WO2019119666A1 - 基于fce模式变冲程重整高辛烷值燃料的控制方法 - Google Patents

基于fce模式变冲程重整高辛烷值燃料的控制方法 Download PDF

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Publication number
WO2019119666A1
WO2019119666A1 PCT/CN2018/080318 CN2018080318W WO2019119666A1 WO 2019119666 A1 WO2019119666 A1 WO 2019119666A1 CN 2018080318 W CN2018080318 W CN 2018080318W WO 2019119666 A1 WO2019119666 A1 WO 2019119666A1
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Prior art keywords
flexible cylinder
reforming
cylinder
engine
stroke
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English (en)
French (fr)
Inventor
尧命发
王洋
王浒
刘海峰
郑尊清
米姗
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Tianjin University
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Tianjin University
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Priority to US16/301,721 priority Critical patent/US11162439B2/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
    • F02M35/10—Air intakes; Induction systems
    • F02M35/1015—Air intakes; Induction systems characterised by the engine type
    • F02M35/10157—Supercharged engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/30—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
    • F02D41/3058—Controlling fuel injection according to or using specific or several modes of combustion characterised by the mode(s) being used the engine working with a variable number of cycles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D15/00—Varying compression ratio
    • F02D15/02—Varying compression ratio by alteration or displacement of piston stroke
    • 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
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • 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
    • F02B75/00—Other engines
    • F02B75/04—Engines with variable distances between pistons at top dead-centre positions and cylinder heads
    • F02B75/048—Engines with variable distances between pistons at top dead-centre positions and cylinder heads by means of a variable crank stroke length
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
    • F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
    • F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
    • F02D13/0203—Variable control of intake and exhaust valves
    • 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
    • F02D19/0668—Treating or cleaning means; Fuel filters
    • F02D19/0671—Means to generate or modify a fuel, e.g. reformers, electrolytic cells or membranes
    • 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
    • F02D41/008—Controlling each cylinder individually
    • 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
    • F02D41/008—Controlling each cylinder individually
    • F02D41/0082—Controlling each cylinder individually per groups or banks
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/30—Controlling fuel injection
    • F02D41/38—Controlling fuel injection of the high pressure type
    • 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
    • F02M31/20—Apparatus for thermally treating combustion-air, fuel, or fuel-air mixture for cooling
    • 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
    • F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
    • F02M35/10—Air intakes; Induction systems
    • F02M35/10209—Fluid connections to the air intake system; their arrangement of pipes, valves or the like
    • F02M35/10222—Exhaust gas recirculation [EGR]; Positive crankcase ventilation [PCV]; Additional air admission, lubricant or fuel vapour admission
    • 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
    • F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
    • F02M35/10—Air intakes; Induction systems
    • F02M35/10242—Devices or means connected to or integrated into air intakes; Air intakes combined with other engine or vehicle parts
    • F02M35/10255—Arrangements of valves; Multi-way valves
    • 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
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two
    • 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
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/027—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle four
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
    • F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
    • F02D13/028—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation for two-stroke engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/30—Controlling fuel injection
    • F02D41/38—Controlling fuel injection of the high pressure type
    • F02D2041/389—Controlling fuel injection of the high pressure type for injecting directly into the cylinder
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies
    • 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

Definitions

  • the present invention relates to an engine, and more particularly to a novel combustion mode engine in a Flexible Cylinder Engine (FCE) mode.
  • FCE Flexible Cylinder Engine
  • part of the gasoline fuel is catalyzed into small molecules such as hydrogen and carbon monoxide in an exhaust gas recirculation dedicated engine cylinder, and then mixed with the remaining gasoline fuel and introduced into the working cylinder as a mixed fuel for combustion.
  • the results show that with the D-EGR strategy, the average thermal efficiency of the engine can be increased by 12-15%.
  • the above fuel reforming mode can improve the combustion efficiency of the engine and reduce the emissions because the reformed fuel is rich in hydrogen, thereby increasing the laminar burning speed of the mixed fuel and broadening the air-fuel ratio of the fuel.
  • the invention discloses a control method for variable stroke reforming high octane fuel based on FCE mode.
  • the flexible cylinder can realize two-stroke and four-stroke working modes by adjusting the valve strategy according to actual working conditions, that is, the flexible cylinder is used as a reforming cylinder to reform a gasoline-based high-octane fuel, and its working mode is two-stroke.
  • the reforming fuel output can be increased to increase the reforming efficiency; when the engine requires a large power output with sufficient power output, the flexible cylinder is converted into a four-stroke.
  • the present invention can switch the flexible cylinder operating mode between two strokes and four strokes.
  • the present invention provides a control method based on an FCE mode variable stroke reforming high octane fuel, the engine used includes an air intake system, and has a plurality of working cylinders and at least one fuel flexible cylinder.
  • the air intake system includes a turbine and a supercharger, an air intake manifold connected to the supercharger, and an air intake three-way valve is disposed on the air intake manifold;
  • the air intake three-way valve is divided into two paths, one is a working cylinder intake pipe, the other is a flexible cylinder intake pipe, and a working circuit is connected between the air intake manifold and the working cylinder intake pipe,
  • a fuel reforming circuit is connected between the working cylinder intake pipe and the flexible cylinder intake pipe; the fuel reforming circuit is sequentially passed through a flexible cylinder intake pipe through a flexible cylinder injector, a flexible cylinder, and a flexible cylinder exhaust tee.
  • the ECU controls the amount of fuel injected by the flexible cylinder injector to the flexible cylinder and the state of the flexible cylinder intake and exhaust valves, so that the working mode of the flexible cylinder is two according to actual engine operating conditions.
  • the flexible cylinder injector switches between stroke and four strokes; when the engine is in a small load and needs to promote combustion stability, the flexible cylinder injector injects an excessively rich fuel having an equivalence ratio greater than 1 into the flexible cylinder, the flexible cylinder being a two stroke Operating mode; when a large engine load requires sufficient power output, the flexible cylinder injector injects a conventional concentration of fuel into the flexible cylinder, the flexible cylinder being in a four-stroke mode;
  • the opening timing of the exhaust valve is selected, and the reforming gas that derives the corresponding required activity of the engine from the flexible cylinder is introduced into the working cylinder.
  • the activity curve of the flexible cylinder reforming gas is obtained: the activity curve of the flexible cylinder reforming gas is obtained by using the CHEMKIN software according to different derivatization products.
  • the flexible cylinder piston performs work to provide power output to the engine
  • the invention is based on a two-stroke flexible cylinder reforming gasoline high-octane fuel engine in the FCE mode, which can be converted according to the specific working conditions of the engine: when the small load is changed, the flexible cylinder is converted into a reforming cylinder, and the valve strategy is realized flexibly. Cylinder two-stroke reforming fuel; when the load is heavy, the flexible cylinder is transformed into the same function as the conventional cylinder, and it becomes a four-stroke work. In the reforming mode, the flexible cylinder two-stroke reforming can provide sufficient reforming gas to the conventional cylinder and improve the reforming efficiency compared to the four-stroke reforming.
  • Figure 1 is a schematic diagram of a high octane fuel engine based on FCE mode
  • FIG. 2 is a schematic view of the valve state in the two-stroke of the flexible cylinder of the present invention, wherein a is a schematic diagram of the intake air, b is a schematic diagram of the compression misfire reforming, and c is a schematic diagram of the exhaust gas.
  • FIG. 3 is a schematic diagram of a valve state in a four-stroke flexible cylinder, wherein a is a schematic diagram of the intake state, b is a schematic diagram of the compressed state, c is a schematic diagram of the state of the work, and d is a schematic diagram of the exhaust state.
  • Figure 4 shows the variation of the activity of the flexible cylinder reforming gas with the opening timing of the exhaust valve.
  • 1-flexible cylinder intake pipe 2-cylinder intake pipe, 3-mixing cavity, 4-cylinder injector, 5-cylinder intake manifold, 6-engine, 7-cylinder, 8- Flexible cylinder, 9-air intake manifold, 10-EGR tube, 11-EGR control valve, 12-supercharger, 13-turbine, 14-exhaust pipe, 15-to-exhaust pipe, 16-exhaust aftertreatment Installation, 17-flexible cylinder exhaust three-way valve, 18-reforming air intercooler, 19-flexible cylinder injector, 20-reforming air pipe, 21-air intake three-way valve, 22-EGR intercooler , 23- intake valve, 24-exhaust valve.
  • the flexible cylinder is designed to be two-stroke/four-stroke flexible switching by the valve strategy adjustment, and the remaining conventional cylinders are fixedly designed as four strokes.
  • the reformer gas supplied to the conventional cylinder is more abundant and the reforming efficiency is higher than in the case where the flexible cylinder is four strokes.
  • the flexible cylinder can be converted into four strokes in the same way as the conventional cylinder valve strategy.
  • the FCE mode engine consists of a flexible cylinder and a conventional cylinder.
  • the flexible cylinder is responsible for reforming the fuel, and the reformed reformed gas is cooled by the pipeline and mixed with fresh fuel to be introduced into the conventional cylinder for combustion.
  • the invention designs a flexible cylinder as two-stroke/four-stroke based on the FCE mode, and the remaining conventional cylinder is a four-stroke new concept engine, wherein the activity of the reforming product in the flexible cylinder can be controlled by controlling the opening timing of the exhaust valve.
  • the valve strategy of the flexible cylinder is now the same as the conventional cylinder, and is converted into four strokes, so that the engine has sufficient power output at a large load.
  • the invention discloses a control method based on FCE mode variable stroke reforming high octane fuel, which mainly realizes two-stroke fuel reforming in an engine cylinder by adjusting a valve strategy, so that the engine obtains enough at a small load. Re-gas, let it run more efficiently and energy-efficiently.
  • the invention is based on a new concept of controllable combustion reaction path.
  • the engine is composed of an intake system, a working system and a fuel reforming system.
  • the structural diagram is shown in Fig. 1.
  • the intake system and working system are the same as those in the FCE mode proposed in Reference [13], but the fuel reforming system valve strategy is optimized.
  • the structure of the engine used is as shown in Fig.
  • the air intake system comprising a turbine 13 and a supercharger 12, an air intake manifold 9 connected to the supercharger 12, the air An air intake three-way valve 21 is disposed on the intake manifold 9; the air intake manifold 9 is divided into two paths from the air intake three-way valve 21, one for the working cylinder intake pipe 2, and the other for a flexible cylinder intake pipe 1, a working circuit is connected between the air intake manifold 9 and the cylinder intake pipe 2, and a fuel reforming is connected between the cylinder intake pipe 2 and the flexible cylinder intake pipe 1 a circuit; the turbocharger is composed of a turbine 13 and a supercharger 12, the exhaust gas from the exhaust pipe 14 drives the turbine 13 to rotate
  • the air intake three-way valve 21 allows only the intake air in the air intake manifold 9 to flow to the flexible cylinder intake pipe 1 and the cylinder intake pipe 2, respectively.
  • the ECU connected to the engine controls the distribution of air from the air intake manifold 9 through the air intake three-way valve 21 in accordance with the difference in pressure between the air intake manifold 9, the flexible cylinder intake pipe 1, and the cylinder intake pipe 2.
  • the flow direction is to prevent the exhaust gas from flowing back into the air intake manifold 9.
  • the working circuit is composed of a supercharger 12, an air intake three-way valve 21, a working cylinder intake pipe 2, a mixing chamber 3, a working cylinder intake manifold 5, a working cylinder injector 4, a working cylinder 7, and an exhaust pipe. 14.
  • the EGR valve 11, the EGR intercooler 22, the total exhaust pipe 15, and the exhaust aftertreatment device 16 are formed.
  • the mixing chamber 3 mixes air from the cylinder intake pipe 2 (or a mixture of EGR and air) and reformed gas from the flexible cylinder 8 through the reforming gas pipe 20; the cylinder injector 4 controls injection The timing and amount of fuel in the working cylinder; the EGR control valve 11 is also disposed on the EGR pipe 10 to control the amount of exhaust gas introduced into the mixing chamber 3; the EGR intercooler 22 is disposed on the pipeline of the EGR pipe 10, Between the mixing chamber 3 and the EGR control valve 11.
  • the fuel reforming circuit comprises a flexible cylinder intake pipe 1, a flexible cylinder injector 19, an intake valve 23, an exhaust valve 24, a flexible cylinder 8, a reforming gas pipe 20, a reforming gas intercooler 18, and a mixing chamber 3. composition.
  • the fuel reforming system circuit passes through the flexible cylinder injector 19, the flexible cylinder 8, the reforming gas pipe 20, and the reforming gas intercooler 18 to the mixing chamber 3 from the fuel into the flexible cylinder intake pipe;
  • the reformed air intercooler 18 is disposed on the reforming gas pipe 20 and interposed between the reforming flexible cylinder 8 and the mixing chamber 3.
  • An ECU connected to the engine controls the amount of fuel injected by the flexible cylinder injector 19 to the flexible cylinder 8 and the state of the intake valve 23 and the exhaust valve 24 of the flexible cylinder 8 so as to be made according to actual engine operating conditions.
  • the mode of operation of the flexible cylinder 8 is between two strokes and four strokes.
  • the flexible cylinder injector 19 sprays the flexible cylinder 8 with an excessively rich fuel having an equivalence ratio greater than 1, and the flexible cylinder is in a two-stroke working mode;
  • the process of implementing the reforming cycle in the two-stroke working mode is:
  • the opening timing of the exhaust valve 24 is selected, and the reforming gas from which the corresponding required activity of the engine is derived from the flexible cylinder 8 is introduced into the working cylinder 7.
  • the activity curve of the flexible cylinder reforming gas is obtained: the activity curve of the flexible cylinder reforming gas is obtained by using the CHEMKIN software according to different reforming products, and FIG. 4 is the activity of the flexible cylinder reforming gas.
  • the flexible cylinder injector 19 injects a conventional concentration of fuel into the flexible cylinder 8, which is in a four-stroke mode; as shown in FIG.
  • the process of implementing a reforming loop in a pattern is:
  • the flexible cylinder 8 piston performs work to provide power output to the engine
  • the ECU connected to the engine adjusts the flexible cylinder valve strategy according to the characteristics of the engine operating conditions: when the flexible cylinder is used as a reforming cylinder to reform gasoline high-octane fuel, the working mode of the cylinder is two strokes; When the engine requires a large power output with a large load, the flexible cylinder is now in the same mode as the conventional cylinder, and is converted into a four-stroke.
  • the flexible cylinder operating mode can be switched between two strokes and four strokes by a valve strategy.
  • the reforming mixture of different reforming degrees that is, the reforming gas with different activities can be obtained, so that the engine can be satisfied in a wide range.
  • the need for different active reformed gases is required.
  • the flexible cylinder is two strokes, the flexible cylinder can be reformed twice when the engine is in a normal four-stroke cycle, so that sufficient reforming gas can be supplied to the conventional cylinder to meet the engine demand.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)

Abstract

一种基于FCE模式变冲程重整高辛烷值燃料的控制方法，与发动机相连的ECU控制灵活缸喷油器（19）向灵活缸（8）的喷油量以及灵活缸进气门（23）和排气门（24）的状态，从而根据发动机实际工况需求使得灵活缸（8）的工作模式在二冲程与四冲程之间切换；当发动机处于小负荷需要促进燃烧稳定时，灵活缸喷油器（19）向灵活缸（8）喷入当量比大于1的过浓燃油，灵活缸（8）为二冲程工作模式，可以增加重整燃料的产量，提高重整效率；当发动机大负荷需要足够的动力输出时，灵活缸喷油器（19）向灵活缸（8）喷入常规浓度燃油，灵活缸（8）为四冲程工作模式，由此可以将灵活缸（8）工作模式在二冲程和四冲程之间切换。

Description

基于FCE模式变冲程重整高辛烷值燃料的控制方法 技术领域
本发明涉及一种发动机，尤其涉及一种灵活缸发动机FCE(Flexible Cylinder Engine)模式下的新型燃烧模式发动机。
背景技术
降低由汽车尾气造成的环境污染以及增加燃油效率是一个全球性的问题，因而世界各国的科学家们相继提出了多种新型燃烧模式[1-9]以缓解这一问题，包括HCCI(均质压燃Homogeneous Charge Compression Ignition)，PPC(部分预混燃烧Partially Premixed Combustion)，RCCI(活性控制均质压燃Reactivity Controlled Compression Ignition)等。这些新型的燃烧模式都是通过改变发动机的初始运行条件或者燃料的属性来实现高效节能这一目的。美国西南研究院的研究人员[10]提出了废气再循环(EGR)专用发动机汽缸策略(D-EGR)以提高发动机的效率和排放。根据D-EGR理论，部分汽油燃料在废气再循环专用发动机汽缸中被催化成氢气和一氧化碳等小分子，而后与其余汽油燃料混合并被导入工作缸中作为混合燃料进行燃烧。研究结果表明，采用D-EGR策略，发动机的平均热效率可以提高12-15％。上述燃料重整模式可以提高发动机的燃烧效率以及降低排放，这是因为重整后的燃料富含氢气，因此提高了混合燃料的层流燃烧速度，并拓宽了燃料的空燃比。上海交通大学的研究人员[11]提出化学热重整TFR新型燃烧策略，即在一台天然气发动机上独立出一个气缸用于重整天然气，将其重整成H2和CO，再导入到其他气缸进行后续燃烧。结果表明，BSHC，BSCO和BSNOx排放分别降低12％，8％及35％。
然而发动机应该在较大的范围内灵活可调以适应实际工况。双燃料燃烧模式和催化重整模式可以实现这一需求，但是这些模式需要在汽车上再加装一个油箱或者一套催化重整装置，这些都会增加汽车的负载。基于上述燃烧策略，公开号为CN105134373，公开日为2015年12月9日，名称为《基于燃烧反应路径可调控的发动机及其调控方法》的中国专利文献中披露了可变缸重整燃烧策略(Flexible cylinder engine，FCE)[12-13]。
[参考文献]
[1]Iwamoto Y.,et al.,Development of gasoline direct injection engine,1997,SAE technical paper。
[2]Kanda T.,et al.,PCCI operation with early injection of conventional diesel fuel,2005,SAE Technical Paper。
[3]Kokjohn S.,et al.,Fuel reactivity controlled compression ignition(RCCI):a pathway to controlled high-efficiency clean combustion.International Journal of Engine Research,2011.12(3):p.209-226。
[4]Reitz R.D.,Duraisamy G.,Review of high efficiency and clean reactivity controlled compression ignition(RCCI)combustion in internal combustion engines.Progress in Energy and Combustion Science,2015.46:p.12-71。
[5]Sgro L.A.,et al.,Investigating the origin of nuclei particles in GDI engine exhausts.Combustion and Flame,2012.159(4):p.1687-1692。
[6]Stanglmaier R.H.,Roberts C.E.,Homogeneous charge compression ignition(HCCI):benefits,compromises,and future engine applications,1999,SAE Technical Paper。
[7]Thring R.H.,Homogeneous-charge compression-ignition(HCCI)engines,1989,SAE Technical paper。
[8]Yao M.F.,Zheng Z,Liu H.F.,Progress and recent trends in homogeneous charge compression ignition(HCCI)engines.Progress in Energy and Combustion Science,2009.35(5):p.398-437。
[9]Zheng M.,et al.,Biodiesel engine performance and emissions in low temperature combustion.Fuel,2008.87(6):p.714-722。
[10]Alger T.,Mangold B.,Dedicated EGR:a new concept in high efficiency engines.SAE international journal of engines,2009.2(2009-01-0694):p.620-631。
[11]Zhu L.,et al.,In-cylinder thermochemical fuel reforming(TFR)in a spark-ignition natural gas engine.Proceedings of the Combustion Institute,2017.36(3):p.3487-3497。
[12]Wang Y.,Wei L.X.,Yao M.F.,A theoretical investigation of the effects of the low-temperature reforming products on the combustion of n-heptane in an HCCI engine and a constant volume vessel.Applied Energy,2016.181:p.132-139。
[13]Yao MF,Wang Y,Jia GR,et al.Novel engine controlled by combustion reaction path and regulating method thereof.U.S.Patent Application No.15/268,586。
发明内容
本发明公开了一种基于FCE模式变冲程重整高辛烷值燃料的控制方法。其中的灵活缸可根据实际工况条件通过调节气门策略实现二冲程和四冲程两种工作模式，即该灵活缸作为重整缸重整汽油类高辛烷值燃料时其工作模式为二冲程，可以增加重整燃料的产量提高重整效率；当发动机大负荷需要足够的动力输出时，灵活缸转变为四冲程。本发明可以将灵活缸工作模式在二冲程和四冲程之间切换。
为了解决上述技术问题，本发明提出的一种基于FCE模式变冲程重整高辛烷值燃料的控制方法，所用发动机包括空气进气系统，并具有多个工作缸和至少一个燃料灵活缸，所述空气进气系统包括涡轮机和增压器，与所述增压器连接的空气进气总管，所述空气进气总管上设有一个空气进气三通阀；所述空气进气总管自所述空气进气三通阀后分为两路，一路为工作缸进气管，另一路为灵活缸进气管，所述空气进气总管与所述工作缸 进气管之间连接有工作回路，所述工作缸进气管与所述灵活缸进气管之间连接有燃料重整回路；所述燃料重整回路是由灵活缸进气管后依次经过灵活缸喷油器、灵活缸、灵活缸排气三通阀、重整气中冷器、重整气管至所述混合腔；其中，所述重整气中冷器设置在重整气管上，且介于所述灵活缸与所述混合腔之间；与发动机相连的ECU控制所述灵活缸喷油器向所述灵活缸的喷油量及所述灵活缸进气门和排气门的状态，从而根据发动机实际工况需求使得所述灵活缸的工作模式在二冲程与四冲程之间的切换；当发动机处于小负荷需要促进燃烧稳定时，所述灵活缸喷油器向所述灵活缸喷入当量比大于1的过浓燃油，所述灵活缸为二冲程工作模式；当发动机大负荷需要足够的动力输出时，所述灵活缸喷油器向所述灵活缸喷入常规浓度燃油，所述灵活缸为四冲程工作模式；其中：
二冲程工作模式实现重整循环的过程是：
1-1)关闭排气门，开启进气门，空气进入灵活缸；
1-2)当灵活缸到达下止点时，关闭进气门和排气门，灵活缸开始低温压缩失火重整高辛烷值燃料；
1-3)根据灵活缸重整气的活性曲线，选择排气门的开启时刻，从所述灵活缸中导出发动机相应所需活性的重整气引入所述工作缸。所述灵活缸重整气的活性曲线的获得是：根据重整产物不同导出时刻活性不同利用CHEMKIN软件得出灵活缸重整气的活性曲线。
四冲程工作模式实现重整循环的过程是：
2-1)关闭排气门，开启进气门，空气进入灵活缸；
2-2)当灵活缸到达下止点时，关闭进气门和排气门，灵活缸开始压缩点燃高辛烷值燃料；
2-3)灵活缸活塞下行做功向发动机提供动力输出；
2-4)开启排气门，燃烧后的废气通过排气门排出。
与现有技术相比，本发明的有益效果是：
本发明基于FCE模式下二冲程灵活缸重整汽油类高辛烷值燃料发动机，即可根据发动机所处具体工况条件：当小负荷时灵活缸转变为重整缸，通过调节气门策略实现灵活缸二冲程重整燃料；当大负荷时灵活缸转变为与常规缸工作职能一样，成为四冲程参与工作。在重整模式下，灵活缸二冲程重整相较于四冲程重整，可以提供给常规缸足够的重整气，提高重整效率。
附图说明
图1是一种基于FCE模式下高辛烷值燃料发动机结构简图；
图2是本发明中灵活缸二冲程时气门状态示意图，其中，a是进气示意图，b是压缩失火重整示意图，c是排气示意图。
图3是灵活缸四冲程时气门状态示意图，其中，a是进气状态示意图，b是压缩状态示意图，c是做功状态示意图，d是排气状态示意图。
图4是灵活缸重整气的活性随排气门开启时刻的变化情况。
图中：1-灵活缸进气管，2-工作缸进气管，3-混合腔，4-工作缸喷油器，5-工作缸进气歧管，6-发动机，7-工作缸，8-灵活缸，9-空气进气总管，10-EGR管，11-EGR控制阀，12-增压器，13-涡轮机，14-排气管，15-总排气管，16-排气后处理装置，17-灵活缸排气三通阀，18-重整气中冷器，19-灵活缸喷油器，20-重整气管，21-空气进气三通阀，22-EGR中冷器，23-进气门，24-排气门。
具体实施方式
下面结合附图和具体实施例对本发明技术方案作进一步详细描述，所描述的具体实施例仅对本发明进行解释说明，并不用以限制本发明。
本发明的设计思路是：本发明中，灵活缸通过气门策略调节设计为二冲程/四冲程灵活切换，而其余常规缸固定设计为四冲程。这样设计相较于灵活缸为四冲程的情况而言提供给常规缸的重整气更加充裕，重整效率更高。而当发动机处于大负荷需要足够的动力输出时，灵活缸可以与常规缸气门策略变为一样，转换成四冲程。FCE模式发动机由灵活缸和常规缸组成，具体工作流程为：灵活缸负责重整燃料，重整后的重整气经过管路冷却后与新鲜燃料混合导入到常规缸中参与燃烧。本发明基于FCE模式基础上具体设计一种灵活缸为二冲程/四冲程，其余常规缸为四冲程的新概念发动机，其中灵活缸中的重整产物活性可通过控制排气门的开启时刻调控，并且当灵活缸由于工况需要转变成常规缸时，灵活缸的气门策略此时与常规缸相同，转变成四冲程，以使发动机在大负荷时拥有足够的功率输出。
本发明提出的一种基于FCE模式变冲程重整高辛烷值燃料的控制方法，主要是通过调节气门策略实现了发动机缸内二冲程燃料重整，从而使发动机在小负荷时获得足够多的重整气，让其更加高效节能运行。本发明基于燃烧反应路径可调控的新概念发动机由进气系统、工作系统和燃料重整系统组成，结构图如图1所示。其中的进气系统和工作系统与参考文献[13]中提出的FCE模式下的结构相同，但优化了燃料重整系统气门策略。所用发动机的结构如图1所示，包括空气进气系统，并具有多个工作缸7和至少一个燃料灵活缸8(诸如：三缸机一个灵活缸，两个工作缸或者六缸机两个灵活缸，四个工作缸，形成“一拖二”模式)，所述空气进气系统包括涡轮机13和增压器12，与所述增压器12连接的空气进气总管9，所述空气进气总管9上设有一个空气进气三通阀21；所述空气进气总管9自所述空气进气三通阀21后分为两路，一路为工作缸进气管2，另一路为灵活缸进气管1，所述空气进气总管9与所述工作缸进气管2之间连接有工作回路，所述工作缸进气管2与所述灵活缸进气管1之间连接有燃料重整回路；涡轮增压器由涡轮机13和增压器12组成，来自排气管14的废气驱动涡轮机13转动，涡轮机13驱动增压器12压 缩进气，实现进气增压；所述空气进气三通阀21控制着来自空气进气总管9空气的分配与流向，防止由于管路内压力大小的差异导致EGR管10内通过的废气回流到空气进气总管9中；所述工作缸进气管2将通过空气进气三通阀21的空气或者EGR与空气的混合气导入到混合腔3中。所述空气进气三通阀21只允许空气进气总管9中的进气分别流向灵活缸进气管1和工作缸进气管2。与发动机相连的ECU根据空气进气总管9、灵活缸进气管1和工作缸进气管2内压力大小的差异通过所述空气进气三通阀21控制来自空气进气总管9的空气的分配与流向，用以防止废气回流到空气进气总管9中。
所述工作回路由增压器12，空气进气三通阀21、工作缸进气管2、混合腔3、工作缸进气歧管5、工作缸喷油器4、工作缸7、排气管14、EGR阀11、EGR中冷器22、总排气管15和排气后处理装置16等组成。所述混合腔3混合来自工作缸进气管2的空气(或者EGR与空气的混合气)和来自灵活缸8经重整气管20的重整气；所述工作缸喷油器4控制着喷入工作缸内燃油的时刻与量；所述EGR控制阀11也设置在EGR管10上，控制着导入混合腔3的废气量；所述EGR中冷器22设置在EGR管10的管路上，介于混合腔3与EGR控制阀11之间。
所述燃料重整回路由灵活缸进气管1、灵活缸喷油器19、进气门23、排气门24、灵活缸8、重整气管20、重整气中冷器18、混合腔3组成。所述燃料重整系统回路从燃料进入灵活缸进气管后依次经过灵活缸喷油器19、灵活缸8、重整气管20、重整气中冷器18至所述混合腔3；其中，所述重整气中冷器18设置在重整气管20上、且介于所述重整灵活缸8与所述混合腔3之间。与发动机相连的ECU控制所述灵活缸喷油器19向所述灵活缸8的喷油量及所述灵活缸8进气门23和排气门24的状态，从而根据发动机实际工况需求使得所述灵活缸8的工作模式在二冲程与四冲程之间的切换。
当发动机处于小负荷需要促进燃烧稳定时，所述灵活缸喷油器19向所述灵活缸8喷入当量比大于1的过浓燃油，所述灵活缸为二冲程工作模式；如图2所示，二冲程工作模式实现重整循环的过程是：
1-1)关闭排气门24，开启进气门23，空气进入灵活缸8；
1-2)当灵活缸8到达下止点时，关闭进气门23和排气门24，灵活缸8开始低温压缩失火高辛烷值燃料；
1-3)根据灵活缸重整气的活性曲线，选择排气门24的开启时刻，从所述灵活缸8中导出发动机相应所需活性的重整气引入所述工作缸7。其中，所述灵活缸重整气的活性曲线的获得是：根据重整产物不同导出时刻活性不同利用CHEMKIN软件得出灵活缸重整气的活性曲线，图4是灵活缸重整气的活性随排气门开启时刻的变化情况。
当发动机大负荷需要足够的动力输出时，所述灵活缸喷油器19向所述灵活缸8喷入常规浓度燃油，所述灵活缸为四冲程工作模式；如图3所示，四冲程工作模式实现重整循环的过程是：
2-1)关闭排气门24，开启进气门23，空气进入灵活缸8；
2-2)当灵活缸8到达下止点时，关闭进气门23和排气门24，灵活缸8开始压缩点燃高辛烷值燃料；
2-3)灵活缸8活塞下行做功向发动机提供动力输出；
2-4)开启排气门24，燃烧后的废气通过排气门24排出。
综上，与发动机相连的ECU根据发动机运行工况特点，对灵活缸气门策略进行调整：当灵活缸作为重整缸重整汽油类高辛烷值燃料时，该缸的工作模式为二冲程；而当发动机大负荷需要足够的动力输出时，灵活缸此时与常规缸工作模式相同，转变为四冲程。通过气门策略可以将灵活缸工作模式在二冲程和四冲程之间切换。因此在灵活缸二冲程重整过程中，通过控制灵活缸排气门的开启时刻，可以获得不同重整程度的重整混合气，即不同活性的重整气，从而可以满足发动机在广阔范围内需要不同活性重整气的需求。并且由于灵活缸是二冲程这就使得当发动机处于一个正常的四冲程循环工作过程时，灵活缸可以重整两次，因此可以向常规缸提供足够的重整气，满足发动机的需求。
尽管上面结合附图对本发明进行了描述，但是本发明并不局限于上述的具体实施方式，上述的具体实施方式仅仅是示意性的，而不是限制性的，本领域的普通技术人员在本发明的启示下，在不脱离本发明宗旨的情况下，还可以做出很多变形，这些均属于本发明的保护之内。

Claims (3)

  1. 一种基于FCE模式变冲程重整高辛烷值燃料的控制方法，所用发动机包括空气进气系统，并具有多个工作缸(7)和至少一个燃料灵活缸(8)，所述空气进气系统包括涡轮机(13)和增压器(12)，与所述增压器(12)连接的空气进气总管(9)，所述空气进气总管(9)上设有一个空气进气三通阀(21)；
    所述空气进气总管(9)自所述空气进气三通阀(21)后分为两路，一路为工作缸进气管(2)，另一路为灵活缸进气管(1)，所述空气进气总管(9)与所述工作缸进气管(2)之间连接有工作回路，所述工作缸进气管(2)与所述灵活缸进气管(1)之间连接有燃料重整回路；
    所述燃料重整回路是由灵活缸进气管(1)后依次经过灵活缸喷油器(19)、灵活缸(8)、灵活缸排气三通阀(17)、重整气中冷器(18)、重整气管(20)至所述混合腔(3)；其中，所述重整气中冷器(18)设置在重整气管(20)上，且介于所述灵活缸(8)与所述混合腔(3)之间；
    其特征在于：
    与发动机相连的ECU控制所述灵活缸喷油器(19)向所述灵活缸(8)的喷油量及所述灵活缸(8)进气门(23)和排气门(24)的状态，从而根据发动机实际工况需求使得所述灵活缸(8)的工作模式在二冲程与四冲程之间的切换；当发动机处于小负荷需要促进燃烧稳定时，所述灵活缸喷油器(19)向所述灵活缸(8)喷入当量比大于1的过浓燃油，所述灵活缸为二冲程工作模式；当发动机大负荷需要足够的动力输出时，所述灵活缸喷油器(19)向所述灵活缸(8)喷入常规浓度燃油，所述灵活缸为四冲程工作模式；其中：
    二冲程工作模式实现重整循环的过程是：
    1-1)关闭排气门(24)，开启进气门(23)，空气进入灵活缸(8)；
    1-2)当灵活缸(8)到达下止点时，关闭进气门(23)和排气门(24)，灵活缸(8)开始低温压缩失火重整高辛烷值燃料；
    1-3)根据灵活缸重整气的活性曲线，选择排气门(24)的开启时刻，从所述灵活缸(8)中导出发动机相应所需活性的重整气引入所述工作缸(7)。
  2. 根据权利要求1所述基于FCE模式变冲程重整高辛烷值燃料的控制方法，其中，二冲程工作模式实现重整循环过程的步骤1-3)中，所述灵活缸重整气的活性曲线的获得是：根据重整产物不同导出时刻活性不同利用CHEMKIN软件得出灵活缸重整气的活性曲线。
  3. 根据权利要求1所述基于FCE模式变冲程重整高辛烷值燃料的控制方法，其中，四冲程工作模式实现重整循环的过程是：
    2-1)关闭排气门(24)，开启进气门(23)，空气进入灵活缸(8)；
    2-2)当灵活缸(8)到达下止点时，关闭进气门(23)和排气门(24)，灵活缸(8)开始压缩点燃高辛烷值燃料；
    2-3)灵活缸(8)活塞下行做功向发动机提供动力输出；
    2-4)开启排气门(24)，燃烧后的废气通过排气门(24)排出。
PCT/CN2018/080318 2017-12-22 2018-03-23 基于fce模式变冲程重整高辛烷值燃料的控制方法 Ceased WO2019119666A1 (zh)

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