CN109441626A - A kind of dual fuel engine and its burning tissues method using major-minor fuel injector and manifold multi-injection - Google Patents
A kind of dual fuel engine and its burning tissues method using major-minor fuel injector and manifold multi-injection Download PDFInfo
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- CN109441626A CN109441626A CN201811017333.XA CN201811017333A CN109441626A CN 109441626 A CN109441626 A CN 109441626A CN 201811017333 A CN201811017333 A CN 201811017333A CN 109441626 A CN109441626 A CN 109441626A
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- 239000000446 fuel Substances 0.000 title claims abstract description 178
- 239000007924 injection Substances 0.000 title claims abstract description 123
- 238000002347 injection Methods 0.000 title claims abstract description 123
- 238000000034 method Methods 0.000 title claims abstract description 19
- 230000009977 dual effect Effects 0.000 title claims description 38
- 241001347978 Major minor Species 0.000 title claims description 21
- 238000002485 combustion reaction Methods 0.000 claims abstract description 50
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 claims abstract description 44
- 239000002283 diesel fuel Substances 0.000 claims abstract description 40
- 239000003345 natural gas Substances 0.000 claims abstract description 22
- 239000002737 fuel gas Substances 0.000 claims description 28
- 238000007906 compression Methods 0.000 claims description 25
- 230000006835 compression Effects 0.000 claims description 23
- 239000007921 spray Substances 0.000 claims description 19
- 239000000567 combustion gas Substances 0.000 claims description 13
- 238000005507 spraying Methods 0.000 claims description 9
- 230000006698 induction Effects 0.000 claims description 7
- 230000002093 peripheral effect Effects 0.000 claims description 3
- 239000007789 gas Substances 0.000 abstract description 28
- 239000000203 mixture Substances 0.000 abstract description 10
- 230000000694 effects Effects 0.000 abstract description 5
- 230000008520 organization Effects 0.000 abstract 1
- 239000003921 oil Substances 0.000 description 8
- 239000008246 gaseous mixture Substances 0.000 description 5
- 238000010586 diagram Methods 0.000 description 4
- 238000007599 discharging Methods 0.000 description 3
- 230000002269 spontaneous effect Effects 0.000 description 3
- 238000000889 atomisation Methods 0.000 description 2
- 239000000295 fuel oil Substances 0.000 description 2
- 230000001535 kindling effect Effects 0.000 description 2
- 238000006467 substitution reaction Methods 0.000 description 2
- 240000002853 Nelumbo nucifera Species 0.000 description 1
- 235000006508 Nelumbo nucifera Nutrition 0.000 description 1
- 235000006510 Nelumbo pentapetala Nutrition 0.000 description 1
- 230000003213 activating effect Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 239000010727 cylinder oil Substances 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 239000008187 granular material Substances 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- TVMXDCGIABBOFY-UHFFFAOYSA-N octane Chemical compound CCCCCCCC TVMXDCGIABBOFY-UHFFFAOYSA-N 0.000 description 1
- 239000003208 petroleum Substances 0.000 description 1
- 238000011160 research Methods 0.000 description 1
- 238000013517 stratification Methods 0.000 description 1
- 238000012360 testing method Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B69/00—Internal-combustion engines convertible into other combustion-engine type, not provided for in F02B11/00; Internal-combustion engines of different types characterised by constructions facilitating use of same main engine-parts in different types
- F02B69/02—Internal-combustion engines convertible into other combustion-engine type, not provided for in F02B11/00; Internal-combustion engines of different types characterised by constructions facilitating use of same main engine-parts in different types for different fuel types, other than engines indifferent to fuel consumed, e.g. convertible from light to heavy fuel
- F02B69/04—Internal-combustion engines convertible into other combustion-engine type, not provided for in F02B11/00; Internal-combustion engines of different types characterised by constructions facilitating use of same main engine-parts in different types for different fuel types, other than engines indifferent to fuel consumed, e.g. convertible from light to heavy fuel for gaseous and non-gaseous fuels
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D19/00—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
- F02D19/06—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed
- F02D19/0639—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed characterised by the type of fuels
- F02D19/0642—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed characterised by the type of fuels at least one fuel being gaseous, the other fuels being gaseous or liquid at standard conditions
- F02D19/0647—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed characterised by the type of fuels at least one fuel being gaseous, the other fuels being gaseous or liquid at standard conditions the gaseous fuel being liquefied petroleum gas [LPG], liquefied natural gas [LNG], compressed natural gas [CNG] or dimethyl ether [DME]
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D19/00—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
- F02D19/06—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed
- F02D19/0663—Details on the fuel supply system, e.g. tanks, valves, pipes, pumps, rails, injectors or mixers
- F02D19/0686—Injectors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D19/00—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
- F02D19/06—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed
- F02D19/08—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed simultaneously using pluralities of fuels
- F02D19/081—Adjusting the fuel composition or mixing ratio; Transitioning from one fuel to the other
-
- 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
-
- 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
- Y02T10/30—Use of alternative fuels, e.g. biofuels
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Oil, Petroleum & Natural Gas (AREA)
- Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
- Combustion Methods Of Internal-Combustion Engines (AREA)
Abstract
本发明属于内燃机燃烧技术领域，具体涉及一种采用主副喷油器和歧管多次喷射的双燃料发动机及其燃烧组织方法。双燃料发动机包括活塞，气缸套，气缸盖，主、副喷油器，歧管低压燃气喷射装置等；主喷油器安装在气缸盖中心，改变其喷油脉宽可控制低负荷时柴油喷射比例；副喷油器倾斜安装在气缸盖上，在中高负荷时微喷柴油，在上止点附近柴油自燃后引燃天然气；歧管低压燃气喷射阀安装在每缸进气歧管上，中高负荷时，控制低压喷气阀的喷射次数和正时，使缸内形成合理的混合气浓度分布。本发明通过柴油引燃保证不同工况下点火稳定性，不同工况下采用不同的油气喷射策略，使缸内实现油气合理分布以达到良好的燃烧效果，从而提升发动机的经济性和排放性。
The invention belongs to the technical field of combustion of internal combustion engines, and in particular relates to a dual-fuel engine using main and auxiliary fuel injectors and manifold injections for multiple times and a combustion organization method thereof. The dual-fuel engine includes piston, cylinder liner, cylinder head, main and auxiliary injectors, manifold low-pressure gas injection device, etc. The main injector is installed in the center of the cylinder head, changing its injection pulse width can control diesel injection at low load Proportional; the auxiliary fuel injector is installed obliquely on the cylinder head, micro-injecting diesel oil at medium and high loads, and igniting natural gas after the diesel self-ignition near the top dead center; the manifold low-pressure gas injection valve is installed on the intake manifold of each cylinder, and the medium-high When under load, the injection times and timing of the low-pressure injection valve are controlled to form a reasonable mixture concentration distribution in the cylinder. The invention ensures ignition stability under different working conditions through diesel ignition, and adopts different oil and gas injection strategies under different working conditions to achieve reasonable distribution of oil and gas in the cylinder to achieve good combustion effect, thereby improving the economy and emission of the engine.
Description
Technical field
The invention belongs to combustion in IC engine technical fields, and in particular to a kind of to use major-minor fuel injector and manifold multi-injection
Dual fuel engine and its burning tissues method.
Background technique
Diesel/natural gas dual-fuel engine can run two kinds of fuel modes, and economy is high, and recondition expense is generally compared directly
The cost for connecing using gas engine fuel is low.Meanwhile double fuel biggest advantage is that NOx and PM discharge can be reduced simultaneously,
This is difficult to realize in traditional diesel engine.Correlation test shows dual fuel engine NOx emission lower than diesel engine water
It is flat, 50% or so can be reduced in middle-low load, while the granular material discharged comparable diesel engine of dual fuel engine reduces nearly 70%,
Effect is than more significant.
On the other hand, although the dual fuel engine thermal efficiency is higher than spark ignition engine, it is lower than diesel engine.With fire
Spark ignition formula engine is compared, diesel oil spontaneous combustion be easily achieved multiple spot kindling, mixture combustion is more rapid, natural gas allow compared with
It works under the conditions of big compression ratio, the thermal efficiency of engine can be improved.But due to gas-duct jetting natural gas, engine inflation effect
Rate reduces, therefore the thermal efficiency of dual fuel engine is lower than diesel engine level on the whole, and substantially and diesel oil in big load
Machine is suitable.The substitution ratio of NG of dual fuel engine will affect in-cylinder combustion situation, especially in middle-low load, higher day
Right gas substitution rate will lead to burning and deteriorate, or even phenomena such as engine fire, cyclical variations aggravation occurs.While and spark plug point
Combustion natural gas engine is compared, since distribution is extensive in the combustion chamber as ignition source for diesel oil, natural gas kindling
Energy increases, and the combustion stability and burn rate that improve natural gas improve the dynamic property and the thermal efficiency of engine in turn.
In terms of improving dual fuel engine injection mode, some patents adjust distributive value such as by setting preset value
CN105020073A, the patent realize the row of reduction under different load in the controls by default distributive value and injection timing
Put, improve the purpose of burning；The fuel injection manner that some patents may take dual fuel engine is summarized such as
CN106870186A, the patent realize different combustion systems by the combination of different fuel spray regime.It burns improving
System aspects, some patents spray the fuel of different octane by major-minor nozzle to realize homogeneous Premixed combustion such as
CN102996223A, the patent provides a kind of premixed combustion system of diesel engine, it is ensured that the higher thermal efficiency；Some patents
Research such as CN204402678U, combustion system involved in the patent have been carried out to the combustion system comprising switchable type fuel injector
Including covering fuel supply system, operating mode is changed by switchable type fuel injector and corresponding control system, to realize not more
With the switching of combustion mode under operating condition.And which kind of operating condition is these patents do not consider under using which kind of combustion mode, how in master
Indoor tissue mixed Daqu and efficient low-discharging burning are fired, and does not propose how to improve engine stable point under gas mode
The problems such as fiery.
Summary of the invention
The purpose of the present invention is to provide it is a kind of have preferable dynamic property, economy and emission performance using major-minor fuel injector and
The dual fuel engine of manifold multi-injection.
A kind of dual fuel engine using major-minor fuel injector and manifold multi-injection, including piston, cylinder jacket, cylinder
Lid, secondary fuel injector, main fuel injector, intake valve, manifold low-pressure fuel gas injection apparatus, air intake duct, combustion chamber；Combustion chamber is by piston
Surface, cylinder jacket peripheral wall and cylinder head lower surface composition；Major-minor fuel injector is mounted in cylinder head, and main fuel injector is located at cylinder
Lid center, axis are overlapped with cylinder-bore axis, and secondary fuel injector is mounted on the right side of cylinder head, axis and cylinder head lower surface institute angulation
Degree is 30-70 °；Manifold low-pressure fuel gas injection valve is mounted in every cylinder inlet manifold, induction stroke exhaust valve closure to intake valve
Down periods are to in-cylinder fuel supply.
The main fuel injector is porous big flow fuel injector, and secondary fuel injector is small flow fuel injector, and two fuel injectors are mutual
It works independently, the maximum stream flow of secondary fuel injector only has the 1-5% of the maximum stream flow of main fuel injector.
The main fuel injector nozzle hole number is 6-8, and multiple spray orifices of secondary fuel injector are arranged in the side of nozzle, is sprayed more
A oil beam.
The combustion chamber uses hemispherical dome structure.
The object of the invention is also to provide a kind of dual fuel engines using major-minor fuel injector and manifold multi-injection
Burning tissues method.
A kind of dual fuel engine burning tissues method using major-minor fuel injector and manifold multi-injection, feature exist
In including the following steps:
Step 1 judges engine load, selects engine working mode；
Step 2, intake process；
Step 3, combustion gas compression process；
Step 4, work by combustion process；
Step 5, exhaust process.
The step 1 specifically includes:
One, when underload, that is, load is lower than 15%, dual fuel engine uses diesel oil operating mode, and fuel injector selects main jet
Oily device；
Two, middle load meets at 15% -70%, and dual fuel engine uses natural gas operating mode, fuel injector choosing
With secondary fuel injector；
Three, when high load capacity, that is, load is greater than 70%, dual fuel engine is switched to homogeneous combustion gas operating mode, at this point, discrimination
Pipe low-pressure fuel gas injection valve and secondary fuel injector work together.
The step 2 specifically includes:
When underload one, when, that is, load is lower than 15%, main fuel injector before the top dead centre of compression stroke end within the scope of 30 DEG C of A to
Cylinder injection diesel oil；
Two, when 15-50% load, manifold low-pressure fuel gas injection valve use single injection event, injection timing be valve opening most
Before and after high-lift within the scope of 10 DEG C of A, for secondary fuel injector using spraying twice, first time injection timing is 70 DEG C of A before compression top center,
Second of injection timing is within the scope of 0-30 DEG C of A before compression top center, diesel injection ratio accounts for entirely circulation combustion under 100% load
The 1-5% of doses ratio；
Three, when 50-70% load, for manifold low-pressure fuel gas injection valve using spraying twice, first time injection timing is exhaust
After valve is closed within the scope of 0-30 DEG C of A, second of injection timing is within the scope of 10-30 DEG C of A after IO Intake Valve Opens maximum lift, pair sprays
For oily device using spraying twice, first time injection timing is 70 DEG C of A before compression top center, and second of injection timing is compression top center
Within the scope of preceding 0-30 DEG C of A, diesel injection ratio accounts for the 1-5% of entire circulating fuel amount ratio under 100% load；
Four, when high load capacity load is greater than 70%, manifold low-pressure fuel gas injection valve uses single injection event, and injection timing is being vented
After valve is closed within the scope of 0-30 DEG C of A, secondary fuel injector uses single injection event, before compression top center within the scope of 5-15 DEG C of A, into cylinder
Diesel oil is sprayed into, injection diesel fuel ratio accounts for the 1-5% of entire circulating fuel amount ratio under 100% load.
The beneficial effects of the present invention are:
The present invention is by making reasonable matched design to dual fuel engine combustion mode and oil-gas jetting strategy, not
With different influence factors is considered under operating condition, engine is made to obtain preferable comprehensive performance；Guarantee different works by diesel oil ignited
The Ignition Stability of natural gas under condition uses different sprays by low-pressure fuel gas injection valve and major-minor fuel injector under different operating conditions
Number and injection pulse width are penetrated, forms the gas concentration gradient distribution of reasonable scale in the combustion chamber, to realize that oil gas is quick
Efficient low-discharging burning, accelerates flame propagation velocity, shortens burning time, is conducive to improve burning quality, reduces delivery temperature,
Dual fuel engine can be improved to catch fire and knock problem.
Detailed description of the invention
Fig. 1 is the specific layout drawing of dual-fuel engine combustion system in embodiment of the present invention；
Fig. 2 is that main fuel injector sprays diesel oil atomization schematic diagram；
Petroleum distribution schematic diagram in cylinder when Fig. 3 is middle load；
Concentration of natural gas distribution schematic diagram in cylinder when Fig. 4 is high load capacity.
Specific embodiment
The present invention is described further with reference to the accompanying drawing:
It as shown in Fig. 1, is the specific layout drawing of dual-fuel engine combustion system in embodiment of the present invention, using master
The dual-fuel engine combustion system structure of secondary fuel injector and manifold multi-injection includes: piston 1, cylinder jacket 2, cylinder head 3, pair
Fuel injector 4, main fuel injector 5, intake valve 6, manifold low-pressure fuel gas injection apparatus 7, air intake duct 8, combustion chamber 9.Combustion chamber is by piston
Upper surface, cylinder jacket peripheral wall and cylinder head lower surface composition；Major-minor fuel injector is mounted in cylinder head, and main fuel injector is located at gas
Cylinder cap center, axis are overlapped with cylinder-bore axis, and secondary fuel injector is mounted on the right side of cylinder head, axis and cylinder head lower surface institute at
Angle is 30-70 °；Low-pressure fuel gas injection valve is mounted in every cylinder inlet manifold, induction stroke exhaust valve closure to intake valve close
To in-cylinder fuel supply during closing.
The burning tissues method is suitable for four stroke natural gas engines, and every circulation includes induction stroke, pressure
Contracting stroke, work by combustion stroke and exhaust stroke.When underload, that is, load be lower than 15% when, dual fuel engine is in diesel oil
The problems such as operating mode, natural gas easily catches fire in underload because of lean burn, so there was only main fuel injector work at this time,
To cylinder injection diesel oil within the scope of 30 DEG C of A before the top dead centre of compression stroke end, diesel oil atomization schematic diagram is as shown in Fig. 2, porous spray
Mouth can make diesel oil form multiple concentration ranges in cylinder, and atomizing effect is also preferable, and the amount of diesel injection is less, and burning is more
Slowly, air is sufficient, and burning sufficiently, is able to achieve preferable emission performance.
When middle load, that is, load is when being 15%-70%, dual fuel engine is switched to combustion gas operating mode, but negative in difference
It is layered again using the concentration of natural gas of different scale gradient under lotus, when 15-50% load after induction stroke exhaust valve closure, low pressure
Fuel gas injection valve starts single injection event, and injection timing is the day sprayed at this time before and after valve opening maximum lift within the scope of 10 DEG C of A
Right gas can form the concentration of natural gas layering of large scale in cylinder；When 50-70% load, low-pressure fuel gas injection valve is using twice
Injection, first time injection timing is within the scope of 0-30 DEG C of A after exhaust valve closure, second of injection timing is that IO Intake Valve Opens are maximum
After lift within the scope of 10-30 DEG C of A, the gas of injection forms more uniform lean mixture in cylinder for the first time, second of injection
Dilute concentration of natural gas distribution under gas integrated distribution is dense on combustion chamber upper layer, formation, secondary fuel injector uses to be sprayed twice, the
Injection timing is 70 DEG C of A before compression top center, and second of injection timing is bavin before compression top center within the scope of 0-30 DEG C of A
Oil spurts ratio accounts for the 1-5% of entire circulating fuel amount ratio under 100% load, and diesel oil is formed in multiple concentration after spraying into cylinder
The heart, and with natural gas that induction stroke sprays into be collectively formed it is upper it is dense under the distribution of dilute multicenter mixture strength distribution such as
Shown in Fig. 3, while the diesel oil of secondary fuel injector injection forms multiple ignition centers to realize gaseous mixture stable ignition, in turn in cylinder
It realizes oil gas rapidly and efficiently low emissions combustion, accelerates flame propagation velocity, shorten after burning period.
When high load capacity, that is, load be greater than 70% when, dual fuel engine is switched to homogeneous combustion gas operating mode, at this point, low pressure
Fuel gas injection valve and secondary fuel injector work together, and required combustion gas is more when due to high load capacity, allow also for high load capacity burning
Temperature height, quick heating, in order to reach good emission effect, fuel gas injection valve uses single injection event, and injection timing is in exhaust valve
After closing within the scope of 0-30 DEG C of A, will form the gaseous mixture for being relatively in such cylinder as shown in figure 4, but natural gas ignition point it is higher
It is unable to spontaneous combustion, it is therefore desirable to which the secondary micro- spray of fuel injector is diesel oil ignited, and secondary fuel injector uses single injection event, the 5-15 before compression top center
Within the scope of DEG C A, the 1-5% that diesel injection ratio accounts for entire circulating fuel amount ratio under 100% load, diesel oil meeting are sprayed into cylinder
It forms multiple ignition points gaseous mixture in cylinder that ignites and realizes homogeneous combustion, the discharge of NOx can be effectively reduced.
The present invention provides a kind of dual fuel engine burning tissues method using major-minor fuel injector and manifold multi-injection,
The dual-fuel engine combustion system includes that piston, cylinder jacket, cylinder head, main fuel injector, secondary fuel injector and manifold are low
Compression ignition gas spraying device etc..Main fuel injector is mounted on cylinder head center, and diesel oil sprays when controlling underload by changing fuel injection pulsewidth
Penetrate ratio；Secondary fuel injector is tiltedly mounted in cylinder head, micro- spray diesel oil in middle high load capacity, after near top dead center diesel oil spontaneous combustion
Ignite natural gas；Low-pressure fuel gas injection valve is mounted in every cylinder inlet manifold, when middle high load capacity, passes through control low pressure snifting valve
Injecting times and timing make to form reasonable mixture strength distribution in cylinder.The present invention guarantees different operating conditions by diesel oil ignited
Under Ignition Stability, by using different oil-gas jetting strategies under different operating conditions, make to realize in cylinder oil gas reasonable layout with
Reach good combustion efficiency, to promote the economy and emission performance of engine.
A kind of dual fuel engine burning tissues method using major-minor fuel injector and manifold multi-injection, structure packet
Include: piston 1, cylinder jacket 2, cylinder head 3, secondary fuel injector 4, main fuel injector 5, intake valve 6, manifold low-pressure fuel gas injection apparatus 7, into
Air flue 8 and combustion chamber 9.Dual fuel engine uses duel fuel injector structure, i.e., secondary fuel injector 4 and main fuel injector 5, and described two
A fuel injector works independently from each other, and the maximum stream flow of secondary fuel injector 4 is much smaller than the maximum stream flow of main fuel injector 5, secondary fuel injector 4
Maximum stream flow only has the 1-5% of the maximum stream flow of main fuel injector 5, and secondary fuel injector 4 work in dual fuel engine combustion gas mode,
It does not work under fuel oil mode；Main fuel injector 5 is the work under the pure diesel oil mould and combustion gas mode underload of dual fuel engine
Make；Main fuel injector is mounted on cylinder head center, and secondary fuel injector is tiltedly mounted on the right side of cylinder head, and multiple spray orifices of secondary fuel injector
It is arranged in the side of nozzle, multiple oily beams of ejection；Combustion chamber has hemispherical configuration, and fuel injector sprays more under gas mode
A oil beam is uniformly distributed in hemispherical combustion chamber, so as to shorten flame travel；Manifold low-pressure fuel gas injection valve peace
In the inlet manifold of every cylinder, combustion gas multi-injection can be realized in entire intake process in gas mode；Underload
When (< 15%), engine is in diesel oil operating mode, and diesel oil is mainly sprayed into cylinder from main fuel injector at this time, at this time secondary oil spout
Device does not work, and main fuel injector uses single injection event, and injection timing is within the scope of 10-30 DEG C of A before compression top center；Moderate duty
When, engine can switch to combustion gas operating mode, and secondary fuel injector and low-pressure fuel gas injection valve cooperate, low in 15-50%
Using the concentration of natural gas gradient distribution of top-down large scale when load, manifold low-pressure fuel gas injection valve single injection event,
Injection timing is within the scope of the 10 DEG C of A in valve opening maximum lift front and back；Top-down smaller scale is used when 50-70% load
Concentration of natural gas gradient distribution, for manifold low-pressure fuel gas injection valve using spraying twice, first time injection timing is induction stroke row
After air valve is closed within the scope of 0-30 DEG C of A, the gas of injection forms more uniform lean mixture in cylinder for the first time, second of injection
Timing is realized within the scope of 10-30 DEG C of A after IO Intake Valve Opens maximum lift, to pass through the ratio of fuel injection twice that controls and timing
The concentration stratification of natural gas in cylinder；Secondary fuel injector may be implemented to spray twice, and first time injection timing is 70 before compression top center
DEG C A, the diesel oil sprayed only provide activating component and gaseous mixture, second of injection timing in the cylinder that can not individually ignite into cylinder
Within the scope of 0-30 DEG C of A, to have sprayed ignition action for the second time before compression top center, the diesel oil control sprayed twice is transported in engine
The 1-5% of row circulating fuel amount entire in the case where diesel fuel mode accounts for 100% load, diesel injection can be formed in multiple igniting in cylinder
The heart, by the control to low-pressure fuel gas injection valve injecting times and timing, realizes different scale to realize stable ignition in cylinder
Mixture strength distribution with realize efficient low-discharging burn；When high load capacity (> 70%), engine is switched to homogeneous combustion gas work
Mode makes to be formed in cylinder more uniform at this time mainly by low-pressure fuel gas injection valve to in-cylinder fuel supply by control jet timing
Gaseous mixture, and it is diesel oil ignited by micro- spray, and low-pressure fuel gas injection valve uses single injection event, injection timing 0- after exhaust valve closure
Within the scope of 30 DEG C of A, secondary fuel injector uses single injection event, and injection timing is diesel pilot before compression top center within the scope of 5-15 DEG C of A
Injection proportion accounts for the 1-5% of entire circulating fuel amount ratio under pure 100% load of diesel fuel mode.Combustion gas mould may be implemented in engine
The flexible switching of formula and fuel oil mode, and by using different oil-gas jetting strategies, make to be able to achieve in cylinder under different operating conditions
Oil gas reasonable layout is to reach good combustion efficiency, to promote the economy and emission performance of engine.
Main fuel injector uses big flow multiple orifice nozzle, and main fuel injector axis is overlapped with cylinder-bore axis, nozzle hole number 6-8
A, main fuel injector works under the starting of pure diesel fuel mode, idling, warming-up and gas mode underload, high in gas mode
It does not work under load；Fuel injection amount is few when gas mode underload, and to guarantee Ignition Stability, diesel fuel ratio is opposite in fuel
It is higher, using main fuel injector to cylinder injection diesel oil, the diesel oil that sprays at this time while there is the dual work to ignite with work by combustion
With.
Secondary fuel injector uses small flow multiple orifice nozzle, and spray orifice was distributed in the side of central axis section, secondary oil spout
Device is tiltedly mounted on the right side of cylinder head, and axis and cylinder head lower surface angulation are 30-70 °, and secondary fuel injector is in gas mode
It works under middle high load capacity, the diesel oil of secondary fuel injector injection, which mainly serves, to ignite, in diesel fuel mode and gas mode underload
It stops working.
Combustion chamber uses hemispherical combustion chamber, can shorten flame travel, and stronger squish flow can be improved compression
The turbulence intensity of near top dead center is conducive to air-fuel mixture process and burning.
Claims (7)
1. a kind of dual fuel engine using major-minor fuel injector and manifold multi-injection, including piston, cylinder jacket, cylinder head,
Secondary fuel injector, main fuel injector, intake valve, manifold low-pressure fuel gas injection apparatus, air intake duct, combustion chamber；It is characterized by: combustion chamber
It is made of piston upper surface, cylinder jacket peripheral wall and cylinder head lower surface；Major-minor fuel injector is mounted in cylinder head, main fuel injector
Positioned at cylinder head center, axis is overlapped with cylinder-bore axis, and secondary fuel injector is mounted on the right side of cylinder head, axis and cylinder head following table
Face angulation is 30-70 °；Manifold low-pressure fuel gas injection valve is mounted in every cylinder inlet manifold, induction stroke exhaust valve closure
To the intake valve down periods to in-cylinder fuel supply.
2. a kind of dual fuel engine using major-minor fuel injector and manifold multi-injection according to claim 1, feature
Be: the main fuel injector is porous big flow fuel injector, and secondary fuel injector is small flow fuel injector, and two fuel injectors are mutually indepedent
Work, the maximum stream flow of secondary fuel injector only have the 1-5% of the maximum stream flow of main fuel injector.
3. a kind of dual fuel engine using major-minor fuel injector and manifold multi-injection according to claim 1, feature
Be: the main fuel injector nozzle hole number is 6-8, and multiple spray orifices of secondary fuel injector are arranged in the side of nozzle, is sprayed multiple
Oily beam.
4. a kind of dual fuel engine using major-minor fuel injector and manifold multi-injection according to claim 1, feature
Be: the combustion chamber uses hemispherical dome structure.
5. a kind of dual fuel engine burning tissues method using major-minor fuel injector and manifold multi-injection, which is characterized in that
Include the following steps:
Step 1 judges engine load, selects engine working mode；
Step 2, intake process；
Step 3, combustion gas compression process；
Step 4, work by combustion process；
Step 5, exhaust process.
6. a kind of dual fuel engine burning tissues using major-minor fuel injector and manifold multi-injection according to claim 5
Method, which is characterized in that the step 1 specifically includes:
One, when underload, that is, load is lower than 15%, dual fuel engine uses diesel oil operating mode, and fuel injector selects main jet oil
Device；
Two, middle load meets at 15% -70%, and dual fuel engine uses natural gas operating mode, and fuel injector is selected secondary
Fuel injector；
Three, when high load capacity, that is, load is greater than 70%, dual fuel engine is switched to homogeneous combustion gas operating mode, at this point, manifold is low
Fuel gas injection valve and secondary fuel injector is pressed to work together.
7. a kind of dual fuel engine burning tissues using major-minor fuel injector and manifold multi-injection according to claim 5
Method, which is characterized in that the step 2 specifically includes:
When underload one, when, that is, load is lower than 15%, main fuel injector is before the top dead centre of compression stroke end within the scope of 30 °C of A into cylinder
Spray diesel oil；
Two, when 15-50% load, manifold low-pressure fuel gas injection valve uses single injection event, and injection timing is that valve opening most rises higher
After Cheng Qian within the scope of 10 °C of A, using spraying twice, first time injection timing is 70 °C of A before compression top center for secondary fuel injector, second
Secondary injection timing is within the scope of 0-30 °C of A before compression top center, diesel injection ratio accounts for entire circulating fuel amount under 100% load
The 1-5% of ratio；
Three, when 50-70% load, for manifold low-pressure fuel gas injection valve using spraying twice, first time injection timing is exhaust valve close
It closes within the scope of rear 0-30 °C of A, second injection timing is secondary fuel injector after IO Intake Valve Opens maximum lift within the scope of 10-30 °C of A
Using spraying twice, first time injection timing is 70 °C of A before compression top center, and second of injection timing is 0- before compression top center
Within the scope of 30 °C of A, diesel injection ratio accounts for the 1-5% of entire circulating fuel amount ratio under 100% load；
Four, when high load capacity load is greater than 70%, manifold low-pressure fuel gas injection valve uses single injection event, and injection timing is in exhaust valve close
It closes within the scope of rear 0-30 °C of A, secondary fuel injector is sprayed into before compression top center within the scope of 5-15 °C of A into cylinder using single injection event
Diesel oil, injection diesel fuel ratio account for the 1-5% of entire circulating fuel amount ratio under 100% load.
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