion phase and
The feedback control of burn rate, so that this kind layering lean burn is existing with the comparable minimum discharge of homogeneous charging ignition,
The ability that can make the engine operated under the combustion mode that there is the work of full load range again, while being easy to implement point of fuel
Layer lean burn, improves its economy.
Specific embodiments of the present invention are described above.It is to be appreciated that the invention is not limited to above-mentioned
Particular implementation, those skilled in the art can make a variety of changes or modify within the scope of the claims, this not shadow
Ring substantive content of the invention.In the absence of conflict, the feature in embodiments herein and embodiment can any phase
Mutually combination.
Claims (6)
1. a kind of double injected petrol lean-combustion engines of perforated plate type atomizer characterized by comprising
Sensor acquires crankshaft position data, camshaft position data, charge flow rate, cooling water temperature and the cylinder pressure of engine
Signal；
Engine speed is calculated according to crankshaft position data and camshaft position data in electronic control unit, according to starting
Machine revolving speed, charge flow rate and cooling water temperature inquire the tables of data prestored, obtain the ideal burning parameter of current working, it would be desirable to
Combustion parameter is converted into engine control amount, presses signal according to the cylinder of cylinder, calculates current Actual combustion parameter, root
Factually border combustion parameter and ideal burning parameter, are modified engine control amount.
2. the double injected petrol lean-combustion engines of perforated plate type atomizer according to claim 1, which is characterized in that the ideal combustion
It burns parameter and the Actual combustion parameter includes: combustion phase and combustion duration.
3. the double injected petrol lean-combustion engines of perforated plate type atomizer according to claim 1, which is characterized in that the engine
Control amount include: dual fuel injection ratio, dual fuel injection moment, throttle opening and exhaust gas control valve aperture.
4. the double injected petrol lean-combustion engines of perforated plate type atomizer according to claim 1, which is characterized in that further include: the
One fuel tank, the second fuel tank, in-cylinder direct-jet mechanism, intake port injection mechanism and electronic control unit；
First fuel tank connects the cylinder by the in-cylinder direct-jet mechanism, and second fuel tank passes through institute
State the air intake duct that intake port injection mechanism connects the cylinder；
The electronic control unit connects the in-cylinder direct-jet mechanism and the intake port injection mechanism, and stores the data
Table.
5. the double injected petrol lean-combustion engines of perforated plate type atomizer according to claim 4, which is characterized in that straight in the cylinder
Spraying mechanism includes: high pressure fuel pump, direct-jet high pressure fuel rail and direct-injection fuel injector, the both ends difference of the direct-jet high pressure fuel rail
The high pressure fuel pump and the direct-injection fuel injector are connected, the other end of the high pressure fuel pump is connected with first fuel tank
It connects, the direct-injection fuel injector is mounted on cylinder head, and the control terminal of the direct-injection fuel injector and the high pressure fuel pump is by leading
Line is connected with the electronic control unit；
The intake port injection mechanism includes: low-pressure fuel pump, intake port injection low-voltage fuel rail and intake port injection fuel injector,
The both ends of the intake port injection low-voltage fuel rail are separately connected the low-pressure fuel pump and the intake port injection fuel injector, institute
The other end for stating low-pressure fuel pump is connected with second fuel tank, and the intake port injection fuel injector is mounted on the cylinder
Inlet manifold on, the inlet valve of cylinder described in face, the control of the intake port injection fuel injector and the low-pressure fuel pump
End is connected by conducting wire with the electronic control unit.
6. the double injected petrol lean-combustion engines of perforated plate type atomizer according to claim 5, which is characterized in that the direct-injection spray
Oily device and the intake port injection fuel injector include perforated plate type atomizer.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910329198.0A CN110145405A (en) | 2019-04-23 | 2019-04-23 | The double injected petrol lean-combustion engines of perforated plate type atomizer |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201910329198.0A CN110145405A (en) | 2019-04-23 | 2019-04-23 | The double injected petrol lean-combustion engines of perforated plate type atomizer |
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113775433A (en) * | 2020-06-10 | 2021-12-10 | 上海汽车集团股份有限公司 | Engine combustion system |
| CN114233505A (en) * | 2022-02-25 | 2022-03-25 | 潍柴动力股份有限公司 | Method for injecting fuel into a swirl combustion chamber, vehicle and storage medium |
| CN115750067A (en) * | 2022-11-09 | 2023-03-07 | 重庆长安汽车股份有限公司 | Hybrid gasoline engine combustion system, combustion method, engine and vehicle |
| CN115750067B (en) * | 2022-11-09 | 2024-04-12 | 重庆长安汽车股份有限公司 | Combustion system and combustion method of hybrid gasoline engine, engine and vehicle |
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