ᄺ䖯ሩ, 2014 ᑈ, 44 ो : 201402
Recent progress and challenges in fundamental combustion research
† Yiguang Ju
Department of Mechanical and Aerospace Engineering, Princeton University, New Jersey, USA
Abstract More than 80% of world energy is converted by combustion. Develop- ment of efficient next generation advanced engines by using alternative fuels and operating at extreme conditions is one of the most important solutions to increase energy sustainability. To realize the advanced engine design, the challenges in combustion research are therefore to advance fundamental understanding of com- bustion chemistry and dynamics from molecule scales to engine scales and to de- velop quantitatively predictive tools and innovative combustion technologies. This review will present the recent progresses and technical challenges in fundamental combustion research in seven areas including advanced engine concepts using low temperature fuel chemistry, new combustion phenomena in extreme conditions, alternative and surrogate fuels, multi-scale modeling, high pressure combustion kinetics, experimental methods and advanced combustion diagnostics Firstly, new engine concepts such as the Homogeneous Charge Compression Ignition (HCCI),
Received: 2014-01-29;accepted: 2014-03-27;online: 2014-04-01 † E-mail: [email protected] $i teas: Yiguang Ju. Recent progress and challenges in fundamental combustion research. "Evances in Mechanics,2014,44: c 2014Advances in Mechanics. 2 ᄺ䖯ሩ 44 ो : 201402
Reactivity Controlled Compression Ignition (RCCI), and pressure gain combus- tion will be introduced. The impact of low temperature combustion chemistry of fuels on combustion in advanced engines will be demonstrated. This is followed by the discussions of the needs of fundamental combustion research for new en- gine technologies. Secondly, combustion phenomena and flame regimes involving new combustion concepts such as fuel and thermal stratifications, plasma assisted combustion, and cool flames at extreme conditions will be analyzed. Thirdly, al- ternative fuels and methodologies to formulate surrogate fuel mixtures to model the target combustion properties of real fuels will be presented. A new concept of radical index and transport weighted enthalpy will be introduced to rank the fuel reactivity and to assess the impact of molecular structure on combustion prop- erties The success and limitations of the current surrogate fuel models will be discussed by using jet fuels and biodiesels as examples. Fourthly, the difficulty of modeling large kinetic mechanism of real fuel will be discussed The multi-time scale (MTS) method and the correlated dynamic adaptive chemistry (CO-DAC) method for kinetic model reduction and computationally efficient modeling will be compared and analyzed. Fifthly, the progress and challenges of high pressure combustion kinetics for hydrogen and larger hydrocarbons will be discussed. The important pressuredependent reaction pathways and key intermediate species at high pressure will be analyzed. Fundamental experimental methods for combus- tion and their uncertainties in acquiring combustion properties for the validation of kinetic mechanism will be discussed. Finally, recent progress in diagnostics of
HO2,H2O2,RO2, ketohydroperoxide, and other key intermediate species for high pressure kinetic mechanism development will be summarized. Conclusions and opportunities of future combustion research will be made.
Keywords alternative fuels, flame chemistry multiscale modeling, experimental methods and uncertainty, multi-species diagnostics
Classification code: O341 Document code: A DOI: 10.6052/1000-0992-14-011 Ju Yiguang : Recent progress and challenges in fundamental combustion research 3
1 Introduction 1.1 Advanced engine design and multi-scale turbulent combustion modeling Combustion converts more than 80% of world energy and has played a dominant role in ground and air transportation. With the current difficulties in developing renewable energy, for a foreseeable future, combustion will remain to be the major energy conversion process in power generation and transportation. However, the energy conversion efficiency of existing combustion engines is low and combustion of fossil fuels is the major source contributing to climate change and air pollution (Chu et al. 2012). As such, there is an urgent need to develop advanced engine technology and new combustion concepts to drastically increase the engine efficiency and reduce emissions (DOE report, 2006). For ground transportation, recently, various new combustion engine technologies such the Homogeneous Charge Com- pression Ignition (HCCI) engines (Dec 2009, Lu et al. 2011, Reitz 2013) and the Reactivity Controlled Compression Ignition (RCCI) engines (Reitz 2013) have been developed. These engines take the advantage of high compression ratio of diesel engines and low emissions of gasoline engines by using highly diluted, premixed and/or highly stratified fuel/air mixtures with excessive exhaust gas recirculation (EGR). As such, to control engine knock, heat release rate, and ignition timing at different engine loads, understanding the combustion process at high pressure and low temperature conditions involving the negative temperature coefficient (NTC) and cool flame chemistry (Curran et al. 1998) becomes extremely impor- tant. Moreover, the low temperature and high pressure combustion processes coupled by strong fuel and temperature non-uniformities in engines are controlled by both large-scale turbulent mixing and sub-grid-scale turbulence-chemistry interactions. Therefore, detailed understanding of combustion processes in HCCI and RCCI engines requires not only an accurate turbulent combustion model which can appropriately predict sub-grid turbulent- chemistry interaction but also a validated high pressure and low temperature chemistry for real transportation fuels. Unfortunately, strictly speaking neither a validated high pressure and low temperature kinetic mechanism for real fuels nor an accurate and computation- ally efficient sub-grid turbulent-chemistry model is available for advanced engine modeling (Chen 2011, Pope 2012). Moreover, previous turbulent combustion experiments and model- ing are mainly focused on high temperature thin flame regimes and few studies are carried to understand how low temperature combustion chemistry and autoignition affect turbulent 4 ᄺ䖯ሩ 44 ो : 201402
flame regimes and propagation speeds (Won et al. 2014) Therefore, the first challenge in combustion is how we can develop validated high pressure and low temperature combustion models for advanced engine modeling. In air transportation, to increase the fuel efficiency and meet the stringent CAEP-6 and NASA (N+3) emission standards of the Committee on Aviation Environmental Protection (CAEP) and NASA, new lean burn aircraft combustor concepts such as the twin annular premixing swirled (TAPS) burner (Mongia 2010), lean-premixed pre-vaporized (LPP), lean direct injection (LDI) burners (Tacina et al. 2003), trapped vortex combustion (TVC) burn- ers (Hsu et al. 1998), and pressure gain combustors (Schwer and Kailasanath 2011) have been developed. To achieve high speed propulsion, supersonic ramjet engines such as X-43 and X-51 have been developed and tested (Moorthy et al. 2012, Yu et al. 2013). Moreover, new advanced gas turbine engines have higher compression ratios and thus have changed the conventional rich-quench-lean diffusion combustion to fully and partially premixed com- bustion. In addition, due to the increase of ignition Damk¨ohler number at elevated tem- perature, the thin flame front flame propagation process in conventional engines is replaced substantially by volumetric ignition. Especially, at ultra-lean fuel conditions, local flame extinction, re-ignition, and ignition to flame as well as ignition to detonation transitions will occur. As such, premixed turbulent flame regimes at high ignition Damk¨ohler may become very different from that of the classical wrinkled and corrugated flamelet regimes (Bradley 1992, Driscoll 2008, Peters 2000) and the conventional incompressible flow, flamelet, and pre-assumed probability density function (PDF) based turbulent combustion modeling ap- proaches may not be appropriate (Peters 1988, Pitsch 2006, Pope 2013) for the new engine modeling. As shown in Fig. 1 (Gou et al. 2010), combustion in engines involves many orders of magnitudes of different time- and length-scales ranging from electronic excitation, molecular diffusion, soot particle formation, sub-grid turbulent mixing, and engine scale flow motion and instability. The main factors affecting the combustion phenomenon depend on the combustion process. For example, for near limit combustion the time scales involving elementary combustion chemistry is important. For engine instability, the timescales of sub- grid turbulent mixing, heat release rate, and acoustic waves are more important. For flame extinction, the molecular diffusion is important. Therefore, the second challenge of combus- tion is how to develop a new turbulent combustion modeling approach which can address the multi-time scale, multi-length scale, and multi-physics combustion processes accurately with detailed kinetic mechanisms. For high speed propulsion such as supersonic combustion and Scramjet engines, vitiated Ju Yiguang : Recent progress and challenges in fundamental combustion research 5
Atom Molecular Microflow Flames Engine combustion Physical process Molecules collisions
Nanoparticles Molecular and turbulent transport scales
Thermo- Soot growth, Mixing, ignition, extinction, flame Physical, chemical chemistry aggregation structure, emissions models Kinetic rates of reactions Turbulent transport-chemistry interaction
Quantum Modeling approach Direct Numerical Simulation Chemistry Statistical Mechanics LES, PDF, RANS
Experiment/validation
10-10 10-8 10-6 10-4 10-2 1 m Fig. 1
Multi-scale processes and multi-scale prediction models in combustion (Gou et al. 2010) air has been widely used in test facilities. As a result, the kinetic effects via air contamina- tion by H2OandNOx on supersonic combustion have complicated the experimental studies for decades. Recently, as reported by Jiang and Yu (2014) the world largest detonation- driven hypervelocity shock tunnel was developed, tested, and calibrated at the Institute of Mechanics in Beijing. This facility significantly extends the current hypersonic test capabil- ity to mimic real flight conditions of Mach number 5∼9 at altitude of 25∼50 km for more than 100 ms test duration, and reduce the kinetic uncertainties due to air contamination.
1.2 New combustion concepts under extreme and non-equilibrium conditions
To enable the above new engine technologies and to achieve low emissions, fuel lean and high speed combustion, various new combustion concepts such as partially premixed and stratified combustion (Dec, 2009), plasma assisted combustion (Starikovskiy 2012, Uddi et al. 2009, Sun et al. 2010), cool flames (Won et al. 2014), microscale combustion (Ju et al. 2011, Fernandez-Pello 2002), and pulsed and spinning detonation engines (Schott 1965, Bykovskii et al. 2006), and nanopropellants (Ohkura et al. 2011, Sabourin 2009) have been developed. These new combustion concepts involve in multi-physical interactions of non-equilibrium chemical and transport processes, and lead to many new combustion 6 ᄺ䖯ሩ 44 ो : 201402 regimes. For example, for high pressure stratified combustion, the flame regimes arising from ignition to flame and ignition to detonation transitions at low temperature conditions are very complicated and have not been well examined (Ju et al. 2011, Sun et al. 2014, Dai et al. 2014) Understanding of cool flame chemistry is extremely important to control engine knocking and to avoid stochastic engine failure. Although cool flames have been observed for many decades (Barnard 1969, Griffiths 1992, Oshibe et al. 2010, Nayagam et al. 2012), establishment of a stable cool flame in laboratories has not succeeded despite numerous attempts. As such, the dynamics, chemical kinetics, and kinetics-transport coupling as well as the cool flame regime diagram remain poorly understood. For example, to date we still do not know how fast a cool flame can propagate and how lean it can burn. On the other hand, for plasma assisted combustion, the highly non-equilibrium energy transfer between electrons, electronically and vibrationally excited molecules, and neutral molecules are not well known (Sun et al 2011, Stancu et al. 2009, Uddi et al. 2009). Moreover, the low temperature fuel oxidation chemistry of large hydrocarbon transportation fuels activated by plasma discharge is also poorly understood (Sun et al. 2014). For microscale energy conversion, the strong thermal and kinetic coupling via flame-wall interaction significantly modified the flame regimes (Ronney 2003, Ju et al. 2003, Maruta et al. 2005, Ju et al. 2005, Xu et al. 2009) In nano-propellant design, functional groups including hydrogen, oxygen, and nitrogen bonds are added to nanosparticles and graphene sheets (Ohkura et al. 2011, Sabourin 2009) to enhance ignition and combustion properties via non-equilibrium photo-chemical and thermal chemical reaction processes. For spinning detonation, the wall curvature and fuel/air mixing have significant impacts on the detonation initiation and propagation modes (Sugiyama et al. 2013). Therefore, the third challenge in combustion is the lack of fundamental understanding of combustion phenomena and flame regimes under extreme and non-equilibrium conditions. 1.3 Alternative fuels
To address the issue of energy sustainability and CO2 emissions from fossil fuels, devel- opment and certification of alternative and renewable fuels from alternative resources and biomass (Chu et al. 2012, Hu et al. 2008, H¨oinghaus et al. 2010, Dooley et al. 2010) have attracted great attention. In the US, about 49 billion liters of corn ethanol (equivalent to 10% of the US annual gasoline consumption) and 4.1 billion liters of biodiesel were produced in 2012. At the same time, unconventional shale gas production has reached one-third of the total US natural gas production. Oil production from tar sand, high hydrogen syngas Ju Yiguang : Recent progress and challenges in fundamental combustion research 7 production from coal and biomass, and synthetic aviation fuel production from natural gas, coal, ethanol, and bio-oils have also increased (Bessee et al. 2011, Simon et al. 2011). Furthermore, the second generation biofuels produced from non-food crops and lignocellu- losic materials will further diversify the feedstock of transportation fuels (Dale et al. 2006, Soetaert et al. 2009, Binder et al. 2009). As shown in Table 1, different fuels have different molecular structures and functional groups, and thus different fuel reactivity and combus- tion and emission properties (Westbrook 2013, Won et al. 2012, Dievart et al. 2012, Gail et al. 2007). Practically, most of the alternative fuels are blended into existing petroleum derived fuels and result in a real fuel with hundreds to thousands of species. On the other hand, advanced engine design requires a generic method to evaluate the performance of alternative fuels involving a large number of species with different functional groups. As such, the fourth challenge in combustion is how we can construct a compact surrogate fuel mixture and kinetic model to model the physical and combustion properties of a real fuel appropriately. Since the resulting surrogate kinetic model will involve several hundreds of species, naturally the fifth challenge is how we can use the large kinetic model of a surrogate mixture to computationally efficiently model turbulent combustion for real fuels (Gou et al. 2010).
Table 1 Fuels with different molecular structures
Normal Branched Valeric Biodiesel, alkane alkane Aromatics biofuels Alcohols Ethers Esters
O O R R OH R 2 1 R2 R1 O
1.4 Experimental and diagnostic methods at high pressure
To develop validated surrogate fuel models, chemical kinetic models, and turbulent combustion models for engine applications, it is important to develop experimental and diagnostic methods with well defined experimental uncertainties so that the measured com- bustion properties can be used in model validation. In last several decades, counterflow flames, spherically propagating flames, flat flames, flow reactors, rapid compression ma- chines, and shock tubes have been developed and used to acquire different experimental targets. However, there are large discrepancies in these experimental data and some of the 8 ᄺ䖯ሩ 44 ो : 201402 key combustion parameters such as the flame speeds and species profiles are not appropri- ately extracted because of the perturbation of sampling nozzles as well as inappropriate assumptions of physical processes and boundary conditions. In addition, with the use of multi-component fuels and excessive exhaust gas recirculation (EGR), the chemical and ra- diation effects from H2OandCO2 and the preferential transport effect of blended fuels will significantly affect the flame dynamics and change the interpretation of experimental data (Ju et al. 1997, 1998, Chen et al. 2007). Therefore, the sixth challenge is how to im- prove and design fundamental combustion experiments with well defined physical processes and boundary conditions so that the uncertainty of the experiments can be modeled and quantified appropriately. As the engine pressure increases and the reaction pathways are more pressure depen- dent. At high pressure, the branching ratio of pressure dependent unimolecular decom- position reactions will become increasingly important in affecting the fuel reactivity. At high pressure and low temperature combustion processes, HO2,H2O2,RO2, and ketohy- droperoxide related fuel oxidation chemistry starts to dominate. Therefore, it is critical to measure the key radicals and intermediate species at elevated pressure to develop low tem- perature chemistry models and to determine the branching ratio of radical decomposition reactions. Unfortunately, due to the high radical reactivity and serious spectra overlaps between HO2,H2O2,RO2, QOOH, and ketohydroperoxides in both infrared (IR) and ultra- violet (UV) regions, the conventional gas sampling methods (Gail et al. 2007, Dooley et al. 2012, Lefkowitz et al. 2012, Tranter et al. 2002,) and molecular beam mass spectrometry (Osswald et al. 2007, Guo et al. 2013, Qi 2013, Taatjes et al. 2008) as well as the laser based diagnostic methods such as the laser induced fluorescence (Li et al. 2013, Ombrello et al. 2006, Sun et al. 2012) and laser absorption methods (Hong et al. 2012, Bahrini et al.
2012) are difficult to be applied to detect HO2,H2O2,RO2, QOOH, ketohydroperoxides, and other key intermediate species (Crowley et al. 1991). As such, the seventh challenge is how to quantitatively measure key radicals and intermediate species at elevated pressure. This review is to provide a summary of the recent progresses in above seven technical challenges. Since the review topic is very broad, it is impossible for this review to include all subject areas and important publications. As such, this review is intended to highlight the major advances in the areas of fundamental research for applications in internal combustion engines and gas turbine engines. Progresses in other specific areas such as oxyfuel combustion (Buhre et al. 2005), supersonic combustion (Billig, 1993, Moorthy et al. 2012, Yu et al. 2013), and turbulent combustion modeling (Pope 2012) can be found in recent reviews Ju Yiguang : Recent progress and challenges in fundamental combustion research 9 in journals such as Proceedings of International Symposiums on Combustion, Progress of Energy of Combustion Science, and Journal of Propulsion and Power.
2 Progress and challenges in combustion research 2.1 The impact of combustion chemistry on turbulent combustion in engines
Unlike the conventional gasoline and diesel engines (Fig. 2), which mainly rely on, respectively, the propagation and transport of premixed and diffusion flames to produce heat release, advanced HCCI and RCCI engines use partially or fully premixed combustion processes with multi-pulse early fuel injection and EGR dilution. As such the combustion process in HCCI and RCCI engines is more dominated by volumetric ignition than flame front propagation. As a result, in advanced engines combustion processes involving auto- ignition and ignition to flame transition play an important role. Ignition process is highly governed by radical initiation and branching processes which depend strongly on the size and structure of fuel molecules Therefore, the heat release rate of advanced engines such as HCCI and RCCI is more affected by initial pressure, temperature, and fuel reactivity than conventional engines. Figure 3 shows the computed ignition delay time of three fuels, n-heptane (normal alkane), iso-octane (branched alkane), and toluene (aromatics) with different molecular structures (Table 1) as a function of temperature at 13.5 atm by using the Real Fuel-2 mechanism (Dooley et al. 2013). It is seen that three fuels have very different ignition delay times due to the difference in their molecular structures. For n-heptane, at both high (larger than 1050 K) and low (less than 700 K) temperatures, the ignition delay time increases exponentially with the decrease of temperature. However,
Gasoline engine Diesel engine HCCI RCCI Fig. 2
Schematic of gasoline, diesel, HCCI, and early injection RCCI engines (Dec.2008, Reitz, 2013) 10 ᄺ䖯ሩ 44 ो : 201402
104 fuel/air mixture, ϕ=1.0, p=13.5 atm 103 toluene 102 iso-octane 101
100 n-heptane lgnition delay time/ms lgnition delay 10-1 0.8 1.0 1.2 1.4 1000/T[1/K] Fig. 3
Ignition delay times of n-heptane, iso-octane, and toluene as a function of temperature at 13.5 atm and stoichiometric condition between 1050 K and 700 K, there is region that the ignition delay time decreases with the decrease of temperature. This region is called the negative temperature coefficient (NTC) region or the low temperature chemistry region (Curran et al. 1998). Note that in the NTC region, the ignition delay time at 13.5 atm is as short as a few milliseconds which are comparable with the combustion timescales in internal combustion engines and gas turbines. Therefore, the NTC chemistry will have a significant impact on the combustion process as the compression ratio of modern engines further increases. Figure 3 also shows that branched alkanes (iso-octane) have longer ignition delay time and weaker NTC effect than normal alkanes. On the other hand, for aromatic fuels, due to the ring stability, no low temperature chemistry is observed and the ignition delay time is much longer than that of normal and branched alkanes. Therefore, the high pressure combustion processes in an engine will be a strong function of fuel molecular structures, particularly at the low temperature region. Failure to control ignition at the NTC region may lead to engine knocking, instability, and an increase of emissions. To show how engine performance is sensitive to fuel molecular structure, Fig. 4 plots a computed time history of the apparent heat release rate (AHRR) as a function of crank angle after the dead center (ATDC) with an n-heptane and iso-octane mixture. It is seen that at 15◦ before TDC, low temperature combustion of n-heptane (cool flame) occurs. As the crank angle approaches to TDC, the in-cylinder temperature and pressure increase and the n-heptane high temperature ignition occurs. As the crank angle passes the TDC, another heat release peak is seen due to iso-octance combustion (longer ignition delay time than Ju Yiguang : Recent progress and challenges in fundamental combustion research 11
Control of combustion duration by ration of fuels 200 Cool iso-octane PRF Burn Flame Burn Primarly n-heptane Primarly 150 n-heptane +entrained iso-octane iso-octane ] Ο
100 AHHR [J/ 50
0 -20 -10 0 10 20 Crank [ATDC] Fig. 4
Time history of heat release rate in a RCCI engine with n-heptane and iso-octane mixture (Reitz 2013) n-heptane, Fig. 3). Figure 4 clearly shows that the combustion process in a RCCI engine is sensitive to fuel molecular structure and that low temperature combustion in NTC region affects the heat release rate. Another example in turbulent combustion with elevated temperature and pressure in air transportation is the staged combustion of in Twin Annular Premixed Swirler (TAPS) burner used for the GEnx gas turbine engine (Fig. 5). In this engine, flames in the highly diluted primary combustion zone are stabilized in the high temperature burned gas region of a premixed pre-burner. Therefore, most of the jet fuel will be vaporized, ignited, and burned at a high temperature and high pressure environment. When the auto-ignition time becomes shorter than the mixing time at elevated temperature, the turbulent combustion and flame instability will be affected by the low temperature ignition. Recent direct numerical simulations (DNS) (El-Asrag et al. 2013, 2014, Zhang et al. 2013) of high pressure and temperature and concentration stratified HCCI combustion using dimethyl-ether (DME) with and without exhaust gas recirculation (EGR) effects showed that, due to the existence of low temperature chemistry of DME, two different ignition- kernel propagation modes were observed (Fig. 6(a)): a wave-like, low-speed, deflagrative mode (the D-mode) and a spontaneous, high-speed, kinetically driven ignition mode (the S-mode). Three criteria were introduced to distinguish the two modes by different character- 12 ᄺ䖯ሩ 44 ो : 201402
Fig. 5
Schematic of Twin Annular Premixed Swirler (TAPS) burner (Mongia 2010)
a b
Q J/m3/s)
8Τ1010 7Τ1010 6Τ1010 5Τ1010 4Τ1010 3Τ1010 2Τ1010 1Τ1010 0
OH
HO2
Fig. 6
(a) Heat release rate of different flame modes (AB and CD) due to fuel (dimethyl ether) and temperature stratifications in a turbulent flow (EI- El-Asrag et al. 2013), (b) OH and HO2 distributions of an ethylene lifted jet flame with the co-flow temperature at 1550 k (Yoo et al. 2011) istic timescales and the ignition Damk¨ohler number using a progress variable conditioned by a proper ignition kernel indicator. The results showed that the spontaneous ignition S-mode was characterized by low scalar dissipation rate, high mixing Damk¨ohler number, and high displacement speed ignition front, while the D-mode was characterized by high scalar dissi- pation rate and low displacement speeds in the order of the laminar flame speed with a small ignition Damk¨ohler number. Another DNS of the near field of a three-dimensional spatially- developing turbulent ethylene jet flame in highly-heated co-flow was performed by Yoo et al. (2011) to determine the flame stabilization mechanism. The DNS was performed at a jet Reynolds number of 10,000 with over 1.29 billion grid points. The results in Fig. 6(b) of OH (heat release process) and HO2 (ignition and chain initiation process) distributions Ju Yiguang : Recent progress and challenges in fundamental combustion research 13 show that, at an elevated co-flow temperature, auto-ignition in a fuel-lean mixture at the flame base is the main source of stabilization of the lifted jet flame. The Damk¨ohler number and chemical explosive mode (CEM) analysis also verified that auto-ignition occurred at the flame base. It was also observed that the lifted flame base exhibited a cyclic ‘saw-tooth’ shaped movement marked by rapid movement upstream and slower movement downstream. This was a consequence of the lifted flame being stabilized by a balance between consecutive auto-ignition events in hot fuel-lean mixtures and convection induced by the high speed jet and co-flow velocities. The above DNS results clearly show that auto-ignition involving low temperature chem- istry for large hydrocarbon transportation fuels may play a very important role in turbulent combustion of engines. Unfortunately, to date the major focus of turbulent combustion has been placed on the measurements of high temperature flame burning velocities and flame structures (Bradley 1992, Driscoll 2008, Peters, 2000, Yuen et al. 2009) and the effects of pressure (Kobayashi et al. 1997, Soika et al. 2003), Lewis number (Bradley 1992, Rutland et al. 1996, Chaudhuri et al. 2012), preferential diffusion (Dunn et al. 2013), and turbulent flame geometry (Smallwood et al. 1995, Shepherd et al. 1992). The measured turbulent burning velocity (ST ) normalized by the laminar flame speed (SL) is fitted as a function of the normalized turbulent intensity (u /SL), the Lewis number (Le), the turbulent integral length scale (l), and the laminar flame thickness (δf ) (Bradley 1992, Driscoll 2008, Peters 2000, Chaudhuri et al. 2012), S u l n T =1+CLe−1 (1) SL SL δf where C represents a constant and n is an adjustable exponent. A turbulent flame regime diagram called the Borghi diagram was used to specify the turbulent flame regime based on the turbulent time scale (l/u ) and the flame time scale (δf /SL) (Peters 2000, Borghi 1984, Li 1994). Although, this turbulent diagram provides very insightful information for different flame regimes such as the wrinkled, corrugated, thin reaction zone, and distributed reaction zone flames, it only includes one characteristic timescale of the flame speed. The ignition timescale is not considered in the Borghi diagram. As a result, the Borghi diagram and the turbulent flame speed relation in Eq. (1) may not be applicable directly to the advanced engines in which ignition and low temperature fuel oxidation play an important role. Therefore, a question naturally arises: how does the low temperature fuel chemistry and auto-ignition at elevated temperature affect the turbulent flame propagation and the Borghi diagram? Additionally, will the turbulent burning velocity still be a well-defined 14 ᄺ䖯ሩ 44 ो : 201402 value when the low temperature reactivity changes the fuel composition and reactivity via low temperature oxidation? Figure 7 schematically shows how the increase of fuel reactivity at elevated tem- perature (ignition Damk¨ohler number) affect the turbulent flame regime. At low ignition Damk¨ohler number, turbulent flame regimes are governed by the length scale of turbulent mixing (e.g. the Taylor microscale) and the thickness of the reaction zone. When the tur- bulent mixing scale is smaller than the thickness of the thin reaction zone, the thin flame regime becomes a distributed reaction zone. However, when the ignition Damk¨ohler number is increased at high temperature due to low temperature chemistry, the flame regime will be affected by the turbulent mixing time, the auto-ignition time, and the flame propagation time. If the auto-ignition time becomes shorter than the flame propagation time, a broad- ened, distributed reaction zone due to auto-ignition will occur (Fig. 7). Unfortunately, few previous studies have addressed the transition between ignition and flame propagation in
103 Distributed reaction zone Thin reaction 102 zone L 1 S
' 10 u Corrugated flamelet 100 Wrinkled Turbulent intensity Turbulent flamelet 10-1 10-1 100 101 102 103 104 103 Distributed 1 dL Turbulent scale reaction zone Thin reaction 102 zone Da ig > L 1 1 S
' 10
u Corrugated flamelet 100 Wrinkled flamelet 10-1 10-1 100 101 102 103 104
1 dL Progress of fuel oxidation Turbulence/chemistry interaction Fig. 7
The change of turbulent flame diagram with the increase of ignition Damk¨ohler Ju Yiguang : Recent progress and challenges in fundamental combustion research 15 turbulent combustion. To demonstrate the effect of low temperature ignition on turbulent flame propaga- tion, recently a new high temperature, high Reynolds number, Reactor Assisted Turbulent Slot (RATS) burner has been developed to investigate turbulent flame regimes and burning rates for large hydrocarbon transportation fuels (Won et al. 2014). The turbulent flow characteristics were quantified using hot wire anemometry. The turbulent flame structures and burning velocities of n-heptane/air mixtures were measured by using planar laser in- duced fluorescence of OH and CH2O with reactant temperatures spanning from 400∼700 K. Figure 8 shows the dependence of flame luminescence and shape on the reactor tempera- ture. Figure 8(a) represents the conventional thin flame front chemically-frozen-flow flame regime. In this case, the initial mixture temperature was so low (500 K) that there was no fuel reactivity before the flame front. However, as the reactor temperature was increased to 700 K with the same flow residence time, Figs. 8(b)∼8(d) show a new turbulent flame regime, the low-temperature-ignition regime. In this flame regime, fuel is partially oxidized due to the low temperature chemistry. Therefore, the conventional assumption of flamelet fails. At Treactor = 700 K, by reducing the flow velocity (increasing the Damk¨ohler number) from 10 to 6 m/s, a transitional regime from low temperature ignition to hot ignition in
(a) (b) (c) (d) (e) (f)
Treactor=500 K 600 K 650 K 700 K 700 K 700 K U=10 m/s 10 m/s 10 m/s 10 m/s 10 m/s 6 m/s
Increasing the ignition Damkohler number & fuel reactivity
Fig. 8
Direct photos of n-heptane/air turbulent flames at ϕ =0.6 with increasing of igni- tion Damk¨ohler number and fuel reactivity, exhibiting distinctive four flame regimes; (a) chemically-frozen-flow regime, (b)–(d) low-temperature-ignition regime, (d) and (e) transi- tional regime between low- to high-temperature-ignition regimes, and (f) high-temperature- ignition regime (Won et al. 2014) 16 ᄺ䖯ሩ 44 ो : 201402 the reactor is observed from Figs. 8(d) and 8(e). This result clearly shows that the flame regime diagram in Fig. 8 needs to be dramatically changed when the ignition Damk¨ohler number is increased at practical engine conditions. To further quantify the effect of low temperature chemistry on the turbulent flame speed, Fig. 9 shows the dependence of normalized turbulent flame speeds and the OH/CH2O planar laser induced fluorescence (PLIF) as a function of turbulent fluctuation velocity at low and elevated temperatures. For the first time, Fig. 9 (left) shows that the turbu- lent burning velocities have two different flame regimes, a chemically-frozen-flow regime and a low-temperature-ignition flame regime, respectively, at low (a) and high (b) reactor temperatures with different turbulent flame speeds. Moreover, the turbulent flame speed at the low-temperature-ignition regime is higher than that of chemically-frozen-flow. The
OH/CH2O PLIF images (right) show clearly the difference of turbulent flame structures of these two flame regimes and the CH2O formation of the low-temperature-ignition flame regime. It is also interesting to note that, contrary to the previous studies, the results in Fig. 9 suggest that the turbulent flame burning velocity for fuels with low temperature chemistry may not be uniquely defined. Rather, it depends on the magnitude of ignition
n-heptane/air, 0.3<φ<1.1, a b 0.68 b 400 < <700 ) 6 K Treactor K ' L u S ' =3.0 Τ( at fixed u SL 60 mm T =650 K =1+1.53 reactor SL ST )0.87
L ' L 4 Τ(u S