CN101375034A - 用于火花点火直喷式发动机的方法和设备 - Google Patents

用于火花点火直喷式发动机的方法和设备 Download PDF

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CN101375034A
CN101375034A CNA2007800036340A CN200780003634A CN101375034A CN 101375034 A CN101375034 A CN 101375034A CN A2007800036340 A CNA2007800036340 A CN A2007800036340A CN 200780003634 A CN200780003634 A CN 200780003634A CN 101375034 A CN101375034 A CN 101375034A
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A·M·利佩特
M·C·德拉克
曾扬兵
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
    • F02B23/08—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition
    • F02B23/10—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition with separate admission of air and fuel into cylinder
    • F02B23/101—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition with separate admission of air and fuel into cylinder the injector being placed on or close to the cylinder centre axis, e.g. with mixture formation using spray guided concepts
    • 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
    • F02B17/00—Engines characterised by means for effecting stratification of charge in cylinders
    • F02B17/005—Engines characterised by means for effecting stratification of charge in cylinders having direct injection in the combustion chamber
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
    • F02M61/1813—Discharge orifices having different orientations with respect to valve member direction of movement, e.g. orientations being such that fuel jets emerging from discharge orifices collide with each other
    • 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
    • F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
    • F02B23/08—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition
    • F02B23/10—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition with separate admission of air and fuel into cylinder
    • F02B2023/103—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition with separate admission of air and fuel into cylinder the injector having a multi-hole nozzle for generating multiple sprays
    • 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
    • F02B75/12—Other methods of operation
    • F02B2075/125—Direct injection in the combustion chamber for spark ignition engines, i.e. not in pre-combustion chamber
    • 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
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/06—Fuel-injectors combined or associated with other devices the devices being sparking plugs
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
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    • Y02T10/12—Improving ICE efficiencies

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  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
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Abstract

一种火花点火直喷式内燃机，包括有效产生燃料喷射模式的燃料喷射器，所述燃料喷射模式在低载比较紧凑，在高载比较大。

Description

用于火花点火直喷式发动机的方法和设备
技术领域
[0001]本发明涉及火花点火直喷式(SIDI)内燃机。更特别地，本发明涉及在宽发动机负载变化范围内SIDI发动机的有效燃料喷射。
背景技术
[0002]燃料喷射器是将燃料喷入发动机(或喷入燃烧室上游的进气歧管、或直接喷入燃烧室)的公知装置。非常需要将喷射的燃料良好地雾化以快速汽化，与空气适当地混合，以获得最佳的燃烧和动力产生，同时使燃烧的不良副产物的形成最少，并防止不受控的燃烧事件。
[0003]工程师研发了具有直接燃料喷射的火花点火式(SIDI)发动机，其依赖于操作员对动力的需求和发动机运行状况，使用分层燃烧充气策略和均质燃烧充气策略。SIDI发动机发展成提高了发动机燃料效率，从而改善了车辆燃料经济性。通常，在高负载情形下，SIDI发动机优选运行于均质充气。并且，在低负载情形下，SIDI发动机优选运行于分层充气。均质充气很容易通过宽的燃烧喷射锥角获得，而分层充气很容易通过窄的燃料喷射锥角获得。工程师权衡了燃料喷射器设计，以解决当选择喷射锥角时低负载和高负载燃料需求的分歧。
发明内容
[0004]一种SIDI发动机，包括具有气缸和往复式活塞的可变容积燃烧室、具有火花隙的火花塞、以及缸内直喷燃料喷射器。用于操作该发动机的方法包括:提供具有以通孔模式布置的多个通孔的燃料喷射器喷嘴，以在发动机低载极限产生具有比较紧凑的燃烧锥角、在发动机高载极限产生比较宽的燃料锥角的燃料喷射模式；以及配合定位所述燃料喷射器和火花隙，使得在所述发动机低载极限时，所述喷射器的一部分燃料喷射模式与所述火花隙相交。每个所述通孔都沿着与喷射器中心线既不平行也不共面的各自通孔轴线有效引导燃料流，从而提供燃料涡流。所述通孔模式在所述发动机低载极限与所述高载极限之间产生通常增大的燃料锥角的燃料喷射模式。所述通孔模式产生通常与大部分进气涡流相反的燃料喷射涡流。
[0005]一种SIDI发动机设备，包括可变容积燃烧室，包括气缸、具有进气门和排气门的气缸盖、以及往复式活塞。所述设备包括:火花塞，具有用于在所述燃烧室内产生火花的火花隙；和燃料喷射器，用于将燃料喷射在所述燃烧室内。所述燃料喷射器包括燃料喷射器喷嘴，所述燃料喷射器喷嘴具有以通孔模式布置的多个通孔，以产生燃料锥角通常随着燃料喷射量增加而增大的燃料喷射模式。并且，所述燃料喷射器和所述火花塞共同定位成使得所述燃料喷射模式与所述火花隙相交。每个所述通孔都沿着与喷射器中心线既不平行也不共面的各自通孔轴线引导燃料流。每个所述通孔都将燃料流引导成通常与大部分进气涡流相反的涡流。所述往复式活塞包括凹室。
[0006]通过阅读和理解下面实施例的详细描述，本领域的技术人员可清楚本发明的这些及其它方面。
附图说明
[0007]本发明可以在某些部分和部分的布置上采用物理形式，在形成其一部分的附图中详细描述和示出了其优选实施例，其中:
[0008]图1A和1B为示出根据本发明的喷射器喷嘴通孔的三维示意图；
[0009]图2A和2B为通过典型SIDI燃烧室的局部截面图，示出和比较了来自现有燃料喷射器和根据本发明的涡流燃料喷射器的流；
[0010]图3为典型SIDI发动机内燃烧速率相对于曲轴角的曲线图，示出和比较了现有燃料喷射器和根据本发明的涡流燃料喷射器；
[0011]图4A和4B为分别示出和比较了从现有燃料喷射器和根据本发明的涡流燃料喷射器的流喷射模式，包括有效锥角和贯入度；
[0012]图5为示出和比较现有燃料喷射器和根据本发明的涡流燃料喷射器的有效喷射锥角相对于轴向喷嘴贯入度的曲线图；
[0013]图6为示出和比较根据本发明的涡流燃料喷射器布置中逆涡流和顺涡流进气的典型SIDI发动机平均当量比相对于曲轴角的曲线图；
[0014]图7为示出和比较根据本发明的涡流燃料喷射器布置中逆涡流和顺涡流进气的典型SIDI发动机火花塞处平均速度相对于曲轴角的曲线图；以及
[0015]图8为示出和比较根据本发明的涡流燃料喷射器布置中逆涡流和顺涡流进气的典型SIDI发动机燃烧速率相对于曲轴角的曲线图。
具体实施方式
[0016]参考附图，其中附图仅仅是示出本发明的目的，而不是限制本发明，图1A和1B示意性地示出了根据本发明实施例的燃料喷射器喷嘴的示例通孔模式10。根据本发明的燃料喷射器喷嘴可包括大致平面的导向板、球形或圆锥形喷射器喷嘴、或者与下面更加全面详细描述的示例通孔模式相当的各种喷嘴设计。根据本发明的通孔20布置成使得燃料流以涡流的形式引入燃烧室，从下面的描述中可更加清楚。包括通孔模式10的燃料喷射器喷嘴往往应用在火花点火直喷式(SIDI)四冲程内燃机的电磁控制燃料喷射器上。例如，图2A和2B的截面图中部分地示出了典型SIDI发动机的燃烧室，其中活塞12可在一端封闭的气缸14内移动，并与气缸14限定了可变容积的燃烧室16。活塞12包括凹室18，燃料主要喷射进该凹室18。燃烧室构造有火花塞36和燃料喷射器42，火花塞36与燃料喷射器42协同布置成使得喷射器42的燃料喷射模式与火花塞隙相交。在图2A和2B所示的典型的SIDI发动机及燃烧室中，燃料喷射器42将其喷嘴相对于气缸轴线大致位于气缸盖的中心，以产生以喷射器中心线38为中心的喷射模式。火花塞36相对于气缸轴线在气缸盖内偏置，其火花隙沿着火花塞中心线34位于燃烧室内。根据如封装、喷射器喷射模式、火花隙突起、火花隙与喷射器喷嘴之间的距离等这类考虑，喷射器中心线38与火花塞中心线34相对于彼此倾斜。
[0017]图1A和1B示出了燃料喷射器42B的喷射器喷嘴中通孔20的三维透视图，详细示出了具体的通孔模式10，当通过发动机控制器的信号致动喷射器42B时，增压燃料通过该通孔模式10进入燃烧室。通孔20的入口22优选定位在与喷射器中心线38同心且在其垂直平面上的第一圆周26上。通孔20的出口24定位在与第一圆周26和喷射器中心线38同心并且也在喷射器中心线38的垂直面上的第二圆周28上。优选地，第二圆周28比第一圆周26大，但是可选地，根据所需的喷射模式(包括当量比分配)，它们可一样大，或者第二圆周28可比第一圆周26小。每个通孔20大致为圆柱形，具有从其通过的各自通孔轴线40。通孔20的通孔轴线40既不平行于喷射器中心线38，也不与其共面，所以建立了具有切向喷射分量的单个燃料流。通过具有所述通孔模式10的喷射器喷嘴的增压燃料导致相对于喷射器中心线38的涡流。比较起见，传统的喷射器具有与喷射器中心线共面且只包括径向喷射分量的通孔轴线。本文上面包括所述通孔模式10的燃料喷射器在本文中下面还可称为涡流喷射器。
[0018]图3中示出了使用上述涡流喷射器将燃料直接喷射入典型SIDI发动机的计算流体力学预计燃料燃烧速率曲线。本领域的技术人员从图3可看出，与传统燃料喷射器相比，涡流喷射器产生更快的初始和峰值燃烧速率。并且，参考图2A和2B，尤其分别参考传统喷射器和涡流喷射器各自在2000 RPM约280 NMEP的中载分层运行点的当量比线44A和44B，本领域的技术人员会看出，沿着涡流喷射器的喷射器轴线集中了更多的燃料。因此，更多的燃料接近于火花塞，加速了燃烧过程的点火和中间阶段，如图3中所示。
[0019]图4A和4B示出了比较在典型中载分层发动机运行条件下从标准喷射器(图4A)和涡流喷射器(图4B)喷射输出的CFD预计喷射模式。更特别地，各图示出了在2000 RPM约280 NMEP的中载分层运行点，相对于喷射起始(SOI)以一度曲轴角(CA)增量的燃料喷射模式进展。与燃料喷射模式相邻的箭头61对应于贯入燃烧室的燃料，本文可称为轴向喷嘴贯入度。图4A和4B示出了当喷流内的中心点62和喷流的外封面64对应于大致0.5的当量比线的喷射微粒。本领域的技术人员可清楚，对于标准喷射器，喷射边缘接近直线，即，对于所有的贯入度喷锥角都基本保持恒定。相反，对于从涡流喷射器输出的喷射，其有效喷射锥度逐渐增大，使得喷射锥缘以铃状曲线向外扩大。当假定其喷射跟随其从喷射器的初始脱离速度，有效喷射锥与轴向喷嘴贯入度之间的关系可通过数学方法获得。图5中示出了标准喷射器与涡流喷射器的有效喷射锥角之间的区别。
[0020]可获得的有效喷射锥角的区别与分层SIDI发动机中的混合物准备有很大的关系，所述混合物准备在没有传统空气节流的情况下依赖于燃料计量来控制负载。基于发动机负载的需求，分层SIDI发动机可运行于两个不同的模式，即均质充气运行模式和分层充气运行模式，每个模式在空气/燃料混合物准备方面都具有不同的需求。对于重载均质运行，主要目标是使发动机功率最大，因此其喷射需要尽可能地扩散，以接触尽可能多的空气，以便与燃料混合。因此，通常是赞成较大喷射锥角的。相反，在轻载分层运行情况下，喷射较少量的燃料，混合物总体上比较稀薄。但是，对燃烧稳定性和低排放的需求要求燃烧的燃料接近化学当量比。因此，需要密集的混合物以达到总体的分层。极端地，在怠速情况下只喷射非常少的燃料，并且该燃料需要非常密集。考虑在不同局部负载所需分层的宽范围，通常选择中间的喷射锥角，这对中载是最优的，但是对重载和轻载并非最优。
[0021]根据本发明，可容易地管理均质运行与分层运行之间的不同运行需求。图5A和5B分别示出了随标准喷射器和涡流喷射器的轴向喷嘴贯入度变化的有效喷射锥角。对于涡流喷射器，其有效喷射锥角随着喷嘴贯入度逐步地增大。从轻载分层运行到重载均质运行，随着增大的负载喷射更多的燃料量。对于与喷射量相关的最终喷射贯入度，在更高的负载实施更高的贯入度，从而实施更大的有效喷射锥角。就其直接效果而言，有效喷射锥角随发动机负载(喷射燃料量)的变化满足了上述发动机运行需求。通过涡流喷射器喷射锥角的进一步优化，与标准喷射器相比，在分层运行和均质运行方面都获得整体上更好的性能。在通过例如净平均有效压力(NMEP)测量的发动机轻载极限有必要使燃料喷射锥角与火花塞隙相交，其中所述净平均有效压力表现出通常接受的不大于指示平均有效压力(IMEP)约5％系数的变化(COV)。
[0022]根据本发明的另一方面，涡流燃料喷射以有效改善燃烧稳定性的方式与大部分进气涡流共同混合在一起。发明人通过CFD建模确定，当引入的燃料流具有与大部分进气涡流方向相反的切向分量时，从涡流喷射器提供喷射的燃料会改善点火稳定性，并提高其峰值燃烧速率。这种协同布置这里称作逆涡流，是优选的，而当引入的燃料流带有与大部分进气涡流方向相同的切向分量时，其在这里称作顺涡流。图6至8中示出了典型的CFD结果。涡流喷射器与大部分进气之间的逆涡流布置降低了喷射引起的速度，从而增加了可燃混合物停留在火花塞隙周围的时间。图6和7中所示CFD结果分别将涡流喷射器在火花塞附近的当量比及速度与进气的逆向总体流动涡旋方向相比。本领域的技术人员可清楚，其速度平均减小约5米/秒，当量比增加约0.2。如图8中所示，逆涡流还导致高10％的峰值燃烧速率，本领域的技术人员从图8可看出，获得了更高的峰值燃烧速率。本领域的技术人员还可看出，包括通孔模式、喷射锥角、涡流强度、火花塞和喷射器位置等的所述布置的操作将导致改变性能结构。
[0023]已经参考优选实施例及其修改描述了本发明。通过阅读和理解说明书，可发现其它变形和修改。本文试图将所有这些变形和修改都包括在本发明的范围内。

Claims (11)

1.一种用于操作火花点火直喷式内燃机的方法，所述内燃机包括具有气缸和往复式活塞的可变容积燃烧室、具有火花隙的火花塞、以及用于在所述燃烧室内实施燃料喷射模式的缸内直喷燃料喷射器，所述方法包括：
提供具有以通孔模式布置的多个通孔的燃料喷射器喷嘴，以产生在发动机低载极限具有比较紧凑的燃料锥角且在发动机高载极限具有比较宽的燃料锥角的燃料喷射模式；以及
定位所述燃料喷射器和火花隙，使得在所述发动机低载极限时，所述喷射器的一部分燃料喷射模式与所述火花隙相交。
2.如权利要求1所述的用于操作火花点火直喷式内燃机的方法，其中每个所述通孔都沿着与喷射器中心线既不平行也不共面的各自通孔轴线有效引导燃料流。
3.如权利要求1所述的用于操作火花点火直喷式内燃机的方法，其中所述通孔模式在所述发动机低载极限与所述高载极限之间产生通常增大的燃料锥角的燃料喷射模式。
4.如权利要求1所述的用于操作火花点火直喷式内燃机的方法，其中所述通孔模式产生通常与大部分进气涡流相反的燃料喷射涡流。
5.一种用于操作火花点火直喷式内燃机的方法，所述内燃机包括具有气缸和往复式活塞的可变容积燃烧室、具有火花隙的火花塞、以及用于在所述燃烧室内实施燃料喷射模式的缸内直喷燃料喷射器，所述方法包括：
从所述燃料喷射器提供燃料喷射模式，该燃料喷射模式在发动机低载极限具有比较紧凑的燃料锥角、在发动机高载极限具有比较宽的燃料锥角、并且在所述发动机低载极限与所述高载极高之间具有通常增大的燃料锥角；以及
定位所述燃料喷射器和火花隙，使得在所述发动机低载极限时，所述喷射器的一部分燃料喷射模式与所述火花隙相交。
6.如权利要求5所述的用于操作火花点火直喷式内燃机的方法，其中提供燃料喷射模式包括提供具有多个通孔的燃料喷嘴，其中每个通孔都沿着与喷射器中心线既不平行也不共面的各自通孔轴线引导燃料流。
7.如权利要求6所述的用于操作火花点火直喷式内燃机的方法，其中每个通孔都将燃料流引导成通常与大部分进气涡流相反的涡流。
8.一种火花点火直喷式内燃机设备，包括：
可变容积燃烧室，包括气缸、具有进气门和排气门的气缸盖、以及往复式活塞；
火花塞，具有用于在所述燃烧室内产生火花的火花隙；
燃料喷射器，用于将燃料喷射在所述燃烧室内；
所述燃料喷射器包括燃料喷射器喷嘴，所述燃料喷射器喷嘴具有以通孔模式布置的多个通孔，以产生燃料锥角通常随着燃料喷射量增加而增大的燃料喷射模式；并且
所述燃料喷射器和所述火花塞共同定位成使得所述燃料喷射模式与所述火花隙相交。
9.如权利要求8所述的火花点火直喷式内燃机设备，其中每个所述通孔都沿着与喷射器中心线既不平行也不共面的各自通孔轴线引导燃料流。
10.如权利要求8所述的火花点火直喷式内燃机设备，其中每个所述通孔都将燃料流引导成通常与大部分进气涡流相反的涡流。
11.如权利要求8所述的火花点火直喷式内燃机设备，其中所述往复式活塞包括凹室。
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US7484494B2 (en) 2009-02-03
US20070175440A1 (en) 2007-08-02
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WO2007090019A3 (en) 2008-01-10
CN101375034B (zh) 2012-01-18
DE112007000209B4 (de) 2015-02-19

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