CN100404814C - Method of operating directly injecting diesel engine - Google Patents

Method of operating directly injecting diesel engine Download PDF

Info

Publication number
CN100404814C
CN100404814C CN 200380106772 CN200380106772A CN100404814C CN 100404814 C CN100404814 C CN 100404814C CN 200380106772 CN200380106772 CN 200380106772 CN 200380106772 A CN200380106772 A CN 200380106772A CN 100404814 C CN100404814 C CN 100404814C
Authority
CN
China
Prior art keywords
piston
shaped
fuel
combustion
combustion chamber
Prior art date
Application number
CN 200380106772
Other languages
Chinese (zh)
Other versions
CN1729354A (en
Inventor
F·齐梅拉
J·萨托
M·格伦斯威格
T·山姆斯
Original Assignee
Avl里斯脱有限公司
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Priority to ATGM860/2002 priority Critical
Priority to AT0086002U priority patent/AT7204U1/en
Application filed by Avl里斯脱有限公司 filed Critical Avl里斯脱有限公司
Publication of CN1729354A publication Critical patent/CN1729354A/en
Application granted granted Critical
Publication of CN100404814C publication Critical patent/CN100404814C/en

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02DCONTROLLING COMBUSTION ENGINES
    • F02D41/00Electrical control of supply of combustible mixture or its constituents
    • F02D41/30Controlling fuel injection
    • F02D41/3011Controlling fuel injection according to or using specific or several modes of combustion
    • F02D41/3017Controlling fuel injection according to or using specific or several modes of combustion characterised by the mode(s) being used
    • F02D41/3035Controlling fuel injection according to or using specific or several modes of combustion characterised by the mode(s) being used a mode being the premixed charge compression-ignition mode
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02BINTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B23/00Other engines characterised by special shape or construction of combustion chambers to improve operation
    • F02B23/02Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition
    • F02B23/06Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition the combustion space being arranged in working piston
    • F02B23/0618Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition the combustion space being arranged in working piston having in-cylinder means to influence the charge motion
    • F02B23/0621Squish flow
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02BINTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B23/00Other engines characterised by special shape or construction of combustion chambers to improve operation
    • F02B23/02Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition
    • F02B23/06Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition the combustion space being arranged in working piston
    • F02B23/0645Details related to the fuel injector or the fuel spray
    • F02B23/0648Means or methods to improve the spray dispersion, evaporation or ignition
    • F02B23/0651Means or methods to improve the spray dispersion, evaporation or ignition the fuel spray impinging on reflecting surfaces or being specially guided throughout the combustion space
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02BINTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B23/00Other engines characterised by special shape or construction of combustion chambers to improve operation
    • F02B23/02Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition
    • F02B23/06Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition the combustion space being arranged in working piston
    • F02B23/0672Omega-piston bowl, i.e. the combustion space having a central projection pointing towards the cylinder head and the surrounding wall being inclined towards the cylinder center axis
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02DCONTROLLING COMBUSTION ENGINES
    • F02D35/00Controlling engines, dependent on conditions exterior or interior to engines, not otherwise provided for
    • F02D35/02Controlling engines, dependent on conditions exterior or interior to engines, not otherwise provided for on interior conditions
    • F02D35/025Controlling engines, dependent on conditions exterior or interior to engines, not otherwise provided for on interior conditions by determining temperatures inside the cylinder, e.g. combustion temperatures
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02DCONTROLLING COMBUSTION ENGINES
    • F02D41/00Electrical control of supply of combustible mixture or its constituents
    • F02D41/0002Controlling intake air
    • F02D41/0007Controlling intake air for control of turbo-charged or super-charged engines
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02DCONTROLLING COMBUSTION ENGINES
    • F02D41/00Electrical control of supply of combustible mixture or its constituents
    • F02D41/30Controlling fuel injection
    • F02D41/38Controlling fuel injection of the high pressure type
    • F02D41/40Controlling fuel injection of the high pressure type with means for controlling injection timing or duration
    • F02D41/401Controlling injection timing
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/01Internal exhaust gas recirculation, i.e. wherein the residual exhaust gases are trapped in the cylinder or pushed back from the intake or the exhaust manifold into the combustion chamber without the use of additional passages
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/02EGR systems specially adapted for supercharged engines
    • F02M26/04EGR systems specially adapted for supercharged engines with a single turbocharger
    • F02M26/05High pressure loops, i.e. wherein recirculated exhaust gas is taken out from the exhaust system upstream of the turbine and reintroduced into the intake system downstream of the compressor
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/02EGR systems specially adapted for supercharged engines
    • F02M26/04EGR systems specially adapted for supercharged engines with a single turbocharger
    • F02M26/06Low pressure loops, i.e. wherein recirculated exhaust gas is taken out from the exhaust downstream of the turbocharger turbine and reintroduced into the intake system upstream of the compressor
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/22Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
    • F02M26/23Layout, e.g. schematics
    • F02M26/24Layout, e.g. schematics with two or more coolers
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/22Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
    • F02M26/23Layout, e.g. schematics
    • F02M26/28Layout, e.g. schematics with liquid-cooled heat exchangers
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/34Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with compressors, turbines or the like in the recirculation passage
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02BINTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B23/00Other engines characterised by special shape or construction of combustion chambers to improve operation
    • F02B23/02Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition
    • F02B23/06Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition the combustion space being arranged in working piston
    • F02B23/0678Unconventional, complex or non-rotationally symmetrical shapes of the combustion space, e.g. flower like, having special shapes related to the orientation of the fuel spray jets
    • F02B23/0693Unconventional, complex or non-rotationally symmetrical shapes of the combustion space, e.g. flower like, having special shapes related to the orientation of the fuel spray jets the combustion space consisting of step-wise widened multiple zones of different depth
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02BINTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B29/00Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
    • F02B29/04Cooling of air intake supply
    • F02B29/0406Layout of the intake air cooling or coolant circuit
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02DCONTROLLING COMBUSTION ENGINES
    • F02D2250/00Engine control related to specific problems or objectives
    • F02D2250/36Control for minimising NOx emissions
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02DCONTROLLING COMBUSTION ENGINES
    • F02D41/00Electrical control of supply of combustible mixture or its constituents
    • F02D41/0025Controlling engines characterised by use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
    • F02D41/0047Controlling exhaust gas recirculation [EGR]
    • F02D41/005Controlling exhaust gas recirculation [EGR] according to engine operating conditions
    • F02D41/0057Specific combustion modes
    • YGENERAL 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
    • Y02TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02TCLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00Road transport of goods or passengers
    • Y02T10/10Internal combustion engine [ICE] based vehicles
    • Y02T10/12Technologies for the improvement of indicated efficiency of a conventional ICE
    • Y02T10/125Combustion chambers and charge mixing enhancing inside the combustion chamber
    • YGENERAL 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
    • Y02TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02TCLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00Road transport of goods or passengers
    • Y02T10/10Internal combustion engine [ICE] based vehicles
    • Y02T10/14Technologies for the improvement of mechanical efficiency of a conventional ICE
    • Y02T10/144Non naturally aspirated engines, e.g. turbocharging, supercharging
    • YGENERAL 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
    • Y02TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02TCLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00Road transport of goods or passengers
    • Y02T10/10Internal combustion engine [ICE] based vehicles
    • Y02T10/40Engine management systems
    • Y02T10/44Engine management systems controlling fuel supply

Abstract

本发明涉及一种用于运行直接喷射柴油内燃机的方法,带有至少一个在气缸(24)内往复移动的活塞(27),其中,内燃机这样运行,使燃油在低于NOx-形成温度的局部温度下并以高于炭黑形成极限的局部空气比进行燃烧,其中,燃油喷射在曲柄转角50°和5°之间的范围内在压缩阶段的上止点之前开始并回收废气,其中,废气回收率约为50%-70%。 The present invention relates to a method for operating a direct injection diesel engine, having at least one cylinder (24) within a reciprocating piston (27), wherein the internal combustion engine is operated such that the temperature of the fuel below the NOx- partially formed and local air at a temperature higher than the ratio of carbon black to form a combustion limit, wherein the fuel injection before top dead center between inner range 5 ° and 50 ° crank angle and the compression phase starts recovering the exhaust gas, wherein the gas recovery rate of about 50% -70%. 为达到特别低的氮氧化物-和炭黑排放,提供至少一个活塞(27),带有一个挤压面(34)和一个环形活塞盆形燃烧室(28)和一个处于挤压面(34)与活塞盆形燃烧室(28)之间过渡区内的收缩部位(29);在活塞(27)向上运动时,产生一种从外向内对着活塞盆形燃烧室(28)的挤压流(43);燃油至少主要向环形活塞盆形燃烧室(28)内喷射,并通过挤压流(43)沿活塞盆形燃烧室侧壁(31)和/或活塞底(32)在至少部分汽化下输送。 In order to achieve particularly low nitrogen oxide - and black carbon, at least one piston (27), (34) and an annular piston having a combustion bowl-shaped pressing surface (28) and at a pressing surface (34 ) and cup-shaped piston combustion chamber (constriction (29) between the transition region 28); while (27) in the upward movement of the piston, to produce a pressed from the outside against the combustion cup-shaped piston (28) stream (43); at least the main fuel to a combustion chamber injection pot-shaped annular piston (28), by extrusion and the stream (43) along the side wall of the combustion chamber bowl-shaped piston (31) and / or piston bottom (32) at least conveying the partially vaporized.

Description

用于运行直接喷射柴油内燃机的方法技术领域本发明涉及一种用于运行直接喷射柴油内燃机的方法,带有至少一个在气缸内往复移动的活塞,其中,内燃t腿样运行,1M油在低于N0x-形淑鹏的局咅鹏下并以高于炭黑形成极限的局部空气比进行燃烧,其中,燃油喷射在曲柄转角50。 TECHNICAL FIELD The direct injection diesel engine for operating the present invention relates to a method for operating a direct injection diesel engine, with at least one reciprocating piston in a cylinder, wherein the internal combustion t-like legs run, 1M in low oil N0x- shaped in Shu Peng Peng Board Pou and higher than the lower limit of the carbon black forming local air ratio of the combustion, wherein the fuel injection in the crank angle 50. 和5°之间的范围内在臓阶段的上止点之前开始并回收废气,其中,賠回收率约为50%-70%。 And recovering the exhaust gas before the start and the internal phase Zang range of between 5 ° dead center, which lost about 50% -70% recovery. 此外,本发明还涉及一种用于实施该方法的一种内燃机。 Further, the present invention relates to a method for an internal combustion engine of the embodiment. 背景技术采用内部燃烧的内燃机中燃^1程駐要的参数是,燃烧过程烧开始的相位、气缸压力的最g以及峰ilffi力。 BACKGROUND internal combustion engine using the fuel in the path parameter ^ 1 is to be in the combustion process burning phase, the best g and the cylinder pressure peak force ilffi started. 在基本上皿直接喷射燃油量的自点«行燃烧的内燃机中,这些参数关键^aai喷油时间点、充气成分和点火延迟来确定。 In the direct injection internal combustion engine substantially dish fuel quantity from the point «line of burners, these key parameters ^ aai injection time point, the charge composition and an ignition delay determined. 这些参数本身由大量影响因素决定,例如像自、燃油量、进气MiS、增压压力、有^CE縮比、气缸充量的废气含量和割牛,。 These parameters are determined by a large number of factors themselves, such as for example from the amount of fuel, the intake air MiS, the supercharging pressure, there ^ CE compression ratio, the exhaust gas contents of the cylinder charge and cut the cattle. 严格的法律规定使m^设if燃烧方法时,必须不断开辟新的途径,以1>柴油内燃机J黑颗粒和NOx-排放的排出物。 Strict statutory provisions that when m ^ combustion method if provided, must constantly open new avenues to 1> J diesel engine discharges black particles and NOx- emissions. 公知的M、废气中NOx-和炭黑排放的方法^Mil^前喷油时间点加大点火延迟,从而舰稀薄的燃油-空气混仏的自点鄉亍燃烧。 M is well known, the method in the exhaust gas and the carbon black NOx- emissions ^ Mil ^ time before the point of injection to increase the ignition delay, so the ship lean fuel - air mixture from point Fo rural combustion right foot. 在这里一种可行的方案称为HCLI-方法(Homogenous Charge Late Injection)。 Here called a feasible solution HCLI- method (Homogenous Charge Late Injection). 如果燃油喷射在压縮阶段的±±点之前足够远进行,那么产生这种混^形成,由此产生一种在一定禾^±提敵昆合的燃油-空气混^。 If the fuel injection phase before the compression point ±± be far enough, then it generates such a mixed ^ formed, thereby producing a certain fuel A ± ^ Wo mentioned Kun engaging enemy - air mix ^. MM气回收可以,IJ将燃烧,保持W" N0x-形,万要求的最《g以下。美国专利US 6.338.245 Bl介绍了一种按照HCLI-方法工作的柴油内燃机,其中,燃烧^g和点火延ifi样调整,在低和中部分负荷范围内使燃烧M低于N0x-形mS和局部空气比高于对炭黑形戯键的数值。燃烧鹏掛仿面舰改'顿气回收率,点火延迟MJt油喷射时间点进行控制。在中和高负荷情况下,燃烧M尽可能陶氐,使其既M^、 N0x-也M^、炭黑形成。此外,公知柴油内燃机的活塞采用基本上环形的活塞盆形燃烧室构成。fet匕方面,在活,面与活塞盆形燃,之间的a:渡区内设置一个收缩部位,构成一个相当窄的通;«断面。M窄的输送横断面掛共一种高混^n形成會遣,由此燃油处理得至鹏显改善。带有这种环照舌塞盆形燃體的活塞,基本由公开专利EP 0 383 001 Al、 DE 1 122 325 AS、 AT 380 311 B、 DE 21 36 594 Al、 DE 974 449 C或者JP 60- MM gas can be recovered, the combustion IJ, holding W "N0x- shape, Wan most requested" g or less. U.S. Patent No. US 6.338.245 Bl describes a diesel engine in accordance with one of the working methods HCLI-, wherein the combustion ^ g and ifi ignition delay adjustment sample, and low recovery section below N0x- M-shaped combustion mS and local air ratio higher than the value of the carbon black form the load range of the play button. Peng hanging imitation combustion modified surface ship 'Benton gas ignition control delay time MJt oil injection point. in the medium and high load conditions, the combustion M Di as pottery, making it both M ^, N0x- also M ^, carbon black formation. Furthermore, well-known diesel engine using a piston a substantially annular piston combustion bowl-shaped configuration .fet dagger aspect, a is between live, pot-shaped combustion surface of the piston, of: crossing a constriction zone is provided, constituting a relatively narrow pass; << narrow section .M conveying a highly cross linked co-mixed would form sent ^ n, thereby to obtain a fuel processing Peng significantly improve the piston ring according with such a tongue-shaped combustion bowl plug body consisting essentially of Patent EP 0 383 001 Al , DE 1 122 325 AS, AT 380 311 B, DE 21 36 594 Al, DE 974 449 C or JP 60- 206960 A是已知的。在常规运行的内燃机中,禾U用这种活塞对内燃机的运份封妒生如下具有优点的效果:可以提高烟气限制的满负荷;可以实现高压缩,从中通过更小的点火延迟产生更低的燃烧噪声、更低的體化合物排放、发动机更有利的起动特性和提高内燃机的效率;此外产生的可能性是将点火时间在方向上靠后延期,M31混^形成會糧在更长时间间隔上保持高水平这种事实,没有明显的烟气、消耗和HC上升。这种可能性意據主要是降低了織化物、燃烧噪声和气缸峰(U1力。此外,公开专利DE 11 22 325 Cl已知一种带有活塞盆形燃烧室和收縮部位的活塞, 其中,在挤压面和收縮部位之间具有一,型。在按照HCLI-方法工作的内燃机中,迄今为止不j顿这种带有深收縮活塞,燃^ 的活塞样式,因为迄今为ihA们认为,由于深活塞娜燃驗和很强的挤压》紘动能力和热力 . 206960 A known internal combustion engine is in normal operation, this piston parts Wo U closure operation of the internal combustion engine Jealous green advantageous effect as follows: the flue gas can be improved full load limit; can achieve high compression, to pass therethrough less ignition delay results in a lower combustion noise, lower emissions of compounds, a more favorable starting characteristics of the engine and increase the efficiency of the internal combustion engine; moreover the possibility of ignition timing is delayed in the rearward direction, M31 mixed ^ the formation of grain held on the fact that high levels of longer intervals, no significant fumes, and HC increased consumption. According to this possibility is intended mainly to reduce the fabric thereof, and the cylinder combustion noise peaks (U1 force. in addition the piston disclosed in Patent No. DE 11 22 325 Cl discloses a pot-shaped piston having a combustion chamber and the constriction, wherein between the pressing surface and the portion having a contraction type in the internal combustion engine operating according to the method HCLI- So far no such j Dayton with deep contraction of the piston, the piston combustion ^ style, because so far ihA believe that, due to the depth of experience and a strong burning alive Serena squeeze "hung kinetic force and heat 的效率会变得过差。美国专利US6.158.413A因此提出首先抑制挤压流,其中,使用带有非常扁平的活塞盆形燃烧室的活塞。发明内容本发明任务在于,对用于运行内燃机的HCLI-方法这样进行改进,使其一方面可以进一步降低織化物和炭黑排放,另一方耐以超U扩大可以在HCLI-运行中行驶的负荷范围。依据本发明该任务由此得以实现,即^i共至少一个活塞,带有至少一个挤压面和一个环股舌塞,燃烧室以及一个在挤压面与活塞盆形»^之间迚渡区内的收缩部位;在活塞向Jdi动时,产生一种/"响内对着活塞盆形燃驗的挤压流;燃油至少主要向环職塞,燃,内喷射,并MW压流沿活塞盆形燃,侧壁和/或活塞底在至少部分汽化下输送。 Efficiency becomes too poor. U.S. Patent No. US6.158.413A extrusion is therefore proposed to suppress first stream, wherein a piston with a piston bowl is flat-shaped combustion chamber. SUMMARY OF INVENTION The object of the present invention is that, for operating an internal combustion engine of HCLI- of such a method to improve, on the one hand it was possible to further reduce a textured black carbon and the other U-resistant super-load range can be expanded with the HCLI- operation. Thus according to the present invention this object is achieved, i.e., at least one piston co ^ I, having at least one surface and a pressing ring Unit tongue plug, a combustion chamber and a piston at the bowl-shaped surface of the pressing »constriction Zhong transition zone between ^; the piston to Jdi when moving, produce a / "pot-shaped inner ring pressing against the plug flow combustion test; plug the ring at least a major fuel level, fuel, the injection pressure and flow in MW piston combustion bowl-shaped, the side walls and / or piston bottom conveyed under at least partial vaporization. 燃油射束&tk方面喷入^A活塞^^燃;^内的挤压流内。 Fuel is injected into the beam & tk aspect ^^ ^ A combustion piston; ^ in the extrusion stream. 挤压流将大部^M油输送到活塞盆形燃烧室内,在那里燃皿化并与流入的空气进行?,均匀的混合。 Most pressing ^ M oil stream fed to the combustion chamber of the piston bowl shape, where the dish of the fuel and air flowing?, Uniform mixing. 活塞, 燃烧室内的流动取决于是否存在带有涡流或者无涡流的进气流。 The piston, the combustion chamber into the flow depends on the presence of air with or without swirl vortices. 因此在依据本发明的一种实施方案中,在气缸内产生一种涡流数》1的带有涡流的进气流,而扁油^©«压流沿活塞鄉燃驢侧壁,在至少部分汽化下向活塞底方向并继變沿活塞底向盆形燃烧室中心输送。 Therefore, in accordance with one embodiment of the present invention, to produce a swirl number "of the intake air flow with a swirl in the cylinder, the flat oil ^ ©« rural fuel flow in direction of the piston sidewall donkey, at least partially vaporizing under the direction of the bottom of the piston and further to change direction of the piston bowl-shaped bottom of the combustion chamber to the delivery center. 涡流在压縮阶段期间保持在活塞^^燃烧室的内部。 ^^ vortex held inside the piston combustion chamber during the compression phase. 而在另一实施方案中则相反,在气缸内产生一种涡流数〈1的无涡流的进气流,而扁油Miil齐压流在至少部分汽化下从盆形燃體中心,沿活塞底向活塞盆形燃烧室侦蝰并继续向收縮部位输送。 While on the contrary in another embodiment, to produce a number of <1 free vortex swirl intake air in the cylinder, and pressed flat together Miil oil flow at least partially vaporized fuel from the center of the basin-shaped, the direction of the piston bottom pot-shaped combustion chamber of the piston and continues to detect viper conveyed to constriction. 情况令人惊异地表明,Mii安装活塞盆形燃;^,起动能力在按HCLl-方法工作的内燃丰;U:并没有明显变差。 Surprisingly case show, the pot-shaped piston mounted Mii fuel; ^, startability of the internal combustion abundance working method according HCLl-; U: not significantly deteriorated. 挤压皿成的热力学的效率的损失,通过活塞盆形燃烧室内得到改善的混合气处理,可以明显抵消高涡流的后果。 Loss of efficiency of the thermodynamic pressed into the dish, mixed gas is improved by the treatment tub-shaped piston combustion chamber, can significantly offset the consequences of a high vortex. 在此方面,最好将燃油向活塞的收縮部位方向喷射,其中,喷射开始时大部分燃油量至少一个燃油射束的射束轴线的切合点,处于盆形燃烧室侧壁和挤压面之间的一个区域内, 该区域包括悬挂壁区、收缩部位以及挤压面与收縮部位之间的进气区。 In this regard, the fuel is preferably injected into the constriction direction of the piston, wherein, when the fuel injection amount of at least a majority of the start of fuel to meet the point of the beam of the beam axis, and in the pot-shaped combustion chamber pressing surfaces of the side walls a region between the wall region comprises a suspension zone, and a constriction zone between the pressing surface of the intake air and the constriction. 在常规的柴油内燃机中,燃油的切合点和喷射时间点通常这样选择,使燃油在喷射开始时- 与负荷无关-射中收縮部位下面的悬挂壁区。 In a conventional diesel engine, the fuel injection time point and a meet point is generally selected so that when the fuel injection start - independent of the load - the constriction exit wall region following the suspension. 在本发明的主题中,切合点在低负荷下根据活塞盆形燃烧室内部悬挂壁区的一个区i或进fiH周整,而且随着负荷的上升切合点向收縮部位的方向移动。 In the subject of the present invention, at low load points meet the internal combustion hanging a pot-shaped piston region into the wall region i or fiH entire periphery, with the rising of load and meet the point moves in the direction of the constriction. 这一点可以MI前喷油时间点达到。 This can be achieved MI before the injection point in time. 由此部分燃油-与挤压流相反-喷射到活塞和气缸盖之间的间隙内。 Whereby part of the fuel - opposite to the extrusion flow - is injected into the gap between the piston and the cylinder head. 喷射到活«面和气缸盖之间间隙内的大部分燃油被挤压流带入活塞盆形燃體内。 Most of the fuel injected into the gap between the living «faces the cylinder head of the piston is pressed into the pot-shaped fuel flow body. 这一点有禾哋陶氐HC-和CO"排放情况下提高了空气分布和混^处理。燃油-空气混^既在活塞盆形»^内也在活»面和气缸盖之间的间隙内进行燃烧。因为内燃机在50%与70%之间这一相当高的废气回收率下运行,所以局部燃烧, 处于N0x-形jM^以下。局部过量空气系数保持條黑形^l及限以上。鹏回收可以舰外部或者内部的废气回收装置进行,或f"ilil外部和内部的废气回收装置与可变的阀门配气组誠行。 This has improved air distribution and processing the mixture ^ "emissions Wo Tao Mi Di HC- and CO fuel - air mixing bowl-shaped piston both ^» also a gap between the inner live ^ »face of the cylinder head combustion because the engine is running at between 50 and 70% of the relatively high recovery of the exhaust gas, the partial combustion, in the following N0x- shaped jM ^ the local excess air ratio of the holding strip-shaped black ^ l and more limited. Peng recycling exhaust gas recovery can be outside or inside the ship is, or f "and the variable exhaust gas recovery ilil external and internal gas distribution valve group Cheng rows. 并且,外部废气回收舰排气阶乾期间打开进气阀和/^MiiS气阶段期间打开排气阀进行。 And, opening the inlet valve and / ^ MiiS opening the exhaust valve during the gas phase during the exhaust stage for external dry gas recovery ship. 燃油喷射在500和2500 bar之间的喷油压力下进行。 Injection at the fuel injection pressure of between 500 and 2500 bar for. 燃烧重点处于上止点后最高10°曲柄转角前的IO。 Key before combustion in the IO up ATDC 10 ° crank angle. 之间,由此产生一种非常高的效率。 Between, thereby producing a very high efficiency. 内燃机以约lO - 2.0 的非局部空气比运行。 The internal combustion engine from about lO - 2.0 Non-local air ratio operation. 为实施该方法而使用一种内燃机,它带有至少一个用于直接燃油喷射的喷射装置,一个it^回收装置和至少一个在气缸内往复移动的活塞,该活塞具有一,明的挤压面和一个环形的活塞盆形燃^。 The method used to implement an internal combustion engine, with which at least one injection means for direct injection of fuel, a recovery it ^ and at least one reciprocates within the cylinder piston has a Ming pressing surfaces and a cup-shaped annular piston combustion ^. 在此方面,活塞在挤压面和活塞盆形燃,之间的过渡区内具有一个圆形的收縮部位。 In this regard, the transition zone between the piston and the piston pressing surface of the cup-shaped combustion, having a circular constriction. 由此一方面产生一种鲜明的挤压流,而另一方面超lj液流以相当高的速度i/HA盆形燃烧室内。 Thereby to produce a distinctive aspect of the extruded flow, on the other hand over lj stream at a relatively high speed i / HA pot-shaped combustion chamber. 活塞盆形燃凝室内相当高的涡流水平面有利地影响充分燃凝状况,由此可以明显降低HC-和C(Hf放。特另陏利的是,活塞盆形燃烧室这群角定尺寸, 使其适用最綠形燃烧錢径DB与活塞直径D之比为:0.5 〈 DB/D < 0.7,而且活塞盆形燃烧室这样确定尺寸,使其适用最爐形燃烧室深度ft与活塞直径D之比为:0.12〈ft/D〈0.22。由此可以将自由燃油射束长度保持在尽可能大的程度上。为构成鲜明的挤压流, 最好活塞盆形燃鹏这样确定尺寸,使其翻收缩部位的直径Dt与最大盆形燃體直径db 之比为:0. 7 < Dr/a < 0. 95。在挤压面和收缩部位之间作为进气区设置一个环形造型,带有平整的底部和圆柱形的壁。最好1雜型具有最:^»燃體深度5%与15%之间的深度,该造型具有至少部分圆柱形的壁,而且该造型在壁的区域内具有大于收縮離直径10% - 20%之间的直径。iia该造型在活塞下行时 Condensate pot-shaped combustion chamber of the piston a relatively high level favorably affect the full vortex fuel hypercoagulable state, and thus can significantly reduce HC- C (Hf discharge. Laid Another advantageous Duo, a piston combustion bowl-shaped angle sized group, making it suitable shape than the most green combustion money diameter DB of the piston diameter D is: 0.5 <DB / D <0.7, the pot-shaped piston and the combustion chamber is dimensioned so that the most suitable depth ft furnace combustion chambers and the piston diameter D ratio of: 0.12 <ft / D <0.22 it can be maintained at the greatest possible extent the free length of the fuel jet streams extruded in sharp, burning is preferably cup-shaped piston Peng dimensioned such that. than the diameter of the constriction diameter Dt turn and db between the maximum fuel bowl-shaped body is:. 0 7 <Dr / a <0. 95. as the inlet is provided an annular region between the pressing surface and the molding shrinkage of parts, with It has a flat bottom and a cylindrical wall type having most preferably 1 heteroatom: ^ a depth of between 5% and 15% of »fuel volume depth, the molding having at least partially cylindrical wall, and the wall region of the molding 20% of the diameter of the molding downlink .iia piston - the shrinkage of greater than 10% from the diameter 降低从活塞盆形燃烧室的径向流出速度。由此燃料部分不是沿活St瑞面, 而是在轴向输送到气缸盖。附图说明下面借助附图对本发明进t辨细说明。其中: 图1示出用于实施依据本发明方法的内燃机; 图2a和2b示出该内燃机气缸的纵剖面; 图3示出图2a的局部放大图ni,以及图4示出依据现有技术水平的该局部放大图。具体实施方式图1示出具有进气收織2和排气收織3的内燃机1。内燃机1 M3im涡轮增压器4增压,后者具有废气驱动的涡轮5和ilil涡轮5驱动的压縮机6。沿压缩机6的逆流在进气恻上设置一个增压空气7賴職7。此外,高压废气回收系统8在废气线路10和进气管11之间具有第一废气回收管9。 戯回收系统8具有废气回收7转卩器12和废气回收阀13。根据排气线路10和进气管11 之间的压差,第一废气回收管9内还可以具有一个it^ 14,以鹏制或提高m回收率。除了该高 Decreases from the radial outflow rate of the combustion bowl-shaped piston part whereby the fuel is not living in St Face, but conveyed to the cylinder head in the axial direction. BRIEF DESCRIPTION t identified by reference into the text description of the present invention, wherein : FIG. 1 shows an internal combustion engine for carrying out the method according to the present invention; Figures 2a and 2b show a longitudinal section of a cylinder of the internal combustion engine; FIG. 3 shows a partial view 2a of ni, and Figure 4 shows an enlarged view of a level according to the prior art this enlarged view. DETAILED DESCRIPTION Figure 1 illustrates an internal combustion engine 3 1. 4 1 M3im turbocharger supercharging, an exhaust gas turbine which is driven ilil 5 and having intake and exhaust close close woven fabric 2 6. the turbo compressor 5 is driven in the reverse flow of the compressor 6 is provided in a pressurized air intake depends sad 7 post 7. in addition, the high-pressure exhaust gas recirculation system 8 between the exhaust gas line 10 and the intake pipe 11 having a first 9. the exhaust gas recirculation pipe 8 play recovery system having exhaust gas recirculation switch 7 Jie 12 and the exhaust gas recirculation valve 13. the differential pressure between the exhaust line 11 and the intake pipe 10, a first exhaust gas recirculation pipe 9 it may also have a ^ 14, or to improve m Peng recovery system. in addition to this high 废气回收系统8外,还具有一个沿涡轮5的顺流和沿压縮机6的逆流的低压废气回收系统15,其中,在废气管16内沿1t^滤清器17的顺流分支第二废气回收管18 并沿压縮机6的逆i顿AiS气管19内。财卜,在第二it^回收管18内设置一个废气回收7賴職20和一个約回收阀21。为控制戯回收率在約管16内沿錢的顺流设置一个鹏阀22。沿第一废气回收管9支线的逆流在it^线路10内设置一个氧化催化器23,去除HC、 CO和颗粒排放的挥发部分。副作用是与此同时賠、鹏提高并因此将附啲能量输送到涡轮5。 Exhaust gas recirculation system 8, also having a downstream direction along a turbine 5 and a low pressure compressor exhaust gas recirculation system 15 of counterflow 6, wherein, in the exhaust pipe 16 along the downstream branch 17 of the second filter 1t ^ 18, and the exhaust gas recovery pipe 6 of the compressor in the reverse i Dayton AiS pipe 19. Choi Bu, in the second recovery pipe 18 is provided it ^ a gas recovery system 7 and 20 depends on a level of about 21 to control the recovery valve play recovery rate along money within about a pipe 16 is provided downstream of valve 22. Peng exhaust gas recirculation pipe 9 along the first leg of the reverse flow it ^ 10 disposed within an oxidation catalyst 23, part of the volatiles were removed HC, CO and particulate emissions line side effects are lost at the same time, and thus increase the attachment Peng GOD energy delivered to the turbine 5. 叙匕方面,原则上也可以将氧化催化器23沿鹏回收管9分支柳顷流设置。 Syria dagger aspect, the principle may be the oxidation catalyst 23 along the recovery pipe 9 branches Liu Peng stream are provided. 图l所示的采用職化催化器23顺流支线的设斷具有的优点是it^賴卩器12受至哽小的污染, 但缺点是由于废气?鹏升高,需要鹏回收7賴P器12具有更高的)ti口能力。 FIG. L 23 disposed downstream of the branch-off has the advantage of using the catalyst level is shown it ^ Lai Jie 12 to choking by small contamination, but the drawback is due to the exhaust? Peng increased, Lai P 7 need to recover Peng 12 has higher) Ti port capability. 内燃机1的*气缸24具有至少一个将柴油直接喷射到燃;^ 26内的喷油阀25,其喷油开始可以在上lh点前50。 241 * cylinder engine having at least one diesel fuel is directly injected into the combustion; ^ 26 fuel injection valve 25 in which injection can be started before the 50 points lh. 至5°曲柄转角之间的范围内变化。 Varied in the range between 5 ° to the crank angle. 喷油压力在此方面处于500和2500 bar之间。 In this regard injection pressure is between 500 and 2500 bar. 在气缸24内往复移动的活塞27具有一个基本上旋转对称的环職塞^^燃鹏28, 设计成一^ht挂壁区30的收縮部位29。 Reciprocating piston 27 within a cylinder 24 having a substantially rotationally symmetrical ring ^^ fuel level Peng plug 28, 29 designed as a constriction ^ ht Wall region 30. 活塞盆形燃,28的侧M用31、活塞皿用32以及凸起的郷»室中心釆用44标注。 Fuel bowl-shaped piston, with the side 31 of the M 28, with the piston 32 and the dish Hongo »preclude the use of the center of the chamber 44 marked protrusion. 在活m^瑞面33上,收縮部位29的外面设计成一个挤压面34。 In living m ^ Face 33, 29 outside the constriction is designed as a pressing surface 34. 活塞27的几何开沐、 喷油时间点和喷油阀25的喷油几何皿这样确定,使喷油射束的轴线35X寸着环绕侧壁31 和挤压面34之间收縮部位29的一个区域36 (图3)。 Mu open geometry of the piston 27, the fuel injection time point and the fuel injection valve 25 of the injector geometry dish determined such that the axis of the beam injection inch 35X with a surrounding side wall 29 between the constriction 31 and the pressing surface 34 region 36 (FIG. 3). 该区域36包括悬挂壁区30、收缩部位29本身以及皿一个环形的造型37a在挤压面34和收縮部位29之间构成的进气区37。 The wall region 36 comprises a suspension zone 30, constriction 29 itself and the shape of an annular dish inlet region 37a between the pressing surfaces 34 and 29 constituting the constriction 37. 造型37a具有一个平整的底部37b和一个圆柱形的壁37c,其中,迚渡^gr设计为约1 ■和活塞盆形燃烧室深度ft的50%之间。 Shape having a flat bottom 37a and a cylindrical wall 37b 37c, which is designed to Zhong ^ gr crossing between about 50% and the piston 1 ■ ft depth of cup-shaped combustion chamber. 造型37a的深度h约为最M形燃,深度ft的5%-15%。 Modeling 37a depth h is approximately M-shaped combustion most 5% -15% of the depth of ft. 造型37a的直径D,大于收縮部位29直径Dr的10。 37a styling diameter D, is greater than the diameter Dr of the constriction 29 10. /。 /. -20%。 -20%. 大部分喷射的燃油量第一喷油射束轴线35固有的第一切合点38,处于区域36的内部并取决于负荷的变化。 Most of the injected fuel quantity of the first fuel injection to the inherent first beam axis 35 relevant points 38, 36 in the inner region and on the load changes. 在低负荷时,切合点38处,挂壁区30的区域内。 At low load, meet at point 38, the inner region of the wall hanging region 30. 附图符号39 ,非常低负荷时最下部的切合点38。 Reference numeral 39, at very low loads the lowermost point 38 meet. 随着负荷上升,切合点38向挤压面34的方向移动,如图3中箭头P2所示。 As the load increases, point 38 moves in a direction to meet the pressing surface 34, as shown by arrow P2 in FIG. 图3中附图符号40表示切合点38的«±部极端位置。 FIG. 3 reference numeral 40 denotes meet «± portion 38 of the extreme position of the point. 因此在较高负荷时,一部分喷射的燃油逆挤压流43或43a的方向喷射至鹏压面34和气缸盖42之间的挤压空间41内。 Therefore, when a high load, the inverse proportion of the fuel injector 43 or 43a in the extrusion direction of flow is injected to the cylinder head 34 Peng pressing surface 41 pressing the space 42 between. 在图2b中,附图符号43表示带有涡流的进气流中的挤压流,而附图符号43a则^^涡流的进气流中的挤压流。 In Figure 2b, reference numeral 43 denotes pressed into a gas stream with the vortex flow, and reference numeral 43a is pressed ^^ stream flowing into the vortex. 3la活塞27的向JJg动,切合点38在喷油期间向活塞皿燃烧室28 的方向移动,如箭头&所示。 3la piston to move JJg 27 relevant points of the piston 38 moves toward the combustion chamber 28 is dish during injection, as shown by arrow &. 在活塞27向上运动时,31»压面34产生的挤压流43、 43a 的作用是,将一部分SA在活M面33和气缸盖42之间构成的挤压空间41内的燃油,由挤压流43、 43a带到活塞盆形燃體28的方向上并在那里汽化。 When the upward movement of the piston 27, the extrusion 31 »pressing surface 34 produces a flow effect 43, 43a is a portion of the fuel in the SA 41 M alive between the cylinder head surface 33 constituting the pressing space 42, the squeeze pressure stream 43, 43a of the piston to the combustion bowl-shaped body 28 and in a direction where vaporized. 由此形成与空气特别好的充分混合,从而一方面提高HCLI-运行中可以超啲最大负荷,而另一方面可以进一步降低HC-和CO"排放。燃烧既在活塞盆形燃烧室28的内部,也在挤压空间41的区域内进行。ffiilit型37a,在活塞27向下运动时明显降低了径向流出速度,由此大大减少了向活塞端面33上和继续向气缸壁输送的燃油部分。由此只有少ftM烧残留物iSA发动机油内。为进行比较,图4示出在常规分层运行的柴油内燃ai:止点区域内燃油喷射开始时喷油射束第一切合点的区域36'。燃油的该区域36' _与负荷状态无关_通常始终处于悬挂壁区30的区域内。因此切合点不移动。喷油的开鄉寺另提在下部部分负荷区域内相对提前处于压縮行程内,也就^h止点之前约50° -5°的曲柄转角时,由此为构成局部均匀的混^较长的点火延迟,可供预混合的燃烧使用。通过鲜明的预混合和稀释 Thereby forming a sufficiently good mixing with the air in particular, on the one hand to improve the operation can be super HCLI- GOD maximum load, on the other hand can be further reduced HC- and CO "emissions in an internal combustion piston both pot-shaped combustion chamber 28 of the for .ffiilit type region 37a, the space 41 are pressed, the downward movement of the piston 27 when the radial outflow velocity decreased, thereby greatly reducing the upper end surface of the piston 33 and the cylinder wall to further transport to the fuel portion thus only a small ftM the burnt engine oil residue iSA for comparison, Figure 4 illustrates operation of diesel combustion in conventional hierarchical ai: a first beam injection region meet at the beginning of the fuel injection point within the dead zone 36 'of fuel in the region 36' _ _ regardless of the state of the load is always in the region generally suspended wall region 30. Thus meet point does not move. another injection opening rural temple mentioned in the part-load region at a lower pressure relative advance the compression stroke, it ^ h before top dead center when the crank angle of about 50 ° -5 °, thereby constituting locally homogenous mix ^ longer ignition delay, for the use of premixed combustion by premixing distinct and dilution 可以超贩低的炭黑-和N0x-排放值。在此方面,局部过量空气系辦台终高于对炭黑形成关键的柳艮。舰50% - 70%之间的高废气回收率达到,局部燃烧鹏台终低于最小的織化物形^So对外部賠的回收^MW气阶段期间打开进气阀和/^Mia气阶si月间打开排气阀^ia行的。掛仿面,喷油在500 - 2500 bar之间的压力时进行。长的点火延迟的作用是,将燃烧阶段推迟到环纟处止点的效率最佳位置。燃烧重点处于上止点后最高10。曲柄转角前的IO。之间,由此可达到一种高效率。高的废气回收率可以或者^M31外部的废气回收装置,或者也可以ffiil外部与内部废气回收装置的组合,ilil可变的阀门控制装置实现。为在混^形成时达到一种高涡流,具有优点的是产生涡流的进气道用于产生最高约5个高涡流数。活塞盆形燃體28具有一个相当大的最大直径Db,其中,DB与D之比处于0.5 - 0.7 的范围 Ultra low carbon black can stall - N0x- and emission values ​​in this regard, the local excess air ratio than do the final stage carbon black forming critical Liu Gen ship 50% - 70% higher recovery rate of the exhaust gas reaches , local combustion Peng final stage was lower than the minimum shape of the knitting ^ So the recovery of the external compensation opening the inlet valve and ^ / ^ Mia steps between the gas exhaust valve opens si ^ months IA MW gas phase during row. hanging surface imitation , the fuel injection 500-- performed between the pressure bar 2500 long ignition delay action is postponed to the combustion stage efficiency optimum position at the dead center of the combustion focus ring is Si after top dead center of the crank 10. the highest. the angle between the front IO., whereby to achieve a high efficiency or high exhaust gas recovery can ^ M31 external exhaust gas recovery, or may be a combination of external and internal exhaust gas recovery, ILIL variable valve ffiil control means implemented. ^ mixed as to achieve a high vortex forming, it is advantageous for producing a swirl of intake of up to about five high swirl number. the piston 28 has a cup-shaped fuel a relatively large maximum diameter ratio Db, wherein, DB and D is in the 0.5 - 0.7 range 。最大活塞深度ft与活塞直径D之比,以有利的方式处于0.12和0.22之间。由此可以产生一种长的自由射束长度,它对混^形成具有优点。为构成一种强挤压流43, 收縮部位29的直径DT与最大活塞直径De之比处于0.7 - 0.95之间。由lt爐至iJJSA活塞盆形燃鹏28内的高进气驗,这有利亍燃油-空气混仏的均匀化。喷油射束35的几何开沐以及活塞^^燃烧室28的几何开沐,可以对常规的柴油内燃机在满负荷離細亍优化。 . Ft depth ratio of maximum piston diameter D of the piston, in an advantageous manner between 0.12 and 0.22. It can be produced free jet length A long, it is formed having mixed ^ advantages of strong constitute a crowded stream 43 pressure, constriction of the diameter DT 29 and the ratio of maximum piston diameter De is 0.7 - 0.95 of the furnace to iJJSA lt high intake test cup-shaped piston 28 within combustion Peng, which is advantageously right foot fuel - air mixture Fo uniform. beam geometry injection opening 35 and a piston ^^ Mu Mu opening 28 of the burner geometry may be conventional diesel engine at full load from the right foot fine optimization.

Claims (18)

1. 用于运行直接喷射柴油内燃机的方法,带有至少一个在气缸(24)内往复移动的活塞(27),其中,内燃机这样运行,使燃油在低于NOx形成温度的局部温度下并以高于炭黑形成极限的局部空气比进行燃烧,其中,燃油喷射在曲柄转角50°和5°之间的范围内在压缩阶段的上止点之前开始并回收废气,其中,废气回收率约为50%-70%,其特征在于,提供至少一个活塞(27),带有至少一个挤压面(34)和一个环形活塞盆形燃烧室(28)和一个处于挤压面(34)与活塞盆形燃烧室(28)之间过渡区内的收缩部位(29);在活塞(27)向上运动时,产生一种从外向内对着活塞盆形燃烧室(28)的挤压流(43);燃油至少主要向环形活塞盆形燃烧室(28)内喷射,并通过挤压流(43)沿活塞盆形燃烧室侧壁(31)和/或活塞底(32)在至少部分汽化下输送,以及,将燃油向活塞(27)的收缩部位(29)方向喷射,其中,喷 A method for the operation of the local temperature of the direct injection diesel engine, having at least one cylinder (24) within a reciprocating piston (27), wherein the internal combustion engine is operated such that the fuel temperature is lower than the NOx formation and to above limit of the carbon black forming local air ratio for combustion, wherein the fuel injection before top dead center between inner range 5 ° and 50 ° crank angle and the compression phase starts recovering the exhaust gas, wherein the exhaust gas recovery rate is about 50 to 70%, characterized in that at least one piston (27), having at least one pressing surface (34) and an annular piston bowl-shaped combustion chamber (28) and at a pressing surface (34) and the piston bowl shaped combustion chamber constriction (29) between the transition region (28); upward movement of the piston (27), to produce a flow from the outside against the pressing piston bowl-shaped combustion chamber (28) (43) ; at least predominantly within the fuel bowl to the combustion chambers an annular piston (28) injection, and (43) delivered at least partially vaporized by extrusion flow in the basin-shaped side wall of the combustion chamber of the piston (31) and / or piston bottom (32) , and a fuel (29) injected into the direction of the constriction of the piston (27), wherein the spray 开始时大部分燃油量的至少一个燃油射束的射束轴线(35)的切合点(38)处于盆形燃烧室侧壁(31)和挤压面(34)之间的一个区域(36)内,该区域包括悬挂壁区(30)、收缩部位(29)以及挤压面和收缩部位(29)之间的进气区(37),切合点(38)在低负荷下根据活塞盆形燃烧室(28)内部悬挂壁区(30)的一个区域进行调整,随着负荷的上升切合点(38)向收缩部位(29)的方向移动。 Most of the amount of fuel at the beginning of at least one of the fuel beam the beam axis (35) of the relevant points (38) is a basin-shaped area between the side wall of the combustion chamber (31) and the pressing surface (34) (36) within the suspension region comprises a wall region (30), the contraction portion (29) and a pressing surface and the constriction of the intake region (37) between (29), in line with the point (38) at a low load in accordance with the cup-shaped piston a combustion chamber (28) suspended inside the wall region (30) in a region to be adjusted in line with the rise of the load point (38) to the moving direction of the constriction (29).
2. 按权利要求1戶腿的方法,其特征在于,在气缸(24)内产生一种涡流数^1 的带有涡流的进气流,而且燃油iliif齐压流(43)沿活塞盆形燃^侧壁(31)在至少部分汽化下向活塞底(32)方向并继会魏活塞底(32)向盆形燃體中心(44)输送。 2. The method as claimed in one of the legs, characterized in that, to generate in the cylinder (24) A feed stream with a swirl number vortex ^ 1, and the fuel pressure iliif homogeneous flow (43) in the pot-shaped piston combustion ^ sidewall (31) to (32) following the direction of the piston and the bottom of the piston will bottom Wei (32) fed to the combustion bowl-shaped central body (44) at least partially vaporized.
3. 按权利要求1所述的方法,其特征在于,在气缸(24)内产生一种涡流数〈1 的无涡流的进气流,而且燃油313«压流(43)在至少部分汽化下从盆形燃烧室中心(44) 沿活塞底(32)向活塞盆形燃烧室侧壁(31)并继续向收缩部位(29)输送。 3. The method as claimed in claim 1, characterized in that, to produce a swirl number <1 no intake flow swirl in the cylinder (24), and fuel 313 «pressure stream (43) at least partially vaporized from (44) and continues (29) conveying the cup-shaped bottom of the piston along the center of the combustion chamber (32) to the combustion bowl-shaped side wall of the piston (31) to the constriction.
4. 按权利要求l - 3之一戶;M的方法,其特征在于,随着负荷的上升,喷油从±±点之前一个分M^合低部分负荷的约5° - 15。 4. Press as claimed in claim l - one 3; M is a method, wherein, with increasing load, a divided fuel injection from the previous M ^ ±± engagement low part load point from about 5 ° - 15. 的区WS上止点之前约50°曲柄转角提前开始。 WS region approximately 50 ° crank angle before top dead center before the start.
5. 按权利要求l - 3之一戶,的方法,其特征在于,燃油喷射在喷油压力处于500 - 2500 bar之间进行。 5. Press as claimed in claim l - one of the three methods, characterized in that the fuel injection pressure in the injection 500-- performed between 2500 bar.
6. 按权利要求l - 3之一戶,的方法,其特征在于,燃',点处于上止点之前的10° -上止点之后的IO。 6. claimed in claim l - one of the three methods, characterized in that the fuel ', at the point before top dead center 10 ° - IO after top dead center. 之间的曲柄转角范围内。 Within a range between a crank angle.
7. 按权利要求1 - 3之一戶,的方法,其特征在于,非局部空气比在1. 0和2. 0之间调整。 One 3, the method, wherein the non-local air between 1.0 and 2.0 to adjust the ratio of - 7.1 as claimed in claim.
8. 按权利要求l - 3之一戶皿的方法,其特征在于,废气回收在外部和/或内部进行。 8. claimed in claim l - Method One dish 3, characterized in that the exhaust gas recirculation in an external and / or internal.
9. 按权利要求8戶,的方法,其特征在于,外部Jl^回收M3i排气阶段期间打开进气阀和/M舰气阶SI月间打开排气阔进行。 9. The method as claimed in claim 8, characterized in that the external Jl ^ M3i recovered during stage of opening the intake and exhaust / M SI steps between ship gas exhaust opening width for months.
10. 直接喷射柴油内燃机,用于实施按权利要求l - 12之一戶腿的方法,禾,该方法可以对燃油喷射的开始在压縮阶段上止点之前的50°至5°曲柄转角之间的范围内进行调整,以及带有一个戯回收率处于50%^70%之间的废气回收系统,带有至少一个在气缸(24)内往复移动的活塞(27),其特征在于,活塞(27)在其端面(33)上具有至少一个挤压面(34)和一个带有收縮部位(29)的环形活塞盆形燃« (28),基本上成凹形弯曲的侧壁(31)和底部(32),以及一个顶幢(31)与收縮部位之间的悬挂壁区(30), 其中,大部分燃油量的喷油驢(25)燃油射束的至少一个射束轴线(35)对着侧壁(31) 与挤压面(34)之间的一个区域(36),该区域(36)包括悬挂壁区(30)、收縮部位(29) 以及挤压面(34)与收縮部位(29)之间的进气区(37),射束轴线(35)的切合点(38) 在低负荷下根据活塞盆形燃 10. The direct injection diesel engine, for implementing according to claim l - Method of one of the legs 12, Wo, the method may be 50 ° before top dead center to 5 ° of crank angle in the compression stage fuel injection start adjusting a range between, and with an exhaust gas recirculation system is in play recovery between 50% ^ 70%, with a piston (27) in at least one reciprocating within the cylinder (24), characterized in that the piston (27) having a pressing surface at least on its end face (33) (34) and an annular portion with a contraction (29) of the pot-shaped piston combustion «(28), substantially concave curved sidewall (31 ) hanging wall region (30) and a bottom (32), and a top blocks (31) and the constriction, wherein the amount of fuel injection donkey majority (25) of the at least one fuel jet beam axis ( 35) a region (36) between the opposite side walls (31) and the pressing surface (34), the region (36) comprises a suspension wall region (30), the contraction portion (29) and a pressing surface (34) and constricts the intake region (37) between (29), the beam axis (35) of the relevant points (38) at a low load in accordance with the fuel bowl-shaped piston 室(28)内部悬挂壁区(30)的一个区域进行调整,随着负荷的上升切合点(38)向收縮部位(29)的方向移动。 A chamber area (28) suspended inside the wall region (30) is adjusted in line with the rise of the load point (38) to the moving direction of the constriction (29).
11. 按权利要求10戶腿的内燃机,^#征在于,活塞盆形燃體(28)这样确定尺寸,使其适用最大盆形燃烧室直径(ft)与活塞直径(D)之比为:0. 5 < IVD < 0. 7。 Claim 11. The legs 10 of the internal combustion engine, # ^ characterized in that the piston bowl-shaped flame holder (28) is dimensioned such that it applies the maximum diameter of the pot-shaped combustion chamber (ft) and (D) the ratio of piston diameter: 0. 5 <IVD <0. 7.
12. 按权利要求10或11之一戶;M的内燃机,其特征在于,活塞盆形燃烧室(28) 这样确定尺寸,使其适用最大盆形燃^深度(ft)与活塞直径(D)之比为:0.12 < Hb/D 〈0. 22。 12. The one of claims 10 or 11; M of the internal combustion engine, wherein the piston bowl-shaped combustion chamber (28) is dimensioned such that it applies the maximum depth of cup-shaped combustion ^ (ft) and the piston diameter (D) ratio of:. 0.12 <Hb / D <0 22.
13. 按权禾腰求10或11之一戶脱的内燃机,其特征在于,活塞盆形燃烧室(28) 这样确定尺寸,使其适用收縮部位(29)的直径(ft)与最大盆形燃烧室直径(ft)之比为: 0. 7 <线< 0. 95。 13. The required weights Wo waist 10 one or removal of the internal combustion engine 11, characterized in that the piston bowl-shaped combustion chamber (28) is dimensioned such that it applies constriction (29) has a diameter (ft) and a maximum pot-shaped a combustion chamber diameter (ft) ratio of: 0.7 <line <0.95. .
14. 按权利要求10或11之一卵悉的内燃机,期寺征在于,进气区(37)在挤压面(34)与收縮部位(29)之间具有一个环形的造型(37a)。 14. The egg of claim 10 or 11 one of the noted engine, characterized in that in Si, having an annular shape (37a) between the intake region (37) in the pressing surface (34) and the constriction (29).
15. 按权利要求14戶脱的内燃机,^f寺征在于,造型(37a)具有通向活塞盆形燃烧室(28)的平,部(37b)。 15. The internal combustion engine as claimed in claim 14 is off, ^ f Temple characterized in that the shape (37a) having a cup-shaped piston leading to the combustion chamber (28) of the flat portion (37b).
16. 按权利要求14戶脱的内燃机,^ft征在于,造型(37a)具有最大盆形燃^ 深度(ft) 5%和15%之间的深度(h)。 16. The internal combustion engine as claimed in claim 14 is off, ^. Ft characterized in that the shape (37a) having a maximum depth of cup-shaped combustion ^ (ft) depth between 5% and 15% (h).
17. 按权利要求14所述的内燃机,其特征在于,造型(37a)具有一个至少部分圆柱形的壁(37c)。 17. The internal combustion engine according to claim 14, characterized in that the shape (37a) having an at least partially cylindrical wall (37c).
18. 按权利要求17戶脱的内燃机,其特征在于,造型(37a)在壁(37c)区域内具有大于收缩部位(29)直径(EO 10% - 20%之间的直径(D,)。 18. The internal combustion engine as claimed in claim 17 off, characterized in that the molding (37a) greater than the contraction portion (29) diameter (EO 10% in the wall (37c) region - the diameter (D 20% of).
CN 200380106772 2002-12-19 2003-12-18 Method of operating directly injecting diesel engine CN100404814C (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
ATGM860/2002 2002-12-19
AT0086002U AT7204U1 (en) 2002-12-19 2002-12-19 Method for operating a directly injecting diesel internal combustion engine

Publications (2)

Publication Number Publication Date
CN1729354A CN1729354A (en) 2006-02-01
CN100404814C true CN100404814C (en) 2008-07-23

Family

ID=32660421

Family Applications (1)

Application Number Title Priority Date Filing Date
CN 200380106772 CN100404814C (en) 2002-12-19 2003-12-18 Method of operating directly injecting diesel engine

Country Status (5)

Country Link
CN (1) CN100404814C (en)
AT (1) AT7204U1 (en)
AU (1) AU2003287752A1 (en)
DE (1) DE10393905B4 (en)
WO (1) WO2004057167A1 (en)

Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4039382B2 (en) * 2004-03-31 2008-01-30 いすゞ自動車株式会社 diesel engine
DE102004045394A1 (en) * 2004-09-18 2006-03-23 Robert Bosch Gmbh Internal combustion engine
DE102004045634A1 (en) 2004-09-21 2006-04-06 Daimlerchrysler Ag Internal combustion engine
JP3979416B2 (en) 2004-10-01 2007-09-19 いすゞ自動車株式会社 diesel engine
FR2878906A1 (en) * 2004-12-07 2006-06-09 Inst Francais Du Petrole Direct injection internal combustion engine e.g. diesel engine, has fuel injector, and tulip with side wall forming negative inclination angle whose absolute value is equal to half crown angle of fuel jets and at least equal to zero degrees
FR2879247A1 (en) * 2004-12-13 2006-06-16 Renault Sas Combustion chamber for direct injection internal combustion engine, has central injector delivering fuel jet along reduced cord angle, and peripheral part, of tulip, with bursting units to burst injected fuel jets against part along angle
DE102004061028B4 (en) * 2004-12-18 2014-10-23 Pierburg Gmbh Exhaust gas recirculation system
EP1838958A1 (en) * 2005-01-18 2007-10-03 Bayerische Motorenwerke Aktiengesellschaft Vehicle comprising an exhaust gas recirculation system
JP4906055B2 (en) * 2006-02-08 2012-03-28 日野自動車株式会社 Combustion chamber structure of direct injection diesel engine
DE102006020642B4 (en) 2006-05-04 2019-05-23 Daimler Ag Method for operating an internal combustion engine and internal combustion engine for such a method
DE102006054043A1 (en) 2006-11-16 2008-05-21 Volkswagen Ag Internal combustion engine with exhaust gas recirculation
DE102009025404B4 (en) 2009-06-16 2018-01-25 Mtu Friedrichshafen Gmbh Piston for valve-controlled reciprocating piston diesel engine
GB201001562D0 (en) * 2010-01-29 2010-03-17 Ricardo Uk Ltd Direct injection diesel
JP6160564B2 (en) * 2014-06-09 2017-07-12 マツダ株式会社 diesel engine
JP6197750B2 (en) 2014-06-09 2017-09-20 マツダ株式会社 Diesel engine combustion chamber structure
AT518516B1 (en) * 2016-03-10 2018-03-15 Avl List Gmbh Piston for a air compressive internal combustion engine

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE974449C (en) * 1952-02-23 1960-12-29 Maschf Augsburg Nuernberg Ag Running fast Diesel Engine with horizontal in the piston combustion chamber rotationsfoermigem
DE1122325B (en) * 1958-12-02 1962-01-18 Mahle Kg Light alloy pistons for internal combustion engines with a provided in the piston head combustion chamber
JPH0886251A (en) * 1994-09-19 1996-04-02 Nissan Motor Co Ltd diesel engine
US5832880A (en) * 1997-07-28 1998-11-10 Southwest Research Institute Apparatus and method for controlling homogeneous charge compression ignition combustion in diesel engines
JP2000145461A (en) * 1998-11-09 2000-05-26 Toyota Motor Corp Internal combustion engine
EP1045136A1 (en) * 1999-04-13 2000-10-18 DaimlerChrysler AG Method for operating a reciprocating internal combustion engine and injection nozzle for carrying out the method
US6158413A (en) * 1999-03-19 2000-12-12 Nissan Motor Co., Ltd. Direct injection diesel engine
US6338245B1 (en) * 1999-09-17 2002-01-15 Hino Motors, Ltd. Internal combustion engine
US20020056434A1 (en) * 2000-09-29 2002-05-16 Tobias Flamig-Vetter Method of operating a diesel internal combustion engine
EP1251252A1 (en) * 2000-01-25 2002-10-23 Kabushiki Kaisha Toyota Chuo Kenkyusho Direct injection type internal combustion engine
EP1348854A1 (en) * 2002-03-27 2003-10-01 Mazda Motor Corporation Combustion control apparatus for a diesel engine, a diesel engine, combustion control method thereof, computer-readable storage medium, and computer program

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2136594A1 (en) 1970-07-30 1972-02-03
AT380311B (en) * 1983-08-04 1986-05-12 Avl Verbrennungskraft Messtech Piston for diesel engines with direct fuel injection
JPH0373751B2 (en) * 1984-03-31 1991-11-22 Honda Motor Co Ltd
AT399912B (en) * 1989-02-15 1995-08-25 Avl Verbrennungskraft Messtech Air-compressing, valve-controlled internal combustion engine
DE19621635B4 (en) * 1996-05-30 2004-02-05 Audi Ag Diesel engine
US6302080B1 (en) * 1998-07-31 2001-10-16 Denso Corporation Fuel injection system having pre-injection and main injection
DE19953932C2 (en) * 1999-11-10 2002-04-18 Daimler Chrysler Ag Method for operating a reciprocating internal combustion engine
JP2001221050A (en) * 2000-02-10 2001-08-17 Nissan Motor Co Ltd Piston of direct injection diesel engine
FR2806753B1 (en) * 2000-03-27 2005-09-23 Toyota Motor Co Ltd Exhaust gas purifier for internal combustion engine

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE974449C (en) * 1952-02-23 1960-12-29 Maschf Augsburg Nuernberg Ag Running fast Diesel Engine with horizontal in the piston combustion chamber rotationsfoermigem
DE1122325B (en) * 1958-12-02 1962-01-18 Mahle Kg Light alloy pistons for internal combustion engines with a provided in the piston head combustion chamber
JPH0886251A (en) * 1994-09-19 1996-04-02 Nissan Motor Co Ltd diesel engine
US5832880A (en) * 1997-07-28 1998-11-10 Southwest Research Institute Apparatus and method for controlling homogeneous charge compression ignition combustion in diesel engines
JP2000145461A (en) * 1998-11-09 2000-05-26 Toyota Motor Corp Internal combustion engine
US6158413A (en) * 1999-03-19 2000-12-12 Nissan Motor Co., Ltd. Direct injection diesel engine
EP1045136A1 (en) * 1999-04-13 2000-10-18 DaimlerChrysler AG Method for operating a reciprocating internal combustion engine and injection nozzle for carrying out the method
US6338245B1 (en) * 1999-09-17 2002-01-15 Hino Motors, Ltd. Internal combustion engine
EP1251252A1 (en) * 2000-01-25 2002-10-23 Kabushiki Kaisha Toyota Chuo Kenkyusho Direct injection type internal combustion engine
US20020056434A1 (en) * 2000-09-29 2002-05-16 Tobias Flamig-Vetter Method of operating a diesel internal combustion engine
EP1348854A1 (en) * 2002-03-27 2003-10-01 Mazda Motor Corporation Combustion control apparatus for a diesel engine, a diesel engine, combustion control method thereof, computer-readable storage medium, and computer program

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
Development of the High Power NADI Concept Using Dual Mode Diesel Combustion to Achieve Zero NOx and Particulate Emissions. Bruno Walter, Bertrand Gatellier,779-787,SAE TECHNICAL PAPER SERIES. 2002
Development of the High Power NADI Concept Using Dual Mode Diesel Combustion to Achieve Zero NOx and Particulate Emissions. Bruno Walter, Bertrand Gatellier,779-787,SAE TECHNICAL PAPER SERIES. 2002 *

Also Published As

Publication number Publication date
DE10393905B4 (en) 2016-09-15
DE10393905D2 (en) 2006-01-19
CN1729354A (en) 2006-02-01
WO2004057167A1 (en) 2004-07-08
AU2003287752A1 (en) 2004-07-14
AT7204U1 (en) 2004-11-25

Similar Documents

Publication Publication Date Title
CN1079492C (en) internal combustion engine
CN203584599U (en) Piston for internal combustion engine
JP3980489B2 (en) In-cylinder injection internal combustion engine control device
US8156927B2 (en) Combustion chamber structure for direct injection diesel engine
EP1134400B1 (en) Auto-ignition combustion management in internal combustion engine
US20110271932A1 (en) Combustion chamber constructions for opposed-piston engines
JP4898891B2 (en) Direct fuel injection diesel engine
JP4308487B2 (en) Fuel injection method in fuel injection device
EP1291516B1 (en) Direct injection diesel engine
CN100564828C (en) internal combustion engine
DE102011109336B4 (en) Diesel engine and method of controlling the same
EP0686759A1 (en) Compression ignition type gasoline engine injecting fuel inside intake port during exhaust stroke
CN100350145C (en) Compression ignition internal combustion engine
DE10348366B4 (en) Method for operating a direct-injection diesel internal combustion engine
US6688279B2 (en) Compression-ignition internal combustion engine
US6158413A (en) Direct injection diesel engine
JP4335533B2 (en) Operation method of supercritical water injection type internal combustion engine
JP4075588B2 (en) diesel engine
US6712036B1 (en) Method of controlling the fuel injection in an internal combustion engine
US7314036B2 (en) Methods for operating a spark-ignition internal combustion engine
US20100312454A1 (en) Fuel injection control apparatus of internal combustion engine
CN101336339B (en) Gas-fueled internal combustion engine and control method for gas-fueled internal combustion engine
JP2005530084A (en) Low emission internal combustion engine
JP2008215356A (en) Injection nozzle of self-igniting internal combustion engine
US6935301B2 (en) Combustion chamber

Legal Events

Date Code Title Description
PB01 Publication
C06 Publication
SE01 Entry into force of request for substantive examination
C10 Entry into substantive examination
GR01 Patent grant
C14 Grant of patent or utility model