在全球石化燃料需求量持續增加的情形下，車用替代燃料的發展成為全球的焦點。
生質柴油因其可再生且物性、化性與石化提煉之柴油相近，已成為極具吸引力之替代燃料。
然而，生質柴油在柴油引擎的使用會造成性能下降及管路阻塞。

本研究利用Ansys Fluent模擬軟體建立一真實柴油引擎力學模型，根據油品燃燒行為進行分析討論，
探討無法從實驗數據所獲得的資訊，實驗平台為中華重型柴油引擎 Mitsubishi 4M42-4AT2 搭配共軌燃油噴射系統。
本研究將對於穩態數值模擬進行研究分析，在模擬當中先使用純柴油進行模擬，經過多個循環模擬後使其達到穩態流場，在與實驗缸壓進行驗證後，更換噴注燃油為生質柴油，並且在相同之操作條件下進行模擬，藉由模擬觀察缸內燃油的燃燒情況。
生質柴油內因含有氧原子而使的燃油在氣相時的燃燒效率較好，而在十六烷值的差異上，生質柴油會產生較大的缸壓峰值及較早的燃燒時間點，也藉由油品的燃燒熱釋放率計算出不同比例生質柴油所產生的能量大小。

In the global petrochemical fuel demand continues to increase, the development of vehicle alternative fuels become the focus of the world.
Biodiesel has become a very attractive alternative fuel because of its renewable and physical properties, chemical properties and petrochemical refining of diesel oil similar.
However, the use of biodiesel in diesel engines can cause performance degradation and pipeline clogging.

In this study, Ansys Fluent simulation software was used to establish a mechanical model of a real diesel engine. According to the combustion behavior of oil,
To explore the information can not be obtained from the experimental data, and the experimental platform for the Chinese heavy diesel engine Mitsubishi 4M42-4AT2 with common rail fuel injection system,
In this study, the steady-state numerical simulation is carried out. In the simulation, the pure diesel is used to simulate the steady-state flow field after several cycles. After the verification with the experimental cylinder pressure, the replacement fuel is Bio-diesel, and simulated under the same operating conditions, by simulating the combustion of fuel in the cylinder.
The combustion efficiency of the fuel in the gaseous diesel is better than that in the gas phase. In the case of the cetane number, the biomass diesel produces a large cylinder pressure peak and an earlier burning time point, But also by the combustion heat release rate of oil to calculate the proportion of biomass produced by the proportion of diesel fuel.

[1] W. Yuan, A. C. Hansen, and Q. Zhang, “Predicting the physical properties of biodiesel for combustion modeling,” American Society of Mechanical Engineers, vol. 46(6), pp. 1487–1493, 2003.
[2] 范仕坤、顧詠元(2012年11月9日)。不同生質柴油對噴霧特性之影響模擬分析。中華民國第十七屆車輛工程學術研討會。
[3] 林克衛(2006年9月)。柴油引擎氮氧化物防治技術SCR(urea)系統之介紹，財團法人車輛研究測試中心。
[4] M. T. Shervani-Tabar, M. Sheykhvazayefi, and M. Ghorbani, “Numerical study on the effect of the injection pressure on spray penetration length,” Applied Mathematical Modelling, vol. 37(14-15), pp. 7778–7788, 2013.
[5] P. J. Tennison, T. L. Georjon, P. V. Farrell, and R. D. Reitz, “An experimental and numerical study of sprays from a common rail injection system for use in an hsdi diesel engine,” SAE Technical Paper, 980810.
[6] N. R. Banapurmath, P. G. Tewari, and V. N. Gaitond, “Experimental investigations on performance and emission characteristics of honge oil biodiesel (home) operated compression ignition engine,” Renewable Energy, vol. 48(4), pp. 193–201, 2012.
[7] L. Labecki and L. C. Ganippa, “Effects of injection parameters and egr on combustion and emission characteristics of rapeseed oil and its blends in diesel engines,” Fuel, vol. 98, pp. 15–28, 2012.
[8] D. Qi, M. Leick, Y. Liu, and C.-F. F. Lee, “Effect of egr and injection timing on combustion and emission characteristics of split injection strategy di- diesel engine fueled with biodiesel,” Fuel, vol. 90(5), pp. 1884–1891, 2011.
[9]Z.Jinghua,H.Wei,L.Xuejun,X.Fangxi,and J.Li,“Study about effects of egr and injection parameters on the combustion and emissions of high- pressure common-rail diesel engine,” International Conference on Industrial Mecha- tronics and Automation, vol.1, pp.290–294, 2010.
[10]M.R.Herfatmanesh,P.Lu,M.A.Attar, and H. Zhao, “Experimental inves- tigation into the effects of two-stage injection on fuel injection quantity, combustion and emissions in a high-speed optical common rail diesel engine,” Fuel, vol. 109, pp. 137–147, 2013.
[11]王冠中，「渦輪增壓共軌柴油引擎之計算流體力學模型」，國立台灣科技大學機械工程系碩士論文(2013)。
[12]曾柏憲，「生質柴油引擎燃燒行為之數值模擬分析」，國立台灣科技大學機械工程系碩士論文(2014)。
[13]T. M. Belal, E. S. M. Marzouk, and M. M. Osman, “Investigating diesel engine performance and emissions using cfd,” Energy and Power Engineering, vol. 5(2), pp. 171–180, 2013.
[14] B. Dhingra, S. Sharma, K. Vora, and B. Ashok, “Cfd modeling of advanced swirl technique at inlet-runner for diesel engine, ” SAE Technical Paper, 2015-26-0095.
[15]R.K.D.A.K.Lichtarowicz and E.Markland,“Discharge coefficients for incompressible non-cavitating flow through long orifices,” Journal of Mechan- ical Engineering Science, 1965.
[16]W. H. Nurick, Orifice Cavitation and Its Effects on Spray Mixing.
[17]T.R.White, B.E.Milton,and M.Behnia,“Direct injection of natural gas/liquid diesel fuel sprays, ” 15th Australasian Fluid Mechanics Conference, 2014.
[18] M.T.Shervani-Tabar,M.Sheykhvazayefi,and M.Ghorbani, “Numerical study on the effect of the injection pressure on spray penetration length,” Applied Mathematical Modelling,vol. 37(14-15), pp.7778–7788, 2013.
[19]H.O.Hardenberg and F. E. Hase, “An empirical formula for computing the pressure rise delay of a fuel from its cetane number and from the relevant parameters of direct-injection diesel engines, ” SAE Technical Paper, 790493.
[20]D.N.Assanis,Z.S.Filipi,S.B.Fiveland, and M.Syrimis,“A predictive ig- nition delay correlation under steady-state and transient operation of a direct injection diesel engine, ”Journal of Engineering for Gas Turbines and Power, ”vol.125, pp.452–457,2003.
[21]Y.V.Aghav, V.M.Thatte,M.N.Kumar,P.A.Lakshminarayanan, and M. K. G. Babu, “ Predicting ignition delay and hc emission for diesel engine encompassing egr and oxygenated fuels, ” SAE Technical Paper, 2008-28-0050.
[22]J. B. Heywood, Internal Combustion Engine Fundamentals, 1988.
[23]鄒文偕，「柴油引擎使用不同比例生質柴油之燃燒行為及氮氧化物排放汙染數值模擬分析」，國立台灣科技大學機械工程系碩士論文(2016)。