氢预燃室射流引燃氨扩散燃烧特性与排放

doi:10.3969/j.issn.1674-8484.2026.05.006

摘要/Abstract

摘要：

针对氢预燃室射流引燃氨预混燃烧放热速率低、未燃NH₃和N₂O排放高的问题，提出氨扩散燃烧策略。采用数值模拟对比2种燃烧模式，研究扩散燃烧中喷孔构型和点火正时的影响。结果表明：扩散燃烧的燃烧效率更高，NH₃、N₂O排放更低； 6孔均布方案的指示热效率高于4孔、2孔单侧方案。喷氨时刻在上止点后 (ATDC) 曲柄转角 (CA) -18°时， ATDC CA为-20°~-14°点火的燃烧效率较高；点火过早导致预燃室失火，过晚则因主燃室工质密度增大、射流火焰降温而降低燃烧效率。所考察方案中，6孔均布与ATDC CA为-20°点火组合兼顾较高指示热效率和较低未燃NH₃排放，N₂O排放满足Euro Ⅶ限值。

关键词: 氨燃料, 氢预燃室, 射流引燃, 扩散燃烧, 燃烧特性

Abstract:

An ammonia diffusion combustion strategy was proposed to address the low heat release rate and high unburned NH₃ and N₂O emissions of ammonia premixed combustion using hydrogen pre-chamber jet ignition. Two combustion modes was compared using numerical simulation to investigate the effects of pre-chamber orifice configuration and spark timing on diffusion combustion. The results show that the diffusion combustion achieves higher combustion efficiency and lower NH₃ and N₂O emissions. The 6-orifice uniform configuration achieves higher indicated thermal efficiency than the 4-orifice and 2-orifice one-sided configurations. With ammonia injection at after top dead center (ATDC) crank angle (CA) −18°, combustion efficiency is high for spark timing between ATDC CA −20° and −14°. Excessively early spark timing causes pre-chamber misfire; excessively late spark timing reduces combustion efficiency because increased in-cylinder charge density in the main combustion chamber lowers the jet flame temperature. Among the configurations investigated, the 6-orifice uniform configuration with spark timing at ATDC CA −20° combines relatively high indicated thermal efficiency with relatively low unburned NH₃ emissions, while N₂O emissions meet the Euro VII emission limits.

Key words: ammonia fuel, hydrogen pre-chamber, jet ignition, diffusion combustion, combustion characteristics

中图分类号:

TK46+
4

宋扬, 刘浩业, 王天友, 孙凯, 林铁坚, 王辉, 贾志琴, 余诗武, 卢天龙. 氢预燃室射流引燃氨扩散燃烧特性与排放[J]. 汽车安全与节能学报, 2026, 17(5): 567-577.

SONG Yang, LIU Haoye, WANG Tianyou, SUN Kai, LIN Tiejian, WANG Hui, JIA Zhiqin, YU Shiwu, LU Tianlong. Combustion and emission characteristics of ammonia diffusion combustion ignited by hydrogen pre-chamber jets[J]. Journal of Automotive Safety and Energy, 2026, 17(5): 567-577.

图/表 18

缸径/ mm	129
活塞行程/ mm	155
转速/ (r·min^-1)	1 200
压缩比	16.3
进气压力/ MPa	0.185
进气温度/ K	305
气门数	4
预燃室容积/ mL	4.26

表1 发动机技术参数

图1 发动机几何模型

模型	选用模型
湍流模型	RNG k-ε
喷雾破碎模型	KH-RT
液滴蒸发模型	Frossling
液滴碰撞模型	NTC collision
壁面传热模型	O’Rourke and Amsden model
燃烧模型	SAGE

表2 三维计算模型设置

图2 缸内压力与放热率曲线的模拟与试验结果对比

变量	AIT	ST	喷孔构型
燃烧模式	ATDC，CA为 -18° (扩散燃烧)/进气道喷射 (预混燃烧)	ATDC， CA为-18°	6孔均布
喷孔构型	ATDC，CA为-18° (扩散燃烧)	ATDC， CA为-18°	6孔均布 (方案A) 4孔单侧 (方案B) 2孔单侧 (方案C)
点火正时	ATDC，CA为-18° (扩散燃烧)	ATDC，CA为-24~ -10°，每隔2°取一点，共8个角度	6孔均布 (方案A) 4孔单侧 (方案B)

表3 参数化方案

图3 预混和扩散燃烧模式下(IMEP = 1.2 MPa)的缸内压力和放热率曲线

图4 预混和扩散燃烧模式下的引燃着火和火焰发展过程

图5 预混燃烧和扩散燃烧下(ST，CA = -18°)排放特性对比

图6 预混和扩散燃烧模式(ST，CA = -18°)的能量分布

图7 不同喷孔构型下的缸内压力和放热率曲线(ST，AIT ，CA = -18°)

图8 不同喷孔构型下引燃着火和火焰发展过程

图9 不同喷孔构型下的能量分布(ST，AIT ，CA = -18°)

图10 不同点火正时下的压力曲线和放热率曲线

图11 不同点火正时方案A与方案B的燃烧相位(左柱：方案A；右柱：方案B)

图12 不同点火正时下的引燃着火与火焰发展过程

图13 方案A在不同点火正时下预燃室内关键参数对比

图14 不同点火正时的NOx、N2O和NH3排放量的对比(AIT, CA = -18°)

图15 不同点火正时的能量分布

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