CN108518286A - HC and CO emission control strategies under a kind of dual fuel engine declared working condition - Google Patents
HC and CO emission control strategies under a kind of dual fuel engine declared working condition Download PDFInfo
- Publication number
- CN108518286A CN108518286A CN201810208711.6A CN201810208711A CN108518286A CN 108518286 A CN108518286 A CN 108518286A CN 201810208711 A CN201810208711 A CN 201810208711A CN 108518286 A CN108518286 A CN 108518286A
- Authority
- CN
- China
- Prior art keywords
- injection
- combustion
- natural gas
- emission control
- cylinder
- 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.)
- Pending
Links
Classifications
-
- 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
- F02D19/10—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 peculiar to compression-ignition engines in which the main fuel is gaseous
- F02D19/105—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 peculiar to compression-ignition engines in which the main fuel is gaseous operating in a special mode, e.g. in a liquid fuel only mode for starting
-
- 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
- F02D19/0623—Failure diagnosis or prevention; Safety measures; Testing
-
- 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
- F02D19/0694—Injectors operating with a plurality of fuels
-
- 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
- F02M43/00—Fuel-injection apparatus operating simultaneously on two or more fuels, or on a liquid fuel and another liquid, e.g. the other liquid being an anti-knock additive
- F02M43/04—Injectors peculiar thereto
Abstract
The present invention relates to HC under a kind of dual fuel engine declared working condition and CO emission control strategies, it is characterised in that：It is made of Theoretical Design and CFD numerical simulations, Theoretical Design includes the selection of combustion mode and spraying system, the determination of fuel injection schedule；CFD numerical simulations establish diesel/natural gas dual-fuel engine combustion chamber model, after verifying model accuracy and adjusting accordingly, the numerical simulation of in-cylinder combustion is carried out for different designs scheme, and according to numerical simulation result, the in-cylinder combustion and emission performance of different ejection schemes are analyzed, and contrast verification is carried out with the qualitative analysis of Theory of Combustion；The effect of emission control strategy is verified from the variation of HC and CO discharge capacitys, obtains general conclusion；The method being combined with CFD numerical simulations using Theoretical Design not only ensures the correctness of design scheme, moreover it is possible to ensure the reasonability of design scheme and good emission control effect.
Description
Technical field
The present invention relates to dual fuel engine Exhaust Emission Control research field more particularly to a kind of dual fuel engine volumes
Determine HC and CO emission control strategies under operating mode.
Background technology
Modern Internal-Combustion Engine needs to meet stringent discharge standard, including nitrogen oxides (NO X ), particulate matter (PM), hydrocarbonization
Object (HC), oxycarbide (CO) etc., and good fuel injection strategy is the key that reduce emission.Therefore it is directed to diesel oil/day
The discharge of hydrocarbons (HC) and oxycarbide (CO), provides Theoretical Design and CFD under right gas dual fuel engine declared working condition
The method that numerical simulation is combined is designed control strategy, and the two analysis result can be mutually authenticated, and arranges HC and CO
The effect for putting control strategy is assessed, and obtains general conclusion；For research dual fuel engine HC and CO emission controls
The formulation of strategy has far reaching significance.
Invention content
The technical problem to be solved in the present invention is to provide HC under a kind of dual fuel engine declared working condition and CO emission controls
Strategy is designed control strategy with the method that CFD numerical simulations are combined using Theoretical Design, and the two analysis result can be with
It is mutually authenticated, and the effect of HC and CO emission control strategies is assessed, obtain general conclusion.
In order to solve the above technical problems, the technical scheme is that：Under a kind of dual fuel engine declared working condition HC with
CO emission control strategies, innovative point are：Under declared working condition, using oil gas share injector, according to diesel oil and natural gas
Different combustion characteristics is designed emission control strategy with the method that CFD numerical simulations are combined using Theoretical Design, two
The result of person can be mutually authenticated, and assess the effect of emission control strategy, and obtain general conclusion；Specific control
System strategy is as follows：
S1：The determination of combustion system：For the declared working condition of dual fuel engine, in order to meet phase mutual coupling of the natural gas with diesel oil
It closes, realizes the controllable layer distributed of in-cylinder mixture strength and propellant composition, have both diffusion combustion and homogeneous flame propagation, use
It is layered compression-ignition mode；
S2：The determination of ejection schemes：The oil gas share injector of use is connected respectively to oil feed line and supply air line, institute
The diesel injection pressures that can be provided are 80 ~ 140MPa, and gas spraying injection pressure is 12 ~ 16MPa；Oil gas share injector is connected to
On double fuel ECU；Corresponding fuel injection schedule is diesel oil single injection event, Gas Exploitation volume injection for the first time and a small amount of the
Secondary injection strategy, and it is all made of the mode of high pressure direct injection in cylinder；
S3：The selection of associated fuel nozzle parameter：On the basis of determining combustion system and ejection schemes, in conjunction with engine reality
Border operating mode and its feature choose suitable diesel oil substitution rate and EGR rate, and substantially not according to required fuel value under declared working condition
The principle of change, and then the amount of diesel pilot and natural gas is calculated, then confirm the time for spraying of diesel oil and natural gas, injection
Number, each emitted dose and sprays pressure every time；
S4：The foundation and verification of engine combustion models：Engine chamber model is established, a certain operating mode of original machine is chosen, it will
The result and experimental result for simulating gained compare and analyze the accuracy for verifying built engine chamber model；
S5：The sunykatuib analysis of different ejection schemes：When determining that engine chamber model meets requirement of experiment, according to different
Ejection schemes carry out design scheme using CFD software the numerical simulation of in-cylinder combustion；According to numerical simulation result, analysis is not
With the in-cylinder combustion and emission performance of ejection schemes, rule and more preferably injection strategy are summed up；Finally, it is arranged from HC and CO
The effect of emission control strategy is verified in variation high-volume.
Further, the ratio of fuel gross calorific value shared by the diesel pilot in the S3 is 6%；Compression stroke stage, diesel oil
20 °C of A high-pressure injections enter cylinder before top dead centre, and injection pressure is 90MPa；Then, natural gas high pressure sectional ejecting enters gas
Cylinder, injection pressure are 14MPa；The ratio that natural gas first time emitted dose accounts for natural gas is 97% ~ 91%, second of injection of natural gas
The ratio that amount accounts for natural gas is 3% ~ 9%；Injection starting point is set to 2 °C of A before top dead centre, the first injection and the second spray to natural gas for the first time
5 ~ 20 °C of A are divided between penetrating.
Further, in the S4 engine chamber model accuracy verification, primarily directed to determined one party
The combustion process of case, simulate gained in-cylinder pressure and experiment in the data surveyed of pressure sensor compare and analyze.
Further, the in-cylinder combustion and emission performance of the different ejection schemes are analyzed, primarily directed to cylinder
The turbulence dissipation rate distribution of fuel, temperature field, combustion pressure, heat liberation rate, heat release rate, velocity field, turbulent flow variation etc. and the HC that generates with
CO, and obtain general conclusion；Wherein, the variation of HC and CO amounts be verify HC and CO emission control strategy effects it is main according to
According to.
The advantage of the invention is that：
1）Binding isotherm design and CFD numerical simulations are designed HC and CO emission control strategies in the present invention, Theoretical Design
The quantitative analysis results of the qualitative analysis and CFD numerical simulations can be mutually authenticated, to illustrate the reasonable of design scheme
Property, and the effect of HC and CO emission control strategies is assessed from the variation of HC and CO amounts；The qualitative analysis is divided with quantitative
Analysis result is mutually authenticated, and not only can guarantee the correctness of design scheme, moreover it is possible to ensure the reasonability of design scheme and good
Emission control effect.
Description of the drawings
The present invention will be further described in detail below with reference to the accompanying drawings and specific embodiments.
Fig. 1 is the oil gas share injector schematic diagram of the present invention.
Fig. 2 is the grid model schematic diagram of the engine intake valve close moment combustion chamber of the present invention.
Fig. 3 is that the engine piston of the present invention is in the grid model schematic diagram of stop moment combustion chamber.
Fig. 4 is pressure curves and simulated pressure curve comparison figure in a certain operating mode cylinder of engine of the present invention.
Fig. 5 is the multiple fuel injection event schematic diagrames of engine of the present invention.
Fig. 6 is second of injection proportion of different natural gases (3%, 5%, 7%, 9%) of the present invention, and HC mass fractions are with day
The change curve of right gas first time and second of injection interval angle.
Fig. 7 be the present invention different natural gases for the first time with second injection interval angle (5 °C of A, 10 °C of A, 15 °C of A,
20 °C of A), HC mass fractions with second of injection proportion of natural gas change curve.
Fig. 8 is second of injection proportion of different natural gases (3%, 5%, 7%, 9%) of the present invention, and CO mass fractions are with day
The change curve of right gas first time and second of injection interval angle.
Fig. 9 be the present invention different natural gases for the first time with second injection interval angle (5 °C of A, 10 °C of A, 15 °C of A,
20 °C of A), CO mass fractions with second of injection proportion of natural gas change curve.
Figure 10 be the present invention second of injection proportion of different natural gases (3%, 5%, 7%, 9%), NO mass fractions with
The change curve of natural gas first time and second of injection interval angle.
Figure 11 be that present invention different natural gases for the first time with second injection interval angle (5 °C of A, 10 °C of A, 15 °
CA, 20 °C of A), NO mass fractions with second of injection proportion of natural gas change curve.
Figure 12,13,14 are natural gas when with second of injection interval angle being for the first time 15 °C of A, different natural gases second
Secondary injection proportion（3%、5%、7%、9%）, cylinder temperature, in-cylinder pressure and combustion heat release rate are bent with the variation of crank angle
Line.
Figure 15,16,17 are second of injection proportion of natural gas when being 7%, and different natural gases is sprayed with second for the first time
Angular interval（5°CA、10°CA、15°CA、20°CA）, cylinder temperature, in-cylinder pressure and combustion heat release rate are with crank angle
Change curve.
Figure 18 is 35 °C of A after top dead centre, single injection strategies, Po-7%-5 °C of A scheme, Po-7%-15 °C of A scheme, cylinder
Interior turbulence dissipation rate, Temperature Distribution, velocity flow profile and the cloud atlas comparison of CO distributions.
Figure 19 is 35 °C of A after top dead centre, single injection strategies, Po-3%-15 °C of A scheme, Po-7%-15 °C of A scheme, cylinder
Interior turbulence dissipation rate, Temperature Distribution, velocity flow profile and the cloud atlas comparison of CO distributions.
As shown in the figure：101. oil gas share injector；102. solenoid valve；103. fuel feeding/oil return；104. two sections of valves of break-make；
105. fuel oil plunger；106. fuel pin；107. natural gas needle-valve；108. plunger；109. natural gas；110. fuel spray；
111. natural gas spray；401. diesel injection；The injection (volume) for the first time of 402. natural gases；403. natural gases, second of injection
(a small amount of)；404. intake stroke lower dead centers；405. compression stroke top dead centres；406. diesel oil and natural gas first time injection interval
Angle；The injection for the first time of 407. natural gases and second of injection interval angle.
Specific implementation mode
The following examples can make professional and technical personnel that the present invention be more fully understood, but therefore not send out this
It is bright to be limited among the embodiment described range.
HC and CO emission control strategies, a kind of specified work of dual fuel engine under a kind of dual fuel engine declared working condition
HC and CO emission control strategies, different from natural gas according to diesel oil using oil gas share injector under declared working condition under condition
Combustion characteristics, emission control strategy is designed with the method that CFD numerical simulations are combined using Theoretical Design, the two
As a result it can be mutually authenticated, and the effect of emission control strategy is assessed, and obtain general conclusion；Specific control plan
It is slightly as follows：
S1：The determination of combustion system：For the declared working condition of dual fuel engine, in order to meet phase mutual coupling of the natural gas with diesel oil
It closes, realizes the controllable layer distributed of in-cylinder mixture strength and propellant composition, have both diffusion combustion and homogeneous flame propagation, use
It is layered compression-ignition mode；
S2：The determination of ejection schemes：The oil gas share injector of use is connected respectively to oil feed line and supply air line, institute
The diesel injection pressures that can be provided are 80 ~ 140MPa, and gas spraying injection pressure is 12 ~ 16MPa；Oil gas share injector is connected to
On double fuel ECU；Corresponding fuel injection schedule is diesel oil single injection event, Gas Exploitation volume injection for the first time and a small amount of the
Secondary injection strategy, and it is all made of the mode of high pressure direct injection in cylinder；
S3：The selection of associated fuel nozzle parameter：On the basis of determining combustion system and ejection schemes, in conjunction with engine reality
Border operating mode and its feature choose suitable diesel oil substitution rate and EGR rate, and substantially not according to required fuel value under declared working condition
The principle of change, and then the amount of diesel pilot and natural gas is calculated, then confirm the time for spraying of diesel oil and natural gas, injection
Number, each emitted dose and sprays pressure every time；
S4：The foundation and verification of engine combustion models：Engine chamber model is established, a certain operating mode of original machine is chosen, it will
The result and experimental result for simulating gained compare and analyze the accuracy for verifying built engine chamber model；
S5：The sunykatuib analysis of different ejection schemes：When determining that engine chamber model meets requirement of experiment, according to different
Ejection schemes carry out design scheme using CFD software the numerical simulation of in-cylinder combustion；According to numerical simulation result, analysis is not
With the in-cylinder combustion and emission performance of ejection schemes, rule and more preferably injection strategy are summed up；Finally, it is arranged from HC and CO
The effect of emission control strategy is verified in variation high-volume.
The ratio of fuel gross calorific value shared by diesel pilot in S3 is 6%；In the compression stroke stage, diesel oil is 20 ° before top dead centre
CA high-pressure injections enter cylinder, and injection pressure is 90MPa；Then, natural gas high pressure sectional ejecting enters cylinder, and injection pressure is
14MPa；The ratio that natural gas first time emitted dose accounts for natural gas is 97% ~ 91%, and second of emitted dose of natural gas accounts for natural gas
Ratio is 3% ~ 9%；Injection starting point is set to 2 °C of A before top dead centre to natural gas for the first time, and the first injection and the second injection interval be 5 ~
20°CA。
The verification of engine chamber model accuracy in S4, primarily directed to the combustion process of determined some scheme,
The data that pressure sensor is surveyed in in-cylinder pressure and experiment obtained by simulating compare and analyze.
The in-cylinder combustion and emission performance of different ejection schemes are analyzed, and are consumed primarily directed to the turbulent flow of cylinder fuel
The rate of dissipating distribution, temperature field, combustion pressure, heat liberation rate, heat release rate, velocity field, turbulent flow variation etc. and the HC and CO generated, and obtain general
The conclusion of property；Wherein, the variation of HC and CO amounts is to verify the Main Basiss of HC and CO emission control strategy effects.
The combustion mode that dual fuel engine may be used includes that homogeneity compression-ignition, layering compression ignition, conventional diesel engine are divided
Analysis is chosen.Among these, the combustion mode of homogeneity compression-ignition can not efficiently control combustion phase, and range of operation is due to by small negative
Lotus catch fire with the influence of big load detonation and be limited in a smaller range, that is, allow to by largely cool down EGR control
Burn rate when high load capacity processed, power output can not be met the requirements；Conventional diesel engine pattern is suitable for cold start-up, idling
And running on the lower load, but under high loads, it is unable to give full play the natural gas engine feature of environmental protection, the advantage of economy, therefore most
Layering compression-ignition mode is chosen eventually.By intercoupling for diesel oil and natural gas, in-cylinder mixture strength and propellant composition are realized
Controllable layer distributed has both diffusion combustion and homogeneous flame propagation.
As shown in Figure 1, oil gas share injector 101 has two sets of needle-valves, internal needle-valve 106 control the injecting time of diesel oil with
Pulsewidth, external needle-valve 106 control CNG, first spray into a small amount of diesel pilot 110 and form fiery core, then high-pressure gas 111 is injected in fire
On flame, to be burnt simultaneously at multiple spot using multiple fiery karyomorphisms that diesel oil is formed, mixture combustion speed is fast, and engine thermal efficiency is high,
Dynamic property is strong.And its external shape and conventional diesel fuel nozzle are very nearly the same, need not carry out big change to original machine substantially
It is dynamic.Integrated comparative, for the declared working condition of this type, using oil gas share injector, in fuel tank the layering of high pressure direct injection expand
Dissipate combustion mode.Oil gas share injector installation site is located at that cylinder cap is placed in the middle, is arranged vertically.
The combustion chamber model that dual fuel engine is drawn out using three-dimensional graphics software is then introduced into CFD numerical simulations
In software, corresponding surface grids and the division of volume mesh, the determination of corresponding boundary condition and the selection of computation model are carried out, to
Set up the combustion chamber numerical model of dual fuel engine.As shown in Figure 2 and Figure 3, piston be located at IC Intake Valve Closes with it is upper
The stop moment.Dynamic mesh quality is good, without bad grid.It is equidistantly connected, is chosen former by 8 channels between precombustion chamber and main combustion chamber
The a certain operating mode of machine compares and analyzes the in-cylinder pressure of simulation gained with the test data that pressure sensor is surveyed, to examine
Test the accuracy of combustion chamber model foundation.Verification result is as shown in Figure 4.
On this basis, the design of related ejection schemes parameter is further carried out.First, the volume residing for engine
Determine operating mode, determines the gross calorific value of fuel needed for original machine.Then, the principle substituted based on equal calorific values, calculate required diesel oil amount with
The amount of natural gas.
Since constant engine operating mode load is higher, and using oil gas share injector 101 and high pressure direct injection in fuel tank
Layering diffusion combustion mode, the ratio of therefore ejection schemes, fuel gross calorific value shared by natural gas higher can be chosen to be 94%.
On this basis, the amount of diesel oil and natural gas is calculated, and EGR rate is chosen to be 10%.On this basis, diesel oil spray is designed
The relevant parameter penetrated.Compression stroke stage, diesel oil 401 enter cylinder in 405 preceding 20 °C of A high-pressure injections of top dead centre, spray pressure
For 90MPa.
On this basis, the design of natural gas correlation nozzle parameter is carried out.In order to promote gaseous mixture in late combustion cylinder
Turbulent perturbation promotes cylinder temperature, to improve the oxygenation efficiency of soot and CO, reduces soot and the discharge of CO, optimizes cylinder
Interior burning.In conjunction with relative combustion theory, natural gas is designed as height by the main jet and rear spray sectional ejecting being analogous in diesel engine
Sectional ejecting is pressed, natural gas injection 402 for the first time is respectively designated as and sprays 403 second with natural gas, and spray pressure and be
14MPa.Wherein, it is 91% ~ 97% that injection 402 for the first time, which accounts for natural gas ratio, second injection 403 account for natural gas ratio be 3% ~
9%.Injection starting point is set to 405 preceding 2 °C of A of top dead centre to natural gas for the first time, and injection for the first time and second of injection interval 407 be 5 ~
20°CA.Therefore it is respectively 3%, 5%, 7%, 9% to choose natural gas first time emitted dose, injection for the first time and second of injection interval point
Not Wei 5 °C of A, 10 °C of A, 15 °C of A, 20 °C of A, different emitted doses intercouple with injection interval, totally 16 kinds（4×4）Fuel injection
Scheme.In addition natural gas single injection strategies（SI cancels second of a small amount of injection, and is Baseline with this scheme）,
One, which shares 17 kinds of fuel injection schedules, carries out numerical simulation.
Fig. 6 to Figure 19 is specifically shown in the numerical simulation result of described 17 kinds different ejection schemes, includes mainly cylinder internal combustion
It burns and emission performance is analyzed, primarily directed to the concentration field of cylinder fuel, temperature field, combustion pressure, heat liberation rate, heat release rate, speed
Field, turbulent flow variation etc. and HC, CO, the NO generated X .Wherein, the variation of HC and CO amounts is verification HC and CO emission control strategies
The Main Basiss of effect.
Analysis can obtain, and using natural gas Split injection strategy, the jet action of second of a small amount of injection 403 promotes cylinder
The turbulent perturbation of interior gaseous mixture, and the combustion heat release of second of a small amount of injection 403 of natural gas improves cylinder temperature, to improve
The oxygenation efficiency of HC and CO, reduce the discharge of HC and CO;When first time and larger second of injection interval 407, compared with
Big rear discharge rate 7% and 9% preferably reduces the discharge of HC and CO, and has good inhibiting effect to the discharge of NOx.First
When secondary smaller with second of injection interval 407, second of 403 ratio of injection is preferably reduced.And injection interval 407 is unsuitable too small, it is no
Then effect can run counter to desire;When second of 403 large percentage of injection 7% and 9%, between larger first time and second of injection
Be conducive to improve discharge every (15 °C of A, 20 °C of A)；When second of 403 ratio of injection is smaller (3%, 5%), discharge to injection interval
407 variation relative insensitivities;Integrated comparative, using more than 10 °C A a certain range of first times and second of injection interval 407,
It is apparent to the effect for reducing HC and CO discharges, and suitably increase second of injection, 403 ratio to inhibiting NOxDischarge more added with
Profit.
The analytical conclusions of the above numerical simulation result meet burning theory and some achievements for being studied of forefathers.It fills
HC and CO emission control strategies under clear present design of defending oneself and a kind of diesel/natural gas dual-fuel engine declared working condition
Correctness, reasonability and good effect.
Natural gas single injection strategies are SI (Single Injection), and as reference scheme
(Baseline)；Natural gas sectional ejecting scheme is Po-a%-b°C A (Post Injection), Po indicate to spray for a small amount of second
It penetrates,a% indicates second of injection proportion,b°C A indicates injection for the first time and second of injection interval, such as second of injection proportion
5%, the scheme that injection for the first time is 12 °C of A with second of injection interval is expressed as Po-5%-12 °C of A.
It should be understood by those skilled in the art that the present invention is not limited to the above embodiments, above-described embodiment and explanation
Merely illustrating the principles of the invention described in book, without departing from the spirit and scope of the present invention, the present invention also has
Various changes and modifications, these changes and improvements all fall within the protetion scope of the claimed invention.The claimed scope of the invention
It is defined by the appending claims and its equivalent thereof.
Claims (4)
1. HC and CO emission control strategies under a kind of dual fuel engine declared working condition, it is characterised in that：Under declared working condition,
Using oil gas share injector, according to the diesel oil combustion characteristics different from natural gas, using Theoretical Design and CFD numerical simulation phases
In conjunction with method emission control strategy is designed, the result of the two can be mutually authenticated, and to the effect of emission control strategy
Fruit is assessed, and obtains general conclusion；Specific control strategy is as follows：
S1：The determination of combustion system：For the declared working condition of dual fuel engine, in order to meet phase mutual coupling of the natural gas with diesel oil
It closes, realizes the controllable layer distributed of in-cylinder mixture strength and propellant composition, have both diffusion combustion and homogeneous flame propagation, use
It is layered compression-ignition mode；
S2：The determination of ejection schemes：The oil gas share injector of use is connected respectively to oil feed line and supply air line, institute
The diesel injection pressures that can be provided are 80 ~ 140MPa, and gas spraying injection pressure is 12 ~ 16MPa；Oil gas share injector is connected to
On double fuel ECU；Corresponding fuel injection schedule is diesel oil single injection event, Gas Exploitation volume injection for the first time and a small amount of the
Secondary injection strategy, and it is all made of the mode of high pressure direct injection in cylinder；
S3：The selection of associated fuel nozzle parameter：On the basis of determining combustion system and ejection schemes, in conjunction with engine reality
Border operating mode and its feature choose suitable diesel oil substitution rate and EGR rate, and substantially not according to required fuel value under declared working condition
The principle of change, and then the amount of diesel pilot and natural gas is calculated, then confirm the time for spraying of diesel oil and natural gas, injection
Number, each emitted dose and sprays pressure every time；
S4：The foundation and verification of engine combustion models：Engine chamber model is established, a certain operating mode of original machine is chosen, it will
The result and experimental result for simulating gained compare and analyze the accuracy for verifying built engine chamber model；
S5：The sunykatuib analysis of different ejection schemes：When determining that engine chamber model meets requirement of experiment, according to different
Ejection schemes carry out design scheme using CFD software the numerical simulation of in-cylinder combustion；According to numerical simulation result, analysis is not
With the in-cylinder combustion and emission performance of ejection schemes, rule and more preferably injection strategy are summed up；Finally, it is arranged from HC and CO
The effect of emission control strategy is verified in variation high-volume.
2. HC and CO emission control strategies, feature under a kind of dual fuel engine declared working condition according to claim 1
It is：The ratio of fuel gross calorific value shared by diesel pilot in the S3 is 6%；In the compression stroke stage, diesel oil is before top dead centre
20 °C of A high-pressure injections enter cylinder, and injection pressure is 90MPa；Then, natural gas high pressure sectional ejecting enters cylinder, injection pressure
Power is 14MPa；The ratio that natural gas first time emitted dose accounts for natural gas is 97% ~ 91%, and second of emitted dose of natural gas accounts for naturally
The ratio of gas is 3% ~ 9%；Injection starting point is set to 2 °C of A before top dead centre to natural gas for the first time, and the first injection is with the second injection interval
5~20°CA。
3. HC and CO emission control strategies, feature under a kind of dual fuel engine declared working condition according to claim 1
It is：The verification of engine chamber model accuracy in the S4, primarily directed to the combustion process of determined some scheme,
The data that pressure sensor is surveyed in in-cylinder pressure and experiment obtained by simulating compare and analyze.
4. HC and CO emission control strategies, feature under a kind of dual fuel engine declared working condition according to claim 1
It is：The in-cylinder combustion and emission performance of the difference ejection schemes are analyzed, primarily directed to the turbulent flow of cylinder fuel
Dissipative shock wave distribution, temperature field, combustion pressure, heat liberation rate, heat release rate, velocity field, turbulent flow variation etc. and the HC and CO generated, and obtain one
As property conclusion；Wherein, the variation of HC and CO amounts is to verify the Main Basiss of HC and CO emission control strategy effects.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810208711.6A CN108518286A (en) | 2018-03-14 | 2018-03-14 | HC and CO emission control strategies under a kind of dual fuel engine declared working condition |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810208711.6A CN108518286A (en) | 2018-03-14 | 2018-03-14 | HC and CO emission control strategies under a kind of dual fuel engine declared working condition |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN108518286A true CN108518286A (en) | 2018-09-11 |
Family
ID=63433707
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810208711.6A Pending CN108518286A (en) | 2018-03-14 | 2018-03-14 | HC and CO emission control strategies under a kind of dual fuel engine declared working condition |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN108518286A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110552795A (en) * | 2019-07-25 | 2019-12-10 | 东风商用车有限公司 | Injection method for diesel micro-injection ignition natural gas engine |
| CN111625960A (en) * | 2020-05-27 | 2020-09-04 | 海南热带汽车试验有限公司 | CFD-based E10 ethanol gasoline engine combustion three-dimensional simulation method |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007172349A (en) * | 2005-12-22 | 2007-07-05 | Mazda Motor Corp | Predictive analysis system, method and program for engine performance |
| CN102410097A (en) * | 2011-10-18 | 2012-04-11 | 北京理工大学 | Method for matching fuel oil segmental injection timing with vortex in cylinder of diesel engine |
| CN103061908A (en) * | 2012-12-21 | 2013-04-24 | 天津大学 | Flexible dual-fuel high pressure combustion chamber (HPCC) engine combustion and discharge control method and deivce |
| CN103321762A (en) * | 2013-07-05 | 2013-09-25 | 华北水利水电大学 | Gas-liquid fuel mixing method and mixing device for hydrogen / gasoline dual-fuel engine |
-
2018
- 2018-03-14 CN CN201810208711.6A patent/CN108518286A/en active Pending
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007172349A (en) * | 2005-12-22 | 2007-07-05 | Mazda Motor Corp | Predictive analysis system, method and program for engine performance |
| CN102410097A (en) * | 2011-10-18 | 2012-04-11 | 北京理工大学 | Method for matching fuel oil segmental injection timing with vortex in cylinder of diesel engine |
| CN103061908A (en) * | 2012-12-21 | 2013-04-24 | 天津大学 | Flexible dual-fuel high pressure combustion chamber (HPCC) engine combustion and discharge control method and deivce |
| CN103321762A (en) * | 2013-07-05 | 2013-09-25 | 华北水利水电大学 | Gas-liquid fuel mixing method and mixing device for hydrogen / gasoline dual-fuel engine |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110552795A (en) * | 2019-07-25 | 2019-12-10 | 东风商用车有限公司 | Injection method for diesel micro-injection ignition natural gas engine |
| CN111625960A (en) * | 2020-05-27 | 2020-09-04 | 海南热带汽车试验有限公司 | CFD-based E10 ethanol gasoline engine combustion three-dimensional simulation method |
| CN111625960B (en) * | 2020-05-27 | 2023-09-01 | 海南热带汽车试验有限公司 | CFD-based E10 ethanol gasoline engine combustion three-dimensional simulation method |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| Ra et al. | Study of high speed gasoline direct injection compression ignition (GDICI) engine operation in the LTC regime | |
| Ra et al. | Gasoline DICI engine operation in the LTC regime using triple-pulse injection | |
| Yang et al. | Ignition and combustion simulations of spray-guided SIDI engine using Arrhenius combustion with spark-energy deposition model | |
| Hanson et al. | An experimental investigation of fuel reactivity controlled PCCI combustion in a heavy-duty engine | |
| Lee et al. | Optimization of the piston bowl geometry and the operating conditions of a gasoline-diesel dual-fuel engine based on a compression ignition engine | |
| Li et al. | The effects of partially premixed combustion mode on the performance and emissions of a direct injection natural gas engine | |
| Yoon et al. | Effects of the swirl ratio and injector hole number on the combustion and emission characteristics of a light duty diesel engine | |
| Kokjohn et al. | Modeling charge preparation and combustion in diesel fuel, ethanol, and dual-fuel PCCI engines | |
| Butts et al. | Investigation of the effects of cetane number, volatility, and total aromatic content on highly-dilute low temperature diesel combustion | |
| Zoldak et al. | Combustion simulation of dual fuel CNG engine using direct injection of natural gas and diesel | |
| Shah et al. | CFD simulations of pre-chamber jets' mixing characteristics in a heavy duty natural gas engine | |
| Walker et al. | Use of low-pressure direct-injection for reactivity controlled compression ignition (RCCI) light-duty engine operation | |
| Kammel et al. | Simulation based predesign and experimental validation of a prechamber ignited HPDI gas combustion concept | |
| Wenming et al. | Phi-T map analysis on RCCI engine fueled by methanol and biodiesel | |
| Park et al. | Modeling the effect of injector nozzle-hole layout on diesel engine fuel consumption and emissions | |
| Shirvani et al. | An investigation of the effects of the piston bowl geometries of a heavy-duty engine on performance and emissions using direct dual fuel stratification strategy, and proposing two new piston profiles | |
| CN108518286A (en) | HC and CO emission control strategies under a kind of dual fuel engine declared working condition | |
| Wang et al. | Effect of injection strategy on the combustion and knock in a downsized gasoline engine with large eddy simulation | |
| Cong et al. | Parameter investigation of the pilot fuel post-injection strategy on performance and emissions characteristics of a large marine two-stroke natural gas-diesel dual-fuel engine | |
| Dimitriou et al. | Diesel engine combustion optimization for bio-diesel blends using Taguchi and ANOVA statistical methods | |
| Paredi et al. | Gas exchange and injection modeling of an advanced natural gas engine for heavy duty applications | |
| Chen et al. | Effect of equivalence ratio on diesel direct injection spark ignition combustion | |
| Deresso et al. | Numerical study of different shape design of piston bowl for diesel engine combustion in a light duty single-cylinder engine | |
| CN108798914A (en) | A kind of dual fuel engine declared working condition NOx emission and detonating combustion control strategy | |
| Zhu et al. | A numerical investigation of gasoline/diesel direct dual fuel stratification (DDFS) combustion at high loads |
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 | ||
| RJ01 | Rejection of invention patent application after publication | ||
| RJ01 | Rejection of invention patent application after publication |
Application publication date: 20180911 |