CN108571392A - Lean-burn systems and method for spark-ignition engine - Google Patents
Lean-burn systems and method for spark-ignition engine Download PDFInfo
- Publication number
- CN108571392A CN108571392A CN201710144104.3A CN201710144104A CN108571392A CN 108571392 A CN108571392 A CN 108571392A CN 201710144104 A CN201710144104 A CN 201710144104A CN 108571392 A CN108571392 A CN 108571392A
- Authority
- CN
- China
- Prior art keywords
- engine
- cylinder
- fuel
- lean
- fuel oil
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- 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
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D43/00—Conjoint electrical control of two or more functions, e.g. ignition, fuel-air mixture, recirculation, supercharging or exhaust-gas treatment
-
- 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
- F02M31/00—Apparatus for thermally treating combustion-air, fuel, or fuel-air mixture
- F02M31/02—Apparatus for thermally treating combustion-air, fuel, or fuel-air mixture for heating
- F02M31/16—Other apparatus for heating fuel
- F02M31/18—Other apparatus for heating fuel to vaporise fuel
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02P—IGNITION, OTHER THAN COMPRESSION IGNITION, FOR INTERNAL-COMBUSTION ENGINES; TESTING OF IGNITION TIMING IN COMPRESSION-IGNITION ENGINES
- F02P5/00—Advancing or retarding ignition; Control therefor
- F02P5/04—Advancing or retarding ignition; Control therefor automatically, as a function of the working conditions of the engine or vehicle or of the atmospheric conditions
- F02P5/045—Advancing or retarding ignition; Control therefor automatically, as a function of the working conditions of the engine or vehicle or of the atmospheric conditions combined with electronic control of other engine functions, e.g. fuel injection
Abstract
The present invention provides a kind of lean-burn systems and method for spark-ignition engine.The method includes：First heated fuel oil, fuel oil is sprayed respectively at two air intake ducts being connect with cylinder again, anxious Boiling Fuel Injection Spray is dodged to be formed, and at the air intake duct of engine when injection fuel oil, the inlet valve of engine is in open state always, or, the inlet valve of engine was closed before this, and then the inlet valve of engine is in open state, and a certain moment of fuel oil is sprayed at the air intake duct of engine, the piston of engine is located at air inlet top dead centre, to form uniform Weak mixture in cylinder；In the compression stroke of engine, in in-cylinder injection fuel oil；It lights a fire when apart from in-cylinder injection fuel oil finish time, 0 crank angle degrees were to 10 crank angle degrees.The present invention can be achieved oil consumption is low, NOx concentration is low, it is granular material discharged less with lean burn at low cost.
Description
Technical field
The present invention relates to technical field of engines, more particularly to a kind of lean-burn systems for spark-ignition engine and
Method.
Background technology
The gaseous mixture that air-fuel ratio is more than chemically correct fuel is referred to as Weak mixture, the combustion of Weak mixture within the engine
It burns and is referred to as lean burn.By forming Weak mixture, pumping loss is not only considerably reduced, but also improve gaseous mixture
Specific heat ratio, and reduce heat transfer loss.Therefore, lean burn is considered as improving the gasoline engine thermal efficiency, reducing the effective of oil consumption
Means.
Currently, lean burn includes mainly three kinds of modes：Homogeneous charge is used to burn in a manner of compression self-igniting
Homogeneous charge compression ignition is used in port-Fuel-Injected to form stratified mixtures in cylinder and be burnt in a manner of spark ignition
Intake port injection is layered lean-burn, and uses in in-cylinder direct-jet to form stratified mixtures in cylinder and in a manner of spark ignition
The in-cylinder direct-jet of burning is layered lean-burn.Wherein, though the in-cylinder direct-jet for being layered lean-burn using in-cylinder direct-jet is layered lean-burn systems
Market is so come into, but only the Ji Jia motor corporations of minority obtain volume production in the world so far, it is big without obtaining
Amount is universal, mainly its there are following Railway Projects：
1) in-cylinder direct-jet layering lean-burn systems easily lead to NOx concentration raising, need that the catalysis specifically for NOx is arranged
Converter, this does not only result in cost increase, also results in lean burn fuel-economizing effect reduction and granular material discharged increase.Specifically
It says, although whole air-fuel ratio is very low, forms partially dense gaseous mixture around spark plug in order to stablize burning and make front half section
The original NOx concentration generated of burning is high, so need to post-process NOx.However, lean burn make it is at low cost and a large amount of
The NOx conversion efficiency of universal ternary catalyzing unit is close to 0%.Therefore, it is necessary to additionally configure NOx turns specifically for lean burn
Change device, as lean-burn NOx collects device (Lean NOx Trap, LNT).But risings of the LNT in addition to bringing cost, it is also necessary to pass through week
The enriching of phase property burns to carry out the regeneration of catalyst converter, this can not only sacrifice oil consumption so that the fuel-economizing potentiality of lean burn are beaten greatly
Discount also easily leads to granular material discharged increase.
2) partially dense burning of the in-cylinder direct-jet layering lean-burn systems around spark plug leads to granular material discharged increase, this
New challenge is brought to the granular material discharged regulation for meeting more and more harsh in current world wide.
3) in-cylinder direct-jet layering lean-burn systems is used to need the piezo-electric crystal in-cylinder direct-jet oil spout of higher operating costs
Device, with realize by several times injection different pressures, the fuel oil of different durations so that in-cylinder direct-jet be layered lean-burn systems cost compared with
It is high.
Invention content
The purpose of the present invention is to provide a kind of lean-burn systems and method for spark-ignition engine, existing to solve
NOx concentration height, granular material discharged height and the problem of high cost that some in-cylinder direct-jet layering lean-burn systems generate.
In order to solve the above technical problems, the present invention provides a kind of lean burn method for spark-ignition engine, including
The injection fuel oil at first heated fuel oil, then two air intake ducts being connect within the engine with cylinder dodges anxious boiling spray to be formed
Mist；And when spraying the fuel oil at the air intake duct of engine, the inlet valve of the engine is in open state always, or
The inlet valve of person, the engine were closed before this, and then the inlet valve of engine is in open state；Also,
The a certain moment of fuel oil is sprayed at the air intake duct of engine, the piston of engine is located at air inlet top dead centre, with the shape in cylinder
At uniform Weak mixture；In the compression stroke of engine, in-cylinder direct-jet is carried out to fuel oil；And it is being sprayed in cylinder
It lights a fire when penetrating fuel oil finish time 0 crank angle degrees to 10 crank angle degrees.
Further, the fuel-injection pressure of the air intake duct of engine is less than or equal to 1MPa.
Further, the maximum temperature after fuel Heating is 90 DEG C to 110 DEG C.
Further, the fuel-injection pressure of in-cylinder direct-jet is more than or equal to 20MPa, and is less than or equal to 150MPa, also, sprays
Oily duration is more than or equal to 0.05ms, and is less than or equal to 0.3ms.
The present invention also provides a kind of lean-burn systems for spark-ignition engine, including an engine, engine packets
The in-cylinder direct-jet fuel injector and spark plug for including at least one cylinder and being arranged in each cylinder, in-cylinder direct-jet fuel injector are used for
In in-cylinder injection fuel oil in the compression stroke of engine, fuel-injection pressure is more than or equal to 20MPa, and oil spout duration is less than
Equal to 0.3ms；Spark plug is spraying 0 crank angle degrees of fuel oil finish time to 10 crank angle degrees apart from in-cylinder direct-jet fuel injector
When light a fire.
Further, further include air intake duct and air flue fuel injector, each cylinder is at least connected with an air intake duct, and at least one
Air flue fuel injector is provided at a air intake duct, air flue fuel injector is used to spray fuel oil into air intake duct thin to be formed in cylinder
Gaseous mixture.
Further, further include the first oil supply pipe and the first oily rail, one end and the air flue oil spout of the first oil supply pipe
Device connects, and the first oily rail is provided on the first oil supply pipe.
Further, further include heating device, air flue fuel injector is ejected through the combustion of heating devices heat into air intake duct
Oil.
Further, the maximum temperature of the fuel oil of air flue fuel injector injection is 90 DEG C to 110 DEG C.
Further, each cylinder connects two air intake ducts, and is both provided with air flue fuel injector at each air intake duct.
Further, further include inlet valve, inlet valve setting is between cylinder and air intake duct, and air flue fuel injector is close to air inlet
Door setting.
Further, the fuel-injection pressure of the air intake duct of engine is less than or equal to 1MPa.
Further, further include exhaust valve, the cylinder has a combustion chamber, in-cylinder direct-jet fuel injector and spark plug setting
Top in combustion chamber, and spark plug is close to exhaust valve.
Further, for in-cylinder direct-jet fuel injector in in-cylinder injection fuel oil, fuel-injection pressure is less than or equal to 150MPa,
And oil spout duration is more than or equal to 0.05ms.
Compared with prior art, provided by the present invention for the lean-burn systems of spark-ignition engine and method, due to
Form homogeneous lean gaseous mixture in cylinder, and in the compression stroke of engine, in-cylinder direct-jet carried out to fuel oil, and away from
It lights a fire when from 0 crank angle degrees of in-cylinder injection fuel oil finish time to 10 crank angle degrees so that the fuel oil around spark plug
Overrich area area reduce, and high-pressure injection improves the turbulence intensity around spark plug in cylinder, to accelerate initial flame
Spread speed so that homogeneous lean gaseous mixture is stabilized burning, on the one hand, reduce in the prior art due to spark plug week
Enclose the content for the NOx that the overrich area of large area is formed in combustion so that the gas discharged out of cylinder need not be arranged
Specifically for the catalytic converter of NOx, cost has not only been saved, has also saved fuel oil, and has been reduced granular material discharged；Another party
Face, due to being homogeneous lean gaseous mixture, the particulate matter reduction of lean burn generation；Another further aspect is formed due to the present invention
It is homogeneous lean gaseous mixture, it is high without use cost and thin to form layering to the sensitive piezo-electric crystal fuel injector of oil product
Gaseous mixture, thus saved cost.
Secondly, first heated fuel oil, then the fuel oil of heating is ejected through to be formed in cylinder at the air intake duct of engine
Weak mixture forms liquid-drop diameter compared to normal due to passing through the fuel oil of heating and easily occurring to dodge urgency boiling phenomenon in injection
The small sudden strain of a muscle urgency Boiling Fuel Injection Spray of spraying of rule, therefore it is more advantageous to the evaporation, atomization and the mixing with air of drop so that it is thin
Gaseous mixture is more uniformly distributed, and uniform Weak mixture makes burning more abundant and more stable, the NOx that generates therewith and big
Particulate matter is reduced.
Secondly, each cylinder sprays fuel oil at two air intake ducts being attached thereto so that the single spray in the present invention
The maximum stream flow of the relatively conventional one fuel injector scheme of a cylinder of oily device can be with smaller, and then reduces the drop ruler of spraying
It is very little, to further improve air-fuel mixture, make homogeneous lean gaseous mixture lean burn while fuel-economizing, reduces what burning generated
NOx and granular material discharged.
Again, due to present invention employs all sprayed at two air intake ducts of cylinder it is heated after fuel oil, to for
Realize that all or part of inlet valve valve opening injection creates condition, i.e., when spraying fuel oil at the air intake duct of engine, engine
Inlet valve be in open state, alternatively, the inlet valve of engine was closed before this, the then air inlet of engine always
Door is in open state, is formed conducive to fuel oil and dodges anxious Boiling Fuel Injection Spray, and certain a period of time of fuel oil is sprayed at the air intake duct of engine
It carves, the piston of engine is located at air inlet top dead centre, so that the fuel oil sprayed at air intake duct can be located at air inlet in piston
At top dead centre, fuel oil just has begun and the gas mixing in cylinder so that the incorporation time of fuel oil and gas maximizes, so
It is maximized with the gas mixing time in cylinder so that dodging anxious Boiling Fuel Injection Spray, the Weak mixture in cylinder is made to mix more equal
It is even, keep Lean burn engine more abundant, and more stable, the NOx and large particle of generation of burning are further reduced.
Description of the drawings
Fig. 1 is the lean-burn systems schematic diagram that spark-ignition engine is used in one embodiment of the invention；
Fig. 2 is the arrangement schematic diagram of the air intake duct of single cylinder in one embodiment of the invention；
Fig. 3 is intake port injection fuel oil, cylinder injection fuel oil and igniting when realizing lean burn in one embodiment of the invention
Tactful schematic diagram；
Fig. 4 is intake port injection fuel oil, cylinder injection fuel oil and point when realizing lean burn in another embodiment of the present invention
The tactful schematic diagram of fire；
The reference numerals are as follows：
10- cylinders；
20- air intake ducts；
The combustion chambers 30-；
40- exhaust valves；
50- spark plugs；
The first fuel oil supply systems of 60-；
61- fuel tanks；
The oily rails of 62- first；
The first oil supply pipes of 63-；
64- heating devices；
65- air flue fuel injectors；
The second fuel oil supply systems of 70-；
The second oil pumps of 71-；
The oily rails of 72- second；
73- in-cylinder direct-jet fuel injectors；
The second oil supply pipes of 74-；
80- inlet valves；
The oil spout period of A- air flue fuel injectors；
The oil spout period of B- in-cylinder direct-jet fuel injectors；
The C- plug ignition moment；
Δ-time interval of the In-cylinder injector end of injection moment apart from time of ignition.
Specific implementation mode
Below in conjunction with the drawings and specific embodiments to the lean-burn systems proposed by the present invention for spark-ignition engine
And method is described in further detail.According to following explanation and claims, advantages and features of the invention will become apparent from.It needs
Illustrate, attached drawing is all made of very simplified form and uses non-accurate ratio, only to convenient, lucidly auxiliary is said
The purpose of the bright embodiment of the present invention.
The present embodiment provides a kind of lean burn methods for spark-ignition engine, and lean mixture is formed in cylinder
Gas, also, in the compression stroke of engine, in in-cylinder injection fuel oil, and apart from in-cylinder injection fuel oil finish time 0
It lights a fire when crank angle degrees are to 10 crank angle degrees.Wherein, above-mentioned all oil spouts and ignition strategies are in one cycle of engine
It completes.
Due to forming Weak mixture in cylinder, and in the compression stroke of engine, in in-cylinder injection fuel oil, fit
When light a fire (lighting a fire when apart from in-cylinder injection fuel oil finish time, 0 crank angle degrees were to 10 crank angle degrees), thus,
On the one hand short in the time of in-cylinder injection fuel oil so that fuel injection amount is reduced so that the overrich formed around spark plug
Area greatly reduces, and most Weak mixture in cylinder is made to remain to keep uniform；On the other hand, the side of high pressure is used in cylinder
Formula sprays fuel oil, and the fuel spray of this high speed improves the turbulence intensity around spark plug, in conjunction in due course igniting, to accelerate
The spread speed of initial flame so that uniform Weak mixture stablizes burning in cylinder.Compared with the prior art in middle cylinder
The layering lean combustion mode of direct injection, first, the overrich area formed around spark plug in the present embodiment are reduced, and can be stablized
Burnup, thus reduce in the prior art due to large-scale overrich area is formed in combustion around spark plug NOx
Content so that the catalytic converter specifically for NOx need not be arranged in the gas discharged out of cylinder, to saved at
This；Secondly, overrich area is reduced, and uniform Weak mixture and burnup stabilization are formed in cylinder, makes fuel oil burning more
Fully, so significantly reducing granular material discharged；Again, since formed is homogeneous lean gaseous mixture to the present invention, without
Use cost is high and forms layering Weak mixture to the sensitive piezo-electric crystal fuel injector of oil product, it is possible to which use is big
The Conventional fuel injectors of bulk article, to save cost.
In preferred embodiment, when carrying out in-cylinder direct-jet to fuel oil, the injection pressure of fuel oil is more than or equal to 20MPa, and less than etc.
In 150MPa, it is 0.05ms to 0.3ms in the injecting time of in-cylinder injection fuel oil, lean burn may make more to stablize, and
Reduce the content for the NOx that burning generates and the discharge of particulate matter.
It is used in order to further reduce the cost, in the present embodiment and sprays fuel oil at the air intake duct of engine in cylinder
Form Weak mixture, general port injector can be used in the fuel oil of intake port injection, compared with the prior art in set
The in-cylinder direct-jet fuel injector in cylinder is set, it is at low cost, and be easily achieved.
In order to make the fuel oil of intake port injection, into cylinder after form the Weak mixture being more uniformly distributed so that thin combustion
The content and particulate matter of NOx after burning is further reduced, in the present embodiment, first heated fuel oil, then at the air intake duct of engine
It is ejected through the fuel oil of heating.This fuel oil after heating easily occurs to dodge anxious boiling phenomenon in injection.Fuel oil is being sent out
The raw liquid-drop diameter for dodging the anxious Boiling Fuel Injection Spray of the sudden strain of a muscle formed after anxious boiling is small compared to conventional spraying, therefore is more advantageous to the steaming of drop
Hair, atomization and the mixing with air so that Weak mixture is more uniformly distributed, and uniform gaseous mixture makes the combustion of Weak mixture
Burn more abundant and more stable, to generate therewith NOx and large particle reduction.For example, before fuel oil sprays at air intake duct,
Maximum temperature after heating is 90 DEG C to 110 DEG C.Specifically, the first fuel delivery is arranged in the fuel oil supply system of engine
System, first fuel oil supply system include that the first oil supply pipe, the first oily rail and air flue fuel injector, air flue fuel injector pass through
First oil supply pipe is connect with the first oily rail, can realize fuel Heating by the oily rail of heating first.First oily rail is fired for storing
Oil, while the pressure oscillation for inhibiting the oil circuit of the first fuel oil supply system to generate, it is ensured that the first fuel oil supply system pressure stability.
In addition, in the present embodiment, it can also be by setting the oil injection time of fuel oil and the opening moment of valve at air intake duct
The Weak mixture in cylinder is set to be more uniformly distributed.For example, refering to what is shown in Fig. 3, engine in the single loop of operating, is starting
When the intake port injection fuel oil of machine, inlet valve is in open state, i.e. inlet valve is in inlet valve lift, alternatively, with reference to figure 4
Shown, inlet valve is first closed, and then inlet valve again is at open state, and in the intake port injection fuel oil of engine
The a certain moment, the piston of engine is located at air inlet top dead centre.Inlet valve is first in open state when spraying fuel oil, and is sending out
The a certain moment of the intake port injection fuel oil of motivation, the piston of engine are located at the valve opening injection strategy at air inlet top dead centre, with
And inlet valve is first closed when injection fuel oil, rear inlet valve is in open state, is fired in the intake port injection of engine
The a certain moment of oil, the piston of engine are located at the part valve opening injection strategy at air inlet top dead centre, both injection strategies make
It obtains at the beginning of exhaust stroke latter stage or induction stroke, will just have occurred and that the spraying dodged boiling and be well atomized is directly entered
Carry out gaseous mixture preparation in cylinder, rather than it is conventional be ejected into air intake duct surface, merely by air intake duct heating and recirculating exhaust gas
Heating and impact make fuel evaporation and atomization, to make the Weak mixture in cylinder mix to be more uniformly distributed, and keep away
Exempt from fuel oil and encounter airway surface to form a large amount of non-fuel films and lead to granular material discharged increase.
It again, can also be optimizing in such a way that the fuel oil of intake port injection enters in cylinder, into one in the present embodiment
Step ensure form the gaseous mixture being more uniformly distributed after fuel oil enters cylinder.For example, in two air inlets being connect with single cylinder
Fuel oil is sprayed in road respectively.Relative to the mode for spraying fuel oil only in an air intake duct of cylinder, single air intake duct intermediate fuel oil
Maximum stream flow reduce, conducive to smaller fuel droplets are formed so that Weak mixture is more uniformly distributed.
In the present embodiment, the in-cylinder direct-jet during uniform Weak mixture is compared with the existing technology is layered lean burn
For the layering Weak mixture of system.
For another example, fuel oil is sprayed at inlet valve in air intake duct, specifically, can be sprayed at inlet valve in air intake duct
Fuel oil.By injecting fuel into air intake duct in compared with the prior art, it is simple by air intake duct heating and recirculating exhaust gas plus
Heat and impact make fuel evaporation and the mode of atomization, and need the mode of oil spout at the time of IC Intake Valve Closes, in the present embodiment
Fuel oil by the injection mode of this close inlet valve, to realize that whole valve opening injections or the injection of part valve opening create item
Part, and more uniform Weak mixture is formed beneficial to having occurred and that the anxious spraying boiled and be well atomized of sudden strain of a muscle is directly entered cylinder.
In the present embodiment, preferably smaller than it is equal to 1Mpa in the injection pressure of the fuel oil of the intake port injection of engine.So
It may be used conventional fuel injector in port-Fuel-Injected, and it is not necessary that high pressure fuel injector and corresponding with high pressure fuel injector is arranged
Second oil pump and the second oily rail, reduce cost.
From the foregoing, it will be observed that the present embodiment sprays to form the anxious Boiling Fuel Injection Spray of sudden strain of a muscle, rationally setting spray by carrying out fuel oil in air intake duct
Mist enters mode and the time of cylinder, to form uniform Weak mixture, in conjunction with the injection mode and oil spout being arranged in cylinder
Time, and the rational point moment of setting, realize the lean burn of efficient stable.What is provided in the present embodiment is above-mentioned for point
The lean burn method of combustion engine is suitable at least one cylinder of engine, as follows with one in the single cylinder of engine
Illustrate for the burning of cycle for realizing the lean-burn systems of the above-mentioned lean burn method for spark-ignition engine.
Refering to what is shown in Fig. 1, the lean-burn systems for spark-ignition engine include：Cylinder 10, air intake duct 20, the first fuel supply system
System 60 and the second fuel oil supply system 70.Air intake duct 20 is connect with cylinder 10, and air is provided for cylinder 10.First fuel supply system
System 60 is that cylinder 10 provides fuel oil by spraying fuel oil in air intake duct 20.Second fuel oil supply system 70 passes through in cylinder 10
Directly injection fuel oil is that cylinder 10 provides fuel oil.
First fuel oil supply system 60 includes first the 61, first oily rail 62 of fuel tank, the first oil supply pipe 63, heating device 64
With air flue fuel injector 65.Air flue fuel injector 65 is connect by the first oil supply pipe 63 with the first oily rail 62, and the first oily rail 62 passes through
First oil supply pipe 63 is connect with the first fuel tank 61.Air flue fuel injector 65 is arranged at air intake duct 20, for into air intake duct 20
Spray fuel oil.The injection pressure for the fuel oil that air flue fuel injector 65 sprays preferably smaller than is equal to 1MPa.Air flue fuel injector 65 can be used
The multiple orifice nozzle of the solenoid-driven of engine is penetrated in conventional admission road, it is preferred to use porous swirl type fuel injector (Swirl
Injector).First oily rail 62 inhibits to generate due to the first fuel tank 61 and 65 oil spout of air flue fuel injector for storing fuel oil
Pressure oscillation, it is ensured that 60 pressure stability of the first fuel oil supply system.Heating device 64 realizes combustion for heating the first oily rail 62
Oil heating so that the maximum temperature of the fuel oil sprayed from air flue fuel injector 65 is 90 DEG C to 110 DEG C.Wherein, heating device 64
Fuel Heating can be realized by heating the first oil supply pipe 63 being connect with air flue fuel injector 65.Certainly, air flue fuel injector 65 sprays
The injection pressure for the fuel oil penetrated is also greater than 1MPa, and only air flue fuel injector 65 correspondingly is needed using suitable for high-pressure injection
Fuel injector and setting for for fuel injector fuel feeding high pressure fuel feed system, the cost is relatively high.
Second fuel oil supply system 70 includes the second fuel tank (not shown), second the 71, second oily rail 72, second of oil pump
Oil supply pipe 74 and in-cylinder direct-jet fuel injector 73.In-cylinder direct-jet fuel injector 73 is connected by the second oil supply pipe 74 and the second oily rail 72
It connects, the second oily rail 72 is connect by the second oil supply pipe 74 with the second oil pump 71, and the second oil pump 71 passes through the second oil supply pipe 74
It is connect with the second fuel tank 61.In-cylinder direct-jet fuel injector 73, close to time of ignition, is sprayed for the phase after the compression stroke into cylinder 10
The high pressure fuel that fuel-injection pressure is more than or equal to 20MPa is penetrated, and oil spout duration is less than or equal to 0.3ms.For example, in-cylinder direct-jet sprays
Oily device 73 uses the interior open loop multiple orifice nozzle of solenoid-driven used in conventional direct spray petrol engine in cylinder.Second oily rail 72 is used
In storage fuel oil, while inhibiting the pressure oscillation generated due to the second oil pump 71 and 73 oil spout of in-cylinder direct-jet fuel injector, it is ensured that the
Two fuel oil supply systems, 70 pressure stability.
It should be appreciated that the first fuel oil supply system 60 and the second fuel oil supply system 70 can respectively contain a fuel tank,
Can also be as shown in Figure 1, the second fuel oil supply system 70 and the first fuel oil supply system 60, which share a fuel tank, (shares the
One fuel tank 61), with cost-effective.
Wherein, further include exhaust valve 40 and spark plug 50 for the lean-burn systems of spark-ignition engine, cylinder includes
Combustion chamber 30, in-cylinder direct-jet fuel injector 73 and spark plug 50 are arranged at 30 top of combustion chamber, also, spark plug 50 is relative to cylinder
Closer to exhaust valve 40 for interior direct-injection fuel injector 73.Spark plug 50 is spraying 0 degree of fuel oil finish time in cylinder 10
It lights a fire when crank angle is to 10 crank angle degrees.It is of course also possible to which spark plug 50 and the setting of in-cylinder direct-jet fuel injector 73 are being fired
Burn the top of room 30, and in-cylinder direct-jet fuel injector 73 for spark plug 50 closer to exhaust valve 40.
The single cylinder 10 of engine generally comprises two air intake ducts 20, refering to what is shown in Fig. 2, can be at two air intake ducts 20
It is respectively provided with air flue fuel injector 65.In the present embodiment, the lean-burn systems for spark-ignition engine further include inlet valve 80, into
Valve 80 is arranged between cylinder 10 and air intake duct 20, and air flue fuel injector 65 is arranged close to inlet valve 80.
Below for the course of work by engine in a working cycles, in conjunction with shown in Fig. 1 and Fig. 2, illustrate this reality
The course of work of the lean-burn systems for spark-ignition engine of example offer is provided.
With reference to figure 3, a working cycles of engine include：Expansion stroke, exhaust stroke, induction stroke and compression punching
Journey.Wherein, compression top center and air inlet top dead centre it is corresponding be that the piston of engine is located at the top dead centre of cylinder, lower dead center pair
What is answered is that the piston of engine is located at the lower dead center of cylinder.Exhaust valve lift refers to that exhaust valve is in the state opened, air inlet
Door lift refers to that inlet valve is in the state opened.In inlet valve lift, it is attached to be located at engine tope center in the piston of engine
Closely, i.e., the injection fuel oil in air intake duct 20 of air flue fuel injector 65 (preferably passes through heating in the oil spout period A of air flue fuel injector
Fuel oil), and fuel-injection pressure is less than or equal to 1MPa, occurs to dodge anxious boiling phenomenon and formed after fuel oil injection to dodge anxious Boiling Fuel Injection Spray,
Anxious Boiling Fuel Injection Spray is dodged as air-flow enters cylinder 10, forms uniform Weak mixture.In compression stroke, in in-cylinder direct-jet oil spout
In the oil spout period B of device, in-cylinder direct-jet fuel injector 73 is fired into cylinder 10 with the fuel injection pressure injection more than or equal to 20MPa
Oil, and injection time is less than or equal to 0.3ms, also, in interval 73 end of injection moment of in-cylinder direct-jet fuel injector, 0 crank angle degrees
To after 10 crank angle degrees, spark plug 50 is lighted a fire in plug ignition moment C.Wherein, the In-cylinder injector end of injection moment away from
Time interval from time of ignition is defined as Δ, and Δ is using crank angle as linear module.In addition, with reference to figure 4, air flue fuel injector 65
The oil spout period when can also be closed since inlet valve 80 spray fuel oil, until inlet valve 80 terminates spray after opening a period of time
Penetrate fuel oil.
To sum up, the lean-burn systems and method provided in this embodiment for spark-ignition engine, due in engine
Intake port injection it is heated after fuel oil, occur to dodge anxious boiling phenomenon when fuel oil being made to spray, rationally setting spraying enters gas
The mode of cylinder and time so that fuel oil, which enters in cylinder, forms mixed uniformly Weak mixture, and in engine compresses
The stroke later stage is big in in-cylinder injection injection pressure, and the fuel oil that injecting time is short, and lights a fire in due course so that around spark plug
The area in the overrich area of formation greatly reduces, and can realize stable burnup, thus reduces in the prior art due to spark plug
The content for the NOx that the overrich area of surrounding large area is formed in combustion so that the gas discharged out of cylinder need not be set
The catalytic converter specifically for NOx is set, also a save cost while fuel-economizing.In addition the reduction of overrich area area, and
Uniform Weak mixture and the burning stablized in cylinder, keep fuel oil burning more abundant, therefore significantly reduce particulate matter
Discharge.In addition, the present embodiment does not need use cost height and the piezo-electric crystal fuel injector sensitive to oil product, but use is big
The Conventional fuel injectors of bulk article, therefore further save cost.
Foregoing description is only the description to present pre-ferred embodiments, not to any restriction of the scope of the invention, this hair
Any change, the modification that the those of ordinary skill in bright field does according to the disclosure above content, belong to the protection of claims
Range.
Claims (14)
1. a kind of lean burn method for spark-ignition engine, which is characterized in that including：
The injection fuel oil at first heated fuel oil, then two air intake ducts being connect within the engine with cylinder dodges anxious boiling to be formed
Rise spraying；
And when spraying the fuel oil at the air intake duct of engine, the inlet valve of the engine is in open state always, or
The inlet valve of person, the engine were closed before this, and then the inlet valve of engine is in open state；
Also, a certain moment of fuel oil is sprayed at the air intake duct of engine, the piston of engine is located at air inlet top dead centre；
In the compression stroke of engine, in-cylinder direct-jet is carried out to fuel oil；And
It lights a fire when apart from in-cylinder injection fuel oil finish time, 0 crank angle degrees were to 10 crank angle degrees.
2. being used for the lean burn method of spark-ignition engine as described in claim 1, which is characterized in that the air inlet of engine
The fuel-injection pressure in road is less than or equal to 1MPa.
3. being used for the lean burn method of spark-ignition engine as described in claim 1, which is characterized in that after fuel Heating
Maximum temperature is 90 DEG C to 110 DEG C.
4. being used for the lean burn method of spark-ignition engine as described in claim 1, which is characterized in that the combustion of in-cylinder direct-jet
Oil spurts pressure is more than or equal to 20MPa, and is less than or equal to 150MPa, also, oil spout duration is more than or equal to 0.05ms, and be less than etc.
In 0.3ms.
5. a kind of lean-burn systems for spark-ignition engine, including an engine, engine includes at least one cylinder
And in-cylinder direct-jet fuel injector and the spark plug being arranged in each cylinder, which is characterized in that in-cylinder direct-jet fuel injector is used for
In in-cylinder injection fuel oil in the compression stroke of engine, fuel-injection pressure is more than or equal to 20MPa, and oil spout duration is less than etc.
In 0.3ms；Spark plug apart from in-cylinder direct-jet fuel injector when spraying fuel oil finish time 0 crank angle degrees to 10 crank angle degrees
Igniting.
6. being used for the lean-burn systems of spark-ignition engine as claimed in claim 5, which is characterized in that further include air intake duct
And air flue fuel injector, each cylinder are at least connected with an air intake duct, air flue fuel injector, gas are provided at least one air intake duct
Road fuel injector is used to spray fuel oil into air intake duct to form Weak mixture in cylinder.
7. being used for the lean-burn systems of spark-ignition engine as claimed in claim 6, which is characterized in that further include the first confession
Oil-piping and the first oily rail, one end of the first oil supply pipe are connect with air flue fuel injector, and the is provided on the first oil supply pipe
One oily rail.
8. being used for the lean-burn systems of spark-ignition engine as claimed in claim 6, which is characterized in that further include heating dress
It sets, air flue fuel injector is ejected through the fuel oil of heating devices heat into air intake duct.
9. being used for the lean-burn systems of spark-ignition engine as claimed in claim 6, which is characterized in that air flue fuel injector sprays
The maximum temperature for the fuel oil penetrated is 90 DEG C to 110 DEG C.
10. being used for the lean-burn systems of spark-ignition engine as claimed in claim 6, which is characterized in that each cylinder connects
Two air intake ducts are connect, and air flue fuel injector is both provided at each air intake duct.
11. being used for the lean-burn systems of spark-ignition engine as claimed in claim 6, which is characterized in that further include air inlet
Door, inlet valve are arranged between cylinder and air intake duct, and air flue fuel injector is arranged close to inlet valve.
12. as claimed in claim 6 be used for spark-ignition engine lean-burn systems, which is characterized in that engine into
The fuel-injection pressure of air flue is less than or equal to 1MPa.
13. being used for the lean-burn systems of spark-ignition engine as claimed in claim 5, which is characterized in that further include exhaust
Door, the cylinder have a combustion chamber, and in-cylinder direct-jet fuel injector and spark plug are arranged at the top of combustion chamber, and spark plug is close
Exhaust valve.
14. the lean-burn systems for spark-ignition engine as described in any one of claim 5 to 13, feature exist
In for in-cylinder direct-jet fuel injector in in-cylinder injection fuel oil, fuel-injection pressure is less than or equal to 150MPa, and oil spout duration is more than
Equal to 0.05ms.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710144104.3A CN108571392B (en) | 2017-03-10 | 2017-03-10 | Lean burn system and method for spark-ignition engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710144104.3A CN108571392B (en) | 2017-03-10 | 2017-03-10 | Lean burn system and method for spark-ignition engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN108571392A true CN108571392A (en) | 2018-09-25 |
| CN108571392B CN108571392B (en) | 2020-10-09 |
Family
ID=63578087
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710144104.3A Active CN108571392B (en) | 2017-03-10 | 2017-03-10 | Lean burn system and method for spark-ignition engine |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN108571392B (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110748918A (en) * | 2019-10-24 | 2020-02-04 | 南京航空航天大学 | Flash boiling type evaporation cavity flame stabilizer suitable for low temperature and low pressure |
| CN111042955A (en) * | 2018-10-12 | 2020-04-21 | 联合汽车电子有限公司 | Engine system and combustion method |
| CN112555017A (en) * | 2019-09-26 | 2021-03-26 | 联合汽车电子有限公司 | Lean combustion system, lean combustion engine and lean combustion method |
| EP3978743A4 (en) * | 2019-05-24 | 2022-06-15 | NISSAN MOTOR Co., Ltd. | Internal combustion engine control method and control device |
| CN115217615A (en) * | 2022-04-06 | 2022-10-21 | 广州汽车集团股份有限公司 | Scavenging device and scavenging method |
Citations (20)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5894832A (en) * | 1996-07-12 | 1999-04-20 | Hitachi America, Ltd., Research And Development Division | Cold start engine control apparatus and method |
| JP2000283007A (en) * | 1999-03-26 | 2000-10-10 | Honda Motor Co Ltd | Internal combustion engine |
| JP2004044453A (en) * | 2002-07-10 | 2004-02-12 | Toyota Motor Corp | Fuel injection control device for internal combustion engine |
| US20050066939A1 (en) * | 2003-08-08 | 2005-03-31 | Kosaku Shimada | Fuel supply system and fuel supply method for in-cylinder direct fuel injection engine |
| JP2005337104A (en) * | 2004-05-26 | 2005-12-08 | Nippon Soken Inc | Control device for internal combustion engine |
| JP2006161580A (en) * | 2004-12-02 | 2006-06-22 | Toyota Motor Corp | Internal combustion engine |
| JP2007255211A (en) * | 2006-03-20 | 2007-10-04 | Toyota Motor Corp | Control device of compression ignition internal combustion engine |
| JP2008106737A (en) * | 2006-09-25 | 2008-05-08 | Toyota Motor Corp | Premixed compression selfignition gasoline engine |
| JP2008138688A (en) * | 2008-01-28 | 2008-06-19 | Toyota Motor Corp | Fuel supply device for internal combustion engine |
| CN101289964A (en) * | 2007-04-20 | 2008-10-22 | 日产自动车株式会社 | Internal combustion engine and combustion method of the same |
| CN102159820A (en) * | 2007-08-09 | 2011-08-17 | 丰田自动车株式会社 | Fuel injection control system and fuel injection control method for spark-ignition internal combustion engine |
| WO2011118030A1 (en) * | 2010-03-26 | 2011-09-29 | トヨタ自動車株式会社 | Combustion controller for internal combustion engine |
| JP2011202568A (en) * | 2010-03-25 | 2011-10-13 | Mitsubishi Motors Corp | Fuel injection control device for internal combustion engine |
| WO2012014288A1 (en) * | 2010-07-27 | 2012-02-02 | トヨタ自動車株式会社 | Internal combustion engine controller |
| CN102650243A (en) * | 2011-02-24 | 2012-08-29 | 马自达汽车株式会社 | Control device and method of spark-ignition gasoline engine |
| CN102650239A (en) * | 2011-02-24 | 2012-08-29 | 马自达汽车株式会社 | Control device of spark-ignition gasoline engine |
| JP2012207631A (en) * | 2011-03-30 | 2012-10-25 | Mazda Motor Corp | Control device of spark ignition type gasoline engine |
| US20120279472A1 (en) * | 2011-04-13 | 2012-11-08 | Thor Windbergs | injection device and internal combustion engine |
| JP2013213509A (en) * | 2013-07-25 | 2013-10-17 | Toyota Motor Corp | Control device of internal combustion engine |
| US20170314499A1 (en) * | 2016-04-27 | 2017-11-02 | Toyota Jidosha Kabushiki Kaisha | Control apparatus for internal combustion engine |
-
2017
- 2017-03-10 CN CN201710144104.3A patent/CN108571392B/en active Active
Patent Citations (20)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5894832A (en) * | 1996-07-12 | 1999-04-20 | Hitachi America, Ltd., Research And Development Division | Cold start engine control apparatus and method |
| JP2000283007A (en) * | 1999-03-26 | 2000-10-10 | Honda Motor Co Ltd | Internal combustion engine |
| JP2004044453A (en) * | 2002-07-10 | 2004-02-12 | Toyota Motor Corp | Fuel injection control device for internal combustion engine |
| US20050066939A1 (en) * | 2003-08-08 | 2005-03-31 | Kosaku Shimada | Fuel supply system and fuel supply method for in-cylinder direct fuel injection engine |
| JP2005337104A (en) * | 2004-05-26 | 2005-12-08 | Nippon Soken Inc | Control device for internal combustion engine |
| JP2006161580A (en) * | 2004-12-02 | 2006-06-22 | Toyota Motor Corp | Internal combustion engine |
| JP2007255211A (en) * | 2006-03-20 | 2007-10-04 | Toyota Motor Corp | Control device of compression ignition internal combustion engine |
| JP2008106737A (en) * | 2006-09-25 | 2008-05-08 | Toyota Motor Corp | Premixed compression selfignition gasoline engine |
| CN101289964A (en) * | 2007-04-20 | 2008-10-22 | 日产自动车株式会社 | Internal combustion engine and combustion method of the same |
| CN102159820A (en) * | 2007-08-09 | 2011-08-17 | 丰田自动车株式会社 | Fuel injection control system and fuel injection control method for spark-ignition internal combustion engine |
| JP2008138688A (en) * | 2008-01-28 | 2008-06-19 | Toyota Motor Corp | Fuel supply device for internal combustion engine |
| JP2011202568A (en) * | 2010-03-25 | 2011-10-13 | Mitsubishi Motors Corp | Fuel injection control device for internal combustion engine |
| WO2011118030A1 (en) * | 2010-03-26 | 2011-09-29 | トヨタ自動車株式会社 | Combustion controller for internal combustion engine |
| WO2012014288A1 (en) * | 2010-07-27 | 2012-02-02 | トヨタ自動車株式会社 | Internal combustion engine controller |
| CN102650243A (en) * | 2011-02-24 | 2012-08-29 | 马自达汽车株式会社 | Control device and method of spark-ignition gasoline engine |
| CN102650239A (en) * | 2011-02-24 | 2012-08-29 | 马自达汽车株式会社 | Control device of spark-ignition gasoline engine |
| JP2012207631A (en) * | 2011-03-30 | 2012-10-25 | Mazda Motor Corp | Control device of spark ignition type gasoline engine |
| US20120279472A1 (en) * | 2011-04-13 | 2012-11-08 | Thor Windbergs | injection device and internal combustion engine |
| JP2013213509A (en) * | 2013-07-25 | 2013-10-17 | Toyota Motor Corp | Control device of internal combustion engine |
| US20170314499A1 (en) * | 2016-04-27 | 2017-11-02 | Toyota Jidosha Kabushiki Kaisha | Control apparatus for internal combustion engine |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111042955A (en) * | 2018-10-12 | 2020-04-21 | 联合汽车电子有限公司 | Engine system and combustion method |
| EP3978743A4 (en) * | 2019-05-24 | 2022-06-15 | NISSAN MOTOR Co., Ltd. | Internal combustion engine control method and control device |
| CN112555017A (en) * | 2019-09-26 | 2021-03-26 | 联合汽车电子有限公司 | Lean combustion system, lean combustion engine and lean combustion method |
| CN110748918A (en) * | 2019-10-24 | 2020-02-04 | 南京航空航天大学 | Flash boiling type evaporation cavity flame stabilizer suitable for low temperature and low pressure |
| CN110748918B (en) * | 2019-10-24 | 2024-03-29 | 南京航空航天大学 | Flash boiling type evaporation cavity flame stabilizer applicable to low temperature and low pressure |
| CN115217615A (en) * | 2022-04-06 | 2022-10-21 | 广州汽车集团股份有限公司 | Scavenging device and scavenging method |
| CN115217615B (en) * | 2022-04-06 | 2023-08-15 | 广州汽车集团股份有限公司 | Scavenging device and scavenging method |
Also Published As
| Publication number | Publication date |
|---|---|
| CN108571392B (en) | 2020-10-09 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| EP2606215B1 (en) | Internal combustion engine provided with a stoichiometric mixture of two fuels with a compression ignition | |
| CN108571392A (en) | Lean-burn systems and method for spark-ignition engine | |
| CN109296446B (en) | Diesel micro-injection ignition natural gas engine combustion organization method with natural gas high-low pressure mixed injection and pre-combustion chamber | |
| WO2012000307A1 (en) | Multi-fuel pre-mixed combustion system of internal combustion engine | |
| CN109441626A (en) | A kind of dual fuel engine and its burning tissues method using major-minor fuel injector and manifold multi-injection | |
| US20190170077A1 (en) | Combustion control method and combustion control system with variable excess air coefficient for gasoline engine | |
| CN114320572A (en) | Multi-combustion-mode ammonia fuel engine and control method thereof | |
| CN108561233A (en) | A kind of diesel/natural gas dual-fuel engine emission control strategy | |
| CN113006928B (en) | Engine with precombustion chamber and working mode thereof | |
| CN105673281B (en) | In a kind of gas/liquid double fuel cylinder/cylinder outer pair of injection apparatus and control method | |
| CN111197532A (en) | Hydrogen/methanol composite fuel engine | |
| CN101907030A (en) | Composite homogeneity compression-ignition engine based on fuel real-time design and jet management | |
| CN102226426A (en) | Dual-fuel composite homogenous charge compression ignition combustion system based on activation heat atmosphere | |
| CN110821661B (en) | Dual-fuel compression-ignition four-stroke engine based on reformed gas and combustion control method | |
| CN109236478B (en) | Combustion organization method of dual-fuel engine adopting high-pressure natural gas injection valve | |
| CN110145405A (en) | The double injected petrol lean-combustion engines of perforated plate type atomizer | |
| CN107939517B (en) | Jet ignition-based engine ultrahigh compression ratio combustion control device and method | |
| CN110953067A (en) | Engine and double-jet combustion method thereof | |
| CN102996223A (en) | Premixed combustion system of diesel engine | |
| CN110821638B (en) | Ignition chamber type engine with high-energy ignition fuel and control method thereof | |
| CN202300664U (en) | Fuel feed system of diesel oil/butanol low-temperature combustion dual-fuel engine | |
| CN110821653A (en) | Dual-fuel ignition chamber type four-stroke engine based on reformed gas and combustion control method | |
| CN205089489U (en) | Marine diesel's air intake system | |
| CN101929364A (en) | Diffusion combustion method for knock-resisting compression ignition of equivalence-ratio gasoline direct injection engine | |
| CN105257431A (en) | Air intake system of marine diesel engine |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |