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Laser Ignition System
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As the demand for higher engine efficiencies and lower emissions drive stationary, spark-ignited reciprocating engine combustion to leaner air/fuel operating conditions and higher in-cylinder pressures, increased spark energy is required for maintain stable combustion and low emissions. Unfortunately, increased spark energy negatively impacts spark plug durability and its effectiveness in transmitting adequate energy as an ignition source. Laser ignition offers the potential to improve ignition system durability, reduce maintenance, as well as to improve engine combustion performance.
This paper discusses recent engine combustion testing with an open beam path laser ignition system in a single- cylinder engine fueled by natural gas. In particular, engine knock and misfire maps are developed for both conventional spark plug and laser spark ignition. The misfire limit is shown to be significantly extended for laser ignition while the knock limit remains virtually unaffected. These results are discussed in detail as are other combustion related phenomena.

.doc  Laser Ignition System.doc (Size: 1.19 MB / Downloads: 1324)

Sl No. Titles Page No.
1 Introduction 5
2 Background 6
3 Experimental 8
4 Description of Timing Schemes 8
5 Spark Energy Measurement 12
6 Engine Test Bed 17
7 High Speed In-Cylinder Data Acquisition 17
8 Test Procedure 18
9 Results and Discussion 19
10 Variable Timing/Equivalence Ratio 26
11 Conclusions 29
12 Definitions, Acronyms and Abbreviations 30
13 References 31

Fuel-lean combustion yields lower combustion temperatures which lead to lower NOx, and higher thermal efficiency due to lower heat losses. Lean mixtures of natural gas and air are relatively difficult to ignite. Also, as engine are forced to operate at higher power densities to further improve efficiency, the resulting increase in in-cylinder pressure at the time of ignition further impedes the quality of the electric spark discharge. Providing the necessary ignition energy to ignite low emission ultra-lean burn natural gas engines or highly efficient (high BMEP) engines severely limits spark plug life and creates a significant operating cost to the user. The lack of spark plugs with the required durability is quickly becoming the limiting factor for their development. The investigation of laser ignition's feasibility and performance is warranted by the potential to improve ignition system durability as well as to improve engine combustion and emission performance.
In contrast to conventional spark plug ignition, the point of ignition (spark) from a laser can be positioned at a considerable distance from potential heat sinks thus eliminating problems involving flame kernel heat transfer quenching common in spark plugs. High peak power laser pulses can be focused to a point to create strong sparks with high surface area. Laser-induced sparks can create instantaneous temperatures and pressures approaching 105 K and 103 atm, respectively with a sudden release of large quantities of reactive and excited chemical species. These extreme local conditions relative to the surrounding gas give rise to rapid, supersonicexpansion and dissipation of energy in the form of heat thus providing for hydrocarbon bond breaking and radical species production.
In this study, we investigate combustion, knock and misfire limits of a single-cylinder engine operating with a laser ignition system. A comparison is made at the same engine operating conditions using a conventional spark system.

The history of laser induced ignition has progressed in three distinct directions. The first is the theoretical analysis of the breakdown phenomenon in which the physical ignition processes at the molecular level of the ignition event are investigated. The second is comprised of laboratory experiments conducted to gain insight and understanding of the ignition process and to help test and tune previously developed theories. The third consists of experiments and analysis performed on slider-crank piston engines to gauge the effectiveness of laser energy ignition on the engine operating parameters.
Past theoretical studies have lead to the statistical development and comparison of ignition delay and ignition probability models to experimental observations allowing the direct correlation of gas (usually methane) concentration to ignitability and ignition delay. Theoretical analysis has also led to the development of shock wave heating models, which aid in the explanation of the propagation of hot expanding gas, produced by the laser spark, that perpetuates the combustion process. Further theoretical examinations and the availability of experimental data have allowed researchers to develop more precise estimations of the minimum required laser induced breakdown energy required for ignition of combustible gases as well as focal length effects.
The method by which the laser induces breakdown in a combustible gaseous mixture has been divided into four basic processes: thermal heating, non resonant breakdown, resonant breakdown and photochemical excitation. Thermal heating takes place where the laser beam is incident on a solid target and induces excitation by heating the target or by exciting a rotational or vibrational modes of oscillation in the surrounding gas. Resonant breakdown occurs when the incident radiation ionizes the gas molecules and frees up electrons to absorb the radiation energy and in turn ionize other gas molecules leading to an avalanche breakdown.
Photochemical ignition occurs when a single photon dissociates a molecule thus allowing the ionized constituents to react with the surrounding gases. Non-resonant breakdown occurs when laser light is focused into a gas and the electrical field component of the light is strong enough to initiate the electrical breakdown of the gas. The non-resonant breakdown mechanism is the predominant factor governing the results presented in this work.
Experimental studies have been vital to extending the value of the theoretical examinations and in gaining a further understanding of the combustion process. Combustion vessel and open flame jet experimentation with methane (CH4) and other combustible gases have proven invaluable in the search for better fuel economy and emissions and provide a better understanding of the general ignition and combustion processes. Results of the laser spark combustion vessel studies has indicated a shortened ignition delay and higher peak pressures than an electrical spark ignited combustion event. Some studies investigated the ignition energy effect on the combustion process and found that for stoichiometric conditions the amount of energy had only a slight pressure dependence, however more energy was required for breakdown as the equivalence ratio approached either lean or rich conditions Other studies have examined multi- point laser ignition as a means of gaining quicker combustion which allows for higher thermal efficiency due to reduced time for thermal losses during the combustion event and overall shorter travel distances for the flames [8,12]. The most promising result of the combustion vessel examination of laser ignition is the ability of the optical energy to ignite and more readily burn lean mixtures. This offers the potential for extending the lean limit in spark ignited engines which is, in part, the purpose of this study.
Laser ignition studies performed on internal combustion engines have allowed researchers to directly study the effect that laser induced ignition has on the operating and emissions characteristics of an operating engine. Past and recent studies have indicated a higher and quicker combustion pressure rise with laser ignition. The experimentation performed by Dale et al., used a gasoline-fueled stoichiometric operating internal combustion engine for testing.
The research performed by Ma et al., involved a motored slider crank mechanism that was not self sustaining. To date, prior work at NETL and in Austria represent the only natural gas-fueled lean-burn engine studies.

Natural gas was used as the test fuel. Its chemistry was determined via gas chromatographic analysis during each test series to account for C/H ratio, heat of combustion as well as hydrocarbon makeup. The ignition system used in baseline testing was a commercial microprocessor based inductive ignition system designed for use on stationary gaseous-fueled industrial engines operating in a variety of applications. Timing was adjustable over a range of 50o CA and spark dwell was adjustable from 500 to 2,000 microseconds. A constant spark dwell of 1500 microseconds was used throughout testing.

During the course of the investigation precise timing adjustments must be made in order to accurately compare the spark events. Careful attention must be taken to ensure that the two systems are timed properly with respect to the experimental test plan and identically, to each other, to ensure the quality of the combustion and emissions data collection. It is assumed and has been verified that the signal propagation times through the electrical systems are negligible, as compared to the overall time scale of the combustion event. The optical path length for the laser was also considered to pose a negligible effect on the operation of the laser ignition system.
The electric spark was timed and initiated via an ignition controller. This unit utilized a Hall Effect sensor to discern the cam position and a flywheel encoder to determine the crank position in order to properly time the electrical discharge. The cam sensor produced a logic low pulse, of a fixed width, that indicated the cam position at 180 degrees before top dead center encoder to initiate the spark at the proper time.A side-gap type spark plug was used for the electrical discharge testing. The side-gap plug style was chosen over the standard J-Gap plug due to slight perceived advantages in start up and cyclic variability performance. A picture of the side gap spark plug can be found in Figure 1. For scale, the threads are standard 14 mm spark plug threads. The plugs were torqued for repeatable alignment in the engine but were not indexed for any necessary alignment direction due to the type of combustion chamber (torroidal) used in this study. In the torroidal bowl, the nearly centrally located plug, was located at the center of the swirl axis.

Figure 1: Side Gap Spark Plug

The timing, as well as the spark energy, was also independently measured and verified via compensated voltage and current probes. These probe types have been used and described in previous ignition studies. The voltage and current waveforms were then displayed with respect to time on a digitizing oscilloscope. The current transformer was mounted on the engine near the ignition system and the spark plug wire was allowed to pass through the center of the probe. The current probe converted the current pulses through the spark plug wire into a voltage waveform that was directly proportional to the amount of current flowing in the secondary wire lead. The voltage probe was connected directly to the center conductor of the secondary spark plug wire. The current and voltage measurement setup are illustrated in Figure 2.

Figure 2: Current and Voltage Measurement Setup for
Electrical Spark Engine Testing.

The voltage, current, and cam trigger waveforms are simultaneously displayed on the oscilloscope. For simplifying this description, only the cam trigger and the current waveform are used to determine the amount of time between the cam trigger signal and the flow of current across the spark plug gap indicating the start of the ignition discharge inside the combustion chamber. The simplified waveforms are illustrated in Figure 3. The timing delay is measured under test.
The laser spark ignition system utilized the same Hall Effect sensor as the electrical discharge ignition system. The signal from the cam sensor is tapped and fed into a digital delay/pulse generator which acted as a compatible interface between the hall sensor and the pulse delay generator used to trigger the laser. The trigger pulse delay was calculated from the cam signal event, given the speed and timing advance (oCA btdc) desired. The laser system used for this project had a delay time from triggering of the device to laser light exiting the output aperture of approximately 180 microseconds, a pulse width of 3-5 nanoseconds and a pulse to pulse jitter of +/- 0.5 nanoseconds [26]. The most significant of the above properties is the delay time which is approximately two orders of magnitude smaller than the time scale of the ignition process.

Figure 3: Cam Trigger and Current Probe Waveforms
In order to measure and verify the laser spark system ignition timing a 1064 nm reflectively coated high energy laser mirror was used as the final turning mirror for the open beam laser spark setup. A fiber optic cable with a collimator was fixed above the mirror to capture the light from the spark and combustion and couple it into a photo multiplier tube (PMT) detector assembly for sensing and amplification. The PMT included a UV filter in front of its aperture that only allowed the spectrum between 300 and 400 nanometers. This ultraviolet (UV) pass filter ensured that the light that fell upon the sensor was indeed from the spark and/or the combustion event due to the presence of OH- radicals in the spark or the combustion flame. The timing system for the laser spark ignition setup also doubled as a way to indicate laser spark integrity in the engine. The voltage waveform signal produced by the PMT was then fed into the digitizing oscilloscope along with the cam trigger signal to determine and verify the correct ignition timing which is very similarly depicted in Figure 3.

In order to more accurately compare the possible differences between the two ignition systems it was necessary to have an accurate measurement of the amount of energy each system delivers to the cylinder. The energy measurement system devised for the electrical discharge system used the high voltage probe and current transformer discussed previously and found in Figure 1. The waveforms were displayed on the digitizing oscilloscope and analyzed using the method found in SAE J973 surface vehicle recommended practice publication. The energy delivery measured for the spark plug was found to be approximately 68 mJ per spark. Energy loss to the electrodes or energy losses due to radiative mechanisms are unknown. The spark plug did not contain an internal resistor. A sample of the experimental waveforms for both voltage and current can be found in Figure 4.

Figure 4: Electrical Current spark voltages and
Waveforms used for measuring spark energy.

The energy measurements for the laser spark system were carried out with two laser energy meters. The first energy meter was placed behind a 2.1% beam splitter to provide online laser pulse energy readings throughout the experimentation. The second was used for the characterization of the optical system from test to test. The complete open-beam system was found to have a total energy loss of approximately 25-30%. The laser plug without the final turning mirror was found to have a loss of approximately 15%. The loss percentage for the final focusing lens in the laser plug was thought to be high, as compared to the rest of the system, due to the fact that it was not anti-reflection coated, on either surface, due to the elevated operating temperatures that it would encounter. The tests were performed with input energies that would produce no less than 50 mJ per pulse once the system and plug losses were factored in. Figure 5 contains a photograph of the laser plug and engine adaptor and a laser plug without the engine adaptor.
Due to engine head geometric constraints the laser plug window lens pressure barrier was not placed within the 14 mm spark plug threads but had to be recessed approximately 24 mm inside the engine adaptor. The focal length of the final lens was 30 mm so that the focus (and spark) would occur approximately 6 mm below the top of the combustion chamber well away from any combustion chamber surfaces. Figure 6 contains a photograph of the laser plug window lens pressure barrier mount that is sealed into the engine adaptor approximately 24 mm above the combustion chamber. The clearance volume is actually 1% greater due to the laser plug. This effectively reduces the compression ratio from 13.3 to 13.2. This slight difference is discussed in terms of its minimal impact in these combustion analyses.

Figure 5: Photograph of laser spark plug with engine
adaptor and laser spark plug alone.

Figure 6: Photograph of the laser spark plug window
lens pressure barrier assembly.

The laser spark ignition system optical bench and laser plug setup is illustrated in Figure 7. The abbreviations are as follows: HR-High Reflector, EM-Energy Meter, BE-Beam Expander, PCX-Plano Convex Lens, PCC- Plano Concave Lens, ADJ. BE-Adjustable Beam Expander. The beam expander on the output of the alignment laser was used to set the alignment beam to approximately the same beam diameter as the high energy Nd:YAG laser beam, which aided in the overall alignment process. The adjustable beam expander was used to vary the beam diameter of the high energy laser beam. The beam diameter for the YAG laser had a direct relationship on the energy density of the laser beam for a given amount of energy per pulse. Therefore the beam diameter for the laser energy just prior to reaching the last mirror, which is mounted directly onto the laser plug, was held constant at approximately 4-4.5 millimeters.

Figure 7: Laser ignition system optical bench
and laser plug setup.

Throughout the engine testing the laser alignment was monitored by the PMT module. The optical collection system and PMT module were connected the same way as previously described. The output signal was also connected to monitoring equipment consisting of a boxcar averager and a PC for data interpretation. The averager was setup to integrate the PMT signal for a particular window of time which only encompassed the ignition pulse. The integrated values were then averaged over three samples and displayed via custom software interface. Along with the average values the standard deviation and raw values were also displayed. By recording the average light output over the course of engine testing, it was very easy to determine any trends in the mean or standard deviation that would indicate a gradual misalignment. When a misalignment was detected, very careful and accurate on the fly adjustments were made between tests to ensure adequate alignment and repeatable energy delivery for subsequent testing at energy levels greater than 50 mJ per pulse. The threshold of 50 mJ per pulse represents an energy threshold above which additional energy has no apparent effect on the ignition event.
The engine facility is located at the U.S. Department of Energy's National Energy Technology Laboratory (NETL) in Morgantown, WV. The engine, a Ricardo Proteus, is a two-valve, four-cycle engine with a toroidal combustion bowl in the piston. The engine has a bore and stroke of 130 mm (5.1 in) and 150 mm (6 in) respectively and a swept volume of 1.997 liters (122.4 cu in) with a compression ratio of 13.3:1. Startup and engine load are controlled by a 420-volt, 100 hp (75 kW), DC dynamometer. Turbocharger conditions are simulated by using a filtered, dried, preheated and pressurized site air source and by using a backpressure control valve in the exhaust. Air/fuel mass ratio is determined via mass flow measurement of both engine inlet air and natural gas fuel. A UEGO exhaust oxygen sensor is also used as a separate reference. NG mass flow was measured using a coriolis mass flow meter. The flow rates used in this study are always well into the mid to upper range of the instrument thus ensuring low measurement error. Engine air flow is measured by using a viscous flow meter which was “flow proven” using a secondary NIST traceable flow standard. An uncertainty analysis of A/F mass ratio using the RMS method indicates 95% uncertainty error of approximately 1.5% of the indicated A/F mass ratio. This is less than the reported accuracy of the UEGO sensor. For this reason as well as our experience that the UEGO signal contains much more noise, we chose the mass flow measurement based A/F mass ratio as our standard. Subsequent analysis of the fuel was required for determination of lamba (λ) or equivalence ratio (φ). This was obtained via GC analysis.

A rapid response piezo-electric pressure transducer is used along with a high-speed digital data acquisition system, triggered by a crankshaft mounted incremental encoder. This study employs the use of a multiple channel indicating system for recording cylinder pressure in relation to crank angle. Data is recorded at an overall throughput of up to 1 MHz. An uncooled gallium orthophosphate (GaPO4) piezoelectric pressure transducer is used for in-cylinder pressure measurement. GaPO4 is chosen for its thermal stability at high temperatures. A piezo amplifier is used to condition the output of the transducer. The piezoelectric transducer is ranged at 200 bar and has a linearity of less than ±0.3% full scale output at operating temperature. Its thermal sensitivity shift in the 200oC to 300oC range is less than ±0.5%. Its cyclic temperature drift and indicated mean effective pressure (IMEP) stability over a 10 hour test period is less than ±0.4 bar and 2% respectively. Engine speed and crank angle (oCA) position are measured using a high-precision optical encoder mounted on the crankshaft end. Crank angle measurement is selectable down to 0.05 oCA. Thermodynamic values based on cylinder pressure and heat release using a simplified first law analysis and employing a constant polytropic coefficient is used as recommended by Randolf.

The engine and associated equipment were allowed to reach equilibrium conditions with inlet air temperature, oil temperature and coolant temperature held constant at 40oC, 80oC and 80oC respectively and engine speed at 30 rev/sec (1800 rpm).

Timing was held constant at 32o btdc. A constant fueling/variable boost approach was taken for the knock and misfire investigation. Fuel rate was held constant at 1.33, 1.58 and 1.82g/s for BMEP levels of 8, 10 and 12 bar respectively. Boost was adjusted over a range of 26 to 117 kpag to control air/fuel ratio. To approach knock or misfire the boost was adjusted in an ascending manner toward misfire limit or a descending manner toward the knock limit. Each approach to misfire (or conversely knock) was followed by an approach to the opposite limit in blocks of two approaches. Three groups of two approaches were randomized and these were further blocked into three groups of load level (8 bar, 10 bar and 12 bar BMEP). By randomizing the approach order and load order, the effect of sequential engine conditioning was minimized.

Both spark plug and laser testing were blocked into three groups of 20 tests (4 levels of ф , 5 levels of spark timing). In each group, ф was randomized into four blocks. Within each block of ф , five timing points of 20, 24, 28, 32 and 36o btdc were also randomized giving 60 separate engine operating conditions. At each change in engine test condition, the engine was allowed to stabilize and combustion data were recorded. The time required for stabilization was maintained constant for each set point change, thus aiding measurement repeatability. Inlet air, oil and coolant temperatures were kept constant at each key state condition. By varying timing and equivalence ratio, the response of emissions and combustion provide an understanding of the combustion and ignition phenomena.


Engine startup was readily obtained using the laser spark system. Aligning the laser beam perpendicularly to the window-lens-mirror assembly (tangential to the radial engine axis) minimized the effect of the radial and axial engine vibration components. The optical pressure boundary in the laser lens/plug/window assembly remained clean during engine operation periods of up to 10 hours. We have accumulated approximately 100 hours of laser spark engine operation to date, but we have not attempted single period operation of more than 10 hours after which time we examine the window assembly. It appears that the laser beam energy delivered to particles near the window assembly is sufficient to prevent deposition. However, abnormal operating conditions or significantly longer operational periods required for commercial operation have not been purposely investigated. Optical damage due to the high power density of the laser over a longer period of time should also be investigated to provide the knowledge base for development of durable components necessary for this application.

The regularity of combustion in spark ignition engines is often characterized by examining the cyclic variation of the indicated mean effective pressure (IMEP). IMEP is derived from dynamic engine pressure measurement. It may be thought of as the cyclic work divided by the displaced volume. Variations in IMEP are closely associated with hydrocarbon emissions as well as thermal efficiency. Generally, misfire starts to occur at IMEP coefficient of variation (COV) levels of approximately 5%-10%. An IMEP COV of 10% was chosen as the definition of the misfire margin for these studies.
Engine knock is a debilitating phenomenon characterized by rapid combustion (detonation) usually in the end gas region. The resulting shock waves breakdown the thermal boundary layers within the cylinder and the resulting high heat transfer to the piston, cylinder liner and valves result in damaging surface temperatures in these components. Engine knock must be avoided in any engine system and understanding and identifying the engine operating characteristics that produce knock is paramount. High frequency pressure oscillations are measured in the engine to define the knock limit. The pressure voltage signal from rapid response piezo-electric pressure transducer is high pass filtered at 4000 Hz. Each engine cycle of this filtered signal was examined to determine its maximum peak amplitude. These peaks are then averaged over 200 engine cycles to determine the measurement denoted in this work as P_HighMaxAve. The P_HighMaxAve threshold value of 1 bar is used as the knock margin criteria.
The data, for either knock (P_HighMaxAve) or misfire (IMEP COV), is generally spread around the misfire or knock limit. The six blocked data points are fitted in a first order linear regression model with the 95% confidence interval plotted to predict the threshold crossing point. An example of this type of plot is given below in Figure 8.

Figure 8: Scatterplot showing equivalence ratio as a function of I
MEP COV for laser operation at 12 barBMEP and 32obtdc timing.
The 0.95 confidenceintervals are plotted about a linear curve fit
With r2=0.9233.

The graph shows the six data points, the linear regression line crossing the 10% IMEP COV line at an equivalence ratio of approximately 0.5122 and 95% confidence boundaries at approximately 0.5110 and 0.5135. This method was followed for all of the misfire data and similarly for the knock data except that a value of one bar for the P_HighMaxAve was used as the threshold criteria.
There are two levels of engine operation (knock or misfire) with six replications each, three load conditions (8, 10, and 12 bar BMEP) and two ignition systems (laser and spark plug) for a total of 72 data points. These six replications are averaged and plotted with their associated 95% confidence error bars on an equivalence ratio/BMEP plot in Figure 9. A visual inspection of Figure 9 indicates an extended misfire limit; however the knock limit is generally unchanged as will be explained.

Figure 9: Knock and Misfire Boundaries for Laser and Spark Plug Engine Operation at 32obtdc Spark Timing

Upon first inspection of the knock limit, with the exception being 8 bar BMEP knock, there is a statistically significant difference between laser and spark plug ignition (p<0.05). However, the actual start of combustion (SOC) is also significantly (p<0.05) different. Considering all of the knock data, the average laser ignition SOC begins 2 CA prior to the spark plug (-14.5 oCA vs. -12.5 oCA). This represents an approximate 7% reduction in ignition delay time. In fact, a difference of 2oCA is fairly typical of each BMEP as indicated by the histogram plot in Figure 10 below.

Figure 10: Histogram, with mean frequency distribution,
of Start of Combustion (SOC) for each load and ignition

A normal distribution fit to the ignition delay data is also plotted along with the histograms. Note that the “spread” in the ignition delay data, which may be represented as its variance or standard deviation, is visually less (i.e. the “spread” in the normal distribution curve is narrower) for the laser spark system. In fact, when considering the data obtained at the misfire limit, the coefficient of variation (COV) of the ignition delay is 4.0% for the spark plug and 1.9% for the laser system. The decrease in ignition delay and it lower COV for the laser ignition system is further indication of the robustness of the ignition event and subsequent flame kernel formation. Further study of the laser ignition event is warranted to understand the spark/flame kernel interaction mechanism and for insight into potential additional benefits that may be gained.
Since it is well known that engine knock is dependent on spark timing, hence SOC, the spark timing was adjusted or spark plug operation to account for the 2oCA retard in SOC experienced with the spark plug over that of the laser at 32obtdc spark timing. Operation was repeated at 10 and 12 bar BMEP. The results are given in Figure 11.
Even with the 2oCA timing advance, the average spark plug SOC was still 0.8oCA retarded over that of the laser at 32obtdc timing. From Figure 11, the spark plug knock limit converged toward the laser knock limit, however, there was still a significant difference at both load conditions (p<0.05).

Figure 11: Knock limit for laser andpark timing spark plug operation at 32obtdc spark timing
and spark plug operation at 34obtdc spark timing at 10 and 12 bar BMEP.
The error bars represent the 95% confedence interval

Minor differences in 10-90% burn duration and the remaining differences in SOC may account for this difference. Temperature, pressure, fuel rate, speed (hence turbulence) and equivalence ratio were constant throughout testing. Combustion phasing is the suspected mechanism that would account for the differences in knock limit.
There were similar differences (p<0.05) in SOC at the misfire boundary. Since it is well known that engine misfire is also dependent on spark timing, hence SOC, the spark timing was adjusted for spark plug operation to account for the 2oCA retard in SOC experienced with the spark plug over that of the laser at 32obtdc spark timing. Operation was repeated at 10 and 12 bar BMEP. The results are plotted in Figure 12.
The average SOC for the spark plug at 32obtdc spark timing was 1o after top dead center (atdc) while for laser operation at 32obtdc spark timing it was 0.5obtdc. This is a difference of 1.5oCA. Again using a 2oCA advancement in timing at 10 and 12 bar BMEP for the spark plug revealed a significant change in the misfire limit (p<0.05), however, the change moved the limit to higher equivalence ratio. This phenomenon occurred in spite of the fact that the average SOC moved from 1oatdc to 1.5obtdc in moving spark timing from 32obtdc to 34obtdc. Irregardless, the difference in misfire limit is very strong. These results clearly indicate lean misfire limit extension via laser ignition in an operating lean- burn natural gas engine.

Figure 12: Misfire limit for laser and spark plug operation at 32obtdc
spark timing and spark plugoperation at 34obtdc spark timing at 10
and 12 bar BMEP. The error bars represent the 95% confidence
interval. To further understand combustion related phenomena
associated with laser spark ignition, a series of engine
tests with varying timing and air/fuel ratio
were conducted.

Once ignition has occurred in a self sustaining combustible mixture, the flame propagation rate for a given engine condition (pressure, temperature and air/fuel ratio) is dependent on the fuel chemistry and turbulence level. As engine speed, hence turbulence, is held constant and fuel chemistry changes are negligible (for example, the average molecular weight of NG varied by no more than 0.24% over the test period), any differences with burn rates must be due to combustion phasing. In the experiment, the duration between the point of 10% mass fuel burned and 90% mass fuel burned (10-90% burn duration) is a good representation of the flame propagation rate. The average 10-90% burn duration is given in Figure 13 for the full data set as a function of SOC. The burn duration averaged 1.4oCA longer for the laser (35.6oCA vs 37.0 for the laser) while the SOC for minimum 10-90% burn duration is 4.5obtdc for the laser and 3.8obtdc for the spark plug. Note that the test conditions for the figures in this section are given in the test procedures section under “Variable Timing Combustion Testing.”
Although the burn duration is slightly longer for the laser, the location of the point at which 90% of the mass fraction of fuel is burned is slightly earlier for the laser. Burn rate and its affect on combustion phasing, can account for differences in many engine parameters. For example, engine thermal efficiency is well correlated with SOC and the 10-50% burn duration (Correlation coefficients of -0.91 and -0.72 respectively).

Figure 13: 10-90% Burn Duration as function of SOC.
The minima for 10-90% burn duration are located at
-4.5oCA and -3.8oCA for the laser and spark
plug respectively

Shorter burn duration also allows for less time for heat transfer during the combustion period and initial expansion stroke. Engine thermal efficiency for the laser and spark plug are given in Figure 14 as a function of SOC and in Figure 15 as a function of 10-50% burn duration. Engine thermal efficiency (ENTHEF) reaches its maxima for laser ignition at an SOC of 8.7obtdc (38.7%) and for spark plug ignition at 7.1obtdc (39.4%). The 10-50% burn duration data in Figure 15 indicates a crossover as the spark plug burn duration apparently decreases beyond that for laser ignition at approximately 12.8oCA duration.

Figure 14: Engine Thermal Efficiency (ENTHEF) for
Laser and spark plug operation as a function of start of
combustion (SOC).

Figure 15: Engine Thermal Efficiency (ENTHEF) for
laser and spark plug operation as a function of 10-50%
burn duration.

Engine combustion testing was performed with an open beam path laser ignition system in a single-cylinder engine fueled by natural gas. In particular, engine knock and misfire maps were developed for both conventional spark plug and laser spark ignition. To further understand combustion related phenomena associated with laser spark ignition, a series of engine tests with varying timing and air/fuel ratio were also conducted. The following conclusions may be SOC, at equal spark timing, over the conventional spark plug system. The engine knock limit exhibits a slight decrease due to laser ignition. This is probably due to small differences in combustion phasing and remaining differences in SOC as ignition delay was significantly shorter in the laser spark system.
Burn duration was slightly longer for laser spark combustion. The resultant phasing differences are likely manifested in the slight decrease indicated in the brake thermal efficiency values for laser ignition.

Table 1 provides the definitions and associated parameters for abbreviations or acronyms used within this manuscript.

Table 1: Definitions, Acronyms and Abbreviations

Ma, J.X., Ryan, T.W., Buckingham, J.P.,
“Nd:YAG Laser Ignition of Natural Gas”.
Schmieder, R.W.,
“Laser Spark Ignition and Extinction of a Methane-Air Diffusion Flame,”.
Ma, J.X., Alexander, D.R., Poulain, D.E.,
“Laser Spark Ignition and Combustion Characteristics of Methane-Air Mixtures,”
Combustion and Flame.
Weinberg, F.J. and Wilson, J.R.,
“A Preliminary Investigation of the Use of Focused Laser Beams for Minimum Ignition
Energy Studies,” Proc. Roy. Soc.
Tran, P.X., “Laser Spark Ignition: Experimental Determination of Laser-Induced
Thresholds of Combustion Gases,” Optics Communications .
Ronney, P.D., “Laser verses conventional ignition of flames,” Optical Engineering,
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:blush:can u provide ppt's on this topic or any other topicsHeartHeartHeartHeart
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we don't have ppt on this topic. but have so many ppts on other topics. which topic you want ?
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hey that word document is password protected..i cant open that..
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hey dude it is a password protected doc.. so plz upload a new doc free with such issues...Angry
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if i download the laser ignition it is asking for some password?y is that password protected? n can i able to get the password?
i too facing the same problem..
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to get information about the topic Laser Ignition System full report ppt and related topic refer the link bellow
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Laser Ignition

.docx  Laser ignition.docx (Size: 1.04 MB / Downloads: 69)


There have been series of advancements in the field of automobiles. Modern science and technology have contributed to this fact. One such advancement is the usage of laser for the combustion process in the combustion chamber. ”Laser ignition” is an emerging technology, still under development, has a promising future.
With the advent of lasers in the 1960s, researchers and engineers discovered a new and powerful tool to investigate natural phenomena and improve technologically critical processes. Nowadays, applications of different lasers span quite broadly from diagnostics tools in science and engineering to biological and medical uses. In this seminar basic principles and applications of lasers for ignition of fuels are concisely reviewed from the engineering perspective. The objective is to present the current state of the relevant knowledge on fuel ignition and discuss select applications, advantages and disadvantages, in the context of combustion of engines. Fundamentally, there are four different ways in which laser light can interact with a combustible mixture to initiate an ignition event. They are referred to as thermal initiation, non-resonant breakdown, resonant breakdown, and photochemical ignition.

By far the most commonly used technique is the non-resonant initiation of combustion primarily because of its freedom in selecting the laser wavelength and ease of implementation. Recent progress in the area of high power fiber optics allowed convenient shielding and transmission of the laser light to the combustion chamber. However, issues related to immediate interfacing between the light and the chamber such as selection of appropriate window material and its possible fouling during the operation, shaping of the laser focus volume, and selection of spatially optimum ignition point remain amongst the important engineering design challenges. One of the potential advantages of the lasers lies in its flexibility to change the ignition location. Also, multiple ignition points can be achieved rather comfortably as compared to conventional electric ignition systems using spark plugs.
Although the cost and packaging complexities of the laser ignition systems have dramatically reduced to an affordable level for many applications, they are still prohibitive for important and high-volume applications such as automotive engines. However, their penetration in some niche markets, such as large stationary power plants and military applications, are imminent. Lasers a type of nonconventional ignition sources can contribute to a future performance optimization.



Combustion is defined as the burning of a fuel and oxidant to produce heat or work. Combustion includes thermal, hydrodynamic, and chemical processes. It starts with the mixing of fuel and oxidant, and sometimes in the presence of other species or catalysts. The fuel can be gaseous, liquid, or solid and the mixture may be ignited with a heat source. When ignited, chemical reactions of fuel and oxidant take place and the heat release from the reaction creates a self-sustained process. The combustion products include heat, light, chemical species, pollutants, mechanical work and plasma. Sometimes, a low-grade fuel, e.g., coal, biomass, or coke, can be partially burned to produce higher-grade fuel, e.g., methane. The partial burning process is called gasification. Various combustion systems, e.g., furnaces, combustors, boilers, reactors, and engines, are developed to utilize combustion heat, chemical species, and work.


Knock is the most important abnormal combustion phenomenon. It important because it puts a limit on the compression ratio at which an engine can be operated, which in turn controls the efficiency and to some extent the power output. It got the name “knock” because of the noise that results from the auto ignition of a portion of fuel air mixture ahead of the advancing flame. As the spark is ignited there is a formation of flame front and it starts propagating. As the flame propagates across the combustion chamber, speed of flame front is about 15 to 30 m/s ; the unburned charge ahead of the flame called the “end gas” is compressed, raising its pressure, temperature and density. In case of abnormal combustion the end gas fuel air mixture undergo fast chemical reactions, which results in auto ignition prior to normal combustion (i.e. the flame front reaching it). During auto ignition a large portion of end gas releases its chemical energy rapidly and spontaneously at a rate 5 to 25 times as in case of normal combustion. This spontaneous ignition of the end gas raises the pressure very rapidly and causes high frequency oscillations inside the cylinder resulting in a high pitched metallic noise characterized as knock. During this knocking phenomenon pressure waves of very large amplitudes propagate across the combustion chamber and very high local pressures are produced which are as high as 150 to 200 bars. Local 5% of the total charge is sufficient to produce a very violent serve knock. The velocity reached during knock is of the order of 300 to 1000 m/s.
Basically knock depends on the outcome of shorter of two different process they are:
• The advancing flame front grabbing all the fuel air mixture.

• The pre combustion reaction in the unburned end gas. The time taken in this preparative phase of auto ignition (i.e. pre combustion reaction) is called “ignition delay”. Knock will not occur if the ignition delay is so long that the flame front consumes all the end gas and auto ignition takes place i.e. normal combustion occurs. Knock will occur if the pre-combustion reaction produce auto ignition before the flame front arrives. Auto ignition when occurs repeatedly, the phenomenon is called “Spark Knock" .Spark knock is controllable by spark advance advancing the spark increases the knock intensity and retarding the spark decreases the knock.


The auto ignition temperature or kindling point of a substance is the lowest temperature at which it will spontaneously ignite in a normal atmosphere without an external source of ignition, such as a flame or spark. This temperature is required to supply the activation energy needed for combustion. The temperature at which chemical will ignite decreases as the pressure increases or oxygen concentration increases. It is usually applied to a combustible fuel mixture.

Spontaneous combustion or self-ignition is a type of combustion which occurs without an external ignition source. Spontaneous combustion is a term used to describe how something just ignited (spontaneously) but in fact spontaneous combustion is more than usually, a slow process that can take several hours of decomposition / oxidization with heat build up to a point of ignition.
The reasons for self-ignition:
• A substance with a relatively low ignition temperature begins to release heat, which may occur in several ways, such as oxidation or fermentation.
• The heat is unable to escape, and the temperature of the material rises.
• The temperature of the material rises above its ignition point
• Combustion begins if a sufficiently strong oxidizer, such as oxygen, is present.


Pre-ignition is the phenomenon of surface ignition before the passage of spark. The usual cause is an overheated spot, which by occur at spark plugs, combustion chamber deposits, or exhaust valves. Mostly it is due to spark plug. Exhaust valve usually run hot and sometimes when there is increase in heat load for these valves there will be an increase in the temperature and may cause pre ignition. Heat transfer principles indicate that the surface of the deposits is hotter than the metal surface to which the deposits are attached. Hence, sufficient deposits result in hot enough surfaces to cause pre ignition.
Pre-ignition is potentially the most damaging surface ignition phenomenon. The effect of pre-ignition is same as very advanced ignition timing. Any process that advances the start of combustion that gives maximum torque will cause higher heat rejection because of the increased burned gas pressures and temperatures (due to the negative work done during the compression stroke). Higher heat rejection causes higher temperature components thus the pre ignition damage is largely thermal which is evidenced by the fusion of spark plugs, piston and destruction of piston rings.


A process where a mixture, which would not ignite by itself, is ignited locally by an ignition source (i.e. electric spark plug, pulsed laser, microwave ignition source) is called induced ignition. In induced ignition, energy is deposited, leading to a temperature rise in a small volume of the mixture, where auto ignition takes place or the energy is used for the generation of radicals. In both cases a subsequent flame propagation occurs and sets the mixture on fire.


Diffraction refers to various phenomena which occur when a wave encounters an obstacle. It is described as the apparent bending of waves around small obstacles and the spreading out of waves past small openings. Similar effects are observed when light waves travel through a medium with a varying refractive index or a sound wave through one with varying acoustic impedance. Diffraction occurs with all waves, including sound waves, water waves, and electromagnetic waves such as visible light, x-rays and radio waves. As physical objects have wave-like properties (at the atomic level), diffraction also occurs with matter and can be studied according to the principles of quantum mechanics.


The ignition system must provide an adequate voltage to initiate a discharge across the spark plug electrodes and supply sufficient energy to ignite the air-fuel mixture. This must occur for all the engines operating conditions and at appropriate time on the compression stroke.
On the modern engines, it is normal for the ignition system to form a subsection of an integrated management system, sharing sensors and circuits, with fuelling and transmission control system.
However the ignition system does the following functions:

• When the compression ratio is lower and self-ignition temperature is quite high, an external source of ignition must be given.
• This takes place close to the compression stroke.
• The function of the ignition system is to propagate the flame and should supply energy within a small volume.
• The ignition should occur in a time interval sufficiently short time to ensure that only a negligible amount of energy is lost other than to establish the flame.


A spark plug (also, very rarely nowadays, in British English: a sparking plug), is an electrical device that fits into the cylinder head of some internal combustion engines and ignites compressed fuels such as aerosol gasoline, ethanol, and liquefied petroleum gas by means of an electric spark. Spark plugs have an insulated central electrode which is connected by a heavily insulated wire to an ignition coil or magneto circuit on the outside, forming, with a grounded terminal on the base of the plug, a spark gap inside the cylinder. A spark plug is composed of a shell, insulator and the central conductor. It pierces the wall of the combustion chamber and therefore must also seal the combustion chamber against high pressures and temperatures without deteriorating, over long periods of time and extended use.
The plug is connected to the high voltage generated by an ignition coil or magneto. As the electrons flow from the coil, a voltage difference develops between the central electrode and side electrode. No current can flow because the fuel and air in the gap is an insulator, but as the voltage rises further, it begins to change the structure of the gases between the electrodes. Once the voltage exceeds the dielectric strength of the gases, the gases become ionized. The ionized gas becomes a conductor and allows electrons to flow across the gap. Spark plugs usually require voltage of 12,000–25,000 volts or more to 'fire' properly, although it can go up to 45,000 volts. They supply higher current during the discharge process resulting in a hotter and longer-duration spark.
As the current of electrons surges across the gap, it raises the temperature of the spark channel to 60,000 K. The intense heat in the spark channel causes the ionized gas to expand very quickly, like a small explosion. This is the "click" heard when observing a spark, similar to lightning and thunder.
The heat and pressure force the gases to react with each other, and at the end of the spark event there should be a small ball of fire in the spark gap as the gases burn on their own. The size of this fireball or kernel depends on the exact composition of the mixture between the electrodes and the level of combustion chamber turbulence at the time of the spark. A small kernel will make the engine run as though the ignition timing was retarded and a large one as though the timing was advanced.


• Lean mixture causes the increase in demand for the ignition energy.
When the air-fuel ratio is very high (that means the content of fuel in that mixture is very less), for the combustion process to take place, the mixture demands more energy.
• This leads to the erosion of the spark plug and thus reduced reliability and lifetime of the spark plug.
When the mixture demands more energy, the spark plug has to supply the required energy for the combustion to take place. This in turn causes the electrodes to wear off, otherwise called as erosion of the spark plug.
• The electrodes of the spark plug should be located near the combustion wall to avoid disturbance of the precisely designed flow
The spark plug has to be placed in correct position for its smooth working and to burn the mixture in much effective way.


Light Amplification by Stimulated Emission of Radiation (LASER or laser) is a mechanism for emitting electromagnetic radiation, often visible light, via the process of stimulated emission. The emitted laser light is (usually) a spatially coherent, narrow low-divergence beam,that can be manipulated with lenses. Laser light is generally a narrow-wavelength electromagnetic spectrum monochromatic light.
The laser used in this ignition is Nd:YAG (neodymium-doped yttrium aluminum garnet) laser of 1064 nm
Nd:YAG (neodymium-doped yttrium aluminum garnet; Nd:Y3Al5O12) is a crystal that is used as a lasing medium for solid-state lasers. The dopant, triply ionized neodymium, typically replaces yttrium in the crystal structure of the yttrium aluminum garnet (YAG), since they are of similar size. Generally the crystalline host is doped with around 1% neodymium by atomic percent.


• Since spark plugs are an integral part of the combustor liner, the ignition kernel is usually located in the suboptimal quench zone of the combustor.

• Lean mixtures along the liner increase the demand on ignition energy, leading to an increased erosion of the spark plug electrodes, and thus to a reduced reliability and lifetime of the igniter. Since spark plug ignition shows a reduced ignitability of lean mixtures below an equivalence ratio of 0.6
• Laser ignition is a possible candidate to solve some of problems because it allows uncoupling of the limiting link between the location of the ignition source and the ignition kernel.

• Lasers are able to ignite the mixture at the best thermodynamic and aerodynamic conditions from almost any installation location. Therefore laser ignition is more independent from variations of the local equivalence ratio than other ignition concepts.

• It is known that lasers are able to ignite leaner mixtures compared with spark plug ignition because there are no electrodes surrounding the initial flame kernel, which, in the case of the spark plug, cool down the kernel and prevent it from evolving further into the combustion chamber.


• Thermal breakdown
• Non-resonant breakdown
• Resonant breakdown
• Photochemical mechanisms


In the case of thermal interaction, ignition occurs without the generation of an electrical breakdown in the combustible medium. The ignition energy is absorbed by the gas mixture through vibrational or rotational modes of the molecules; therefore no well-localized ignition source exists. Instead, energy deposition occurs along the whole path in the gas. According to the characteristic transport times therein, it no necessary to deposit the needed ignition energy in a very short time. So this ignition can also be achieved using quasi continuous wave lasers.


It involves non-resonant multi-photon dissociation of a molecule followed by resonant photo ionization of an atom. As well as photochemical ignition, it requires highly energetic photons. Therefore, these two types of interaction do not appear to be relevant for this study and practical applications.
Post: #9
I want full report of this topic and also ppt, can you send this on my id- sanket2431[at]

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