Fig. 14 Combustion Pressure

　

3.2 RESULTS FROM GAS TURBINE

The gas turbine that is used in this study is simple open-cycle system. So the gas turbine performance is varied with the atmospheric conditions such as pressure and temperature, and it is difficult to discuss the series of experimental results. In experiments, obtained results are modified according to the equations that estimate the standard atmospheric condition (Intake temperature : 15 ℃, pressure : 760mmHg). All results were compared and discussed with the modification above mentioned. ^(4,(5

Specific fuel consumption has a great difference with change in the mixing ratio of the rape-seed oil to diesel fuel oil. In cases of 15% (vol.) and 20% (vol.) blended fuel, fuel consumption becomes 15% worse compared to the cases 5% (vol.) and 10% (vol.) at the same load condition (70%). It is sown as Fig.15. The rape-seed oil consists of a taffy acid amide (oleic acid) and it needs longer period to achieve a complete combustion. It is assumed that higher amount of unburned fuel is exhausted in cases of larger mixing rate.

As shown in Fig. 16, measured thermal efficiency also follows the same tendency that is observed in the result of fuel consumption. Thermal efficiency of the cases of 15% (vol.) and 20% (vol.) blended fuel shows 10% lower value compared the cases with 5% (vol.) and 10% (vol.).

Figure 17 indicates the NO density in exhaust emissions with change in the mixing rate of rape-seed oil. The specific caloric heat of rape-seed is lower than the diesel fuel oil, so the flame temperature becomes lower in increase of mixing rate. Rape-seed oil (C₁₇H₃₃COOH) does not contain nitrogen, thus the fuel NO becomes lower with increase mixing rate.⁽²

　

Fig. 15 Fuel Consumption Curve

Fig. 16 Thermal Efficiency

Fig. 17 NO Density of Exhaust Gas

　

The increasing rate of NO is shown in Fig.18 and Fig.19. Here we mean the ratio of NO emission between the test condition and the pure diesel oil condition.

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