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Figure 10 illustrates the theoretical results from the simplified model considered, together with the experimental data. These results and measurements are presented one next to the other, in order to facilitate the validity analysis of the proposed simulation methodology.
These results illustrate that the trends are comparable for both sets of data, that is, a similar range is obtained for all of the variables reported. A lower pressure is generated in chamber 5, which is attributed to the shorter length of this chamber. However, such increase in pressure does not correspond exactly to the difference of lengths, as the ratio of lengths would cause a differential pressure of 2.3/1.23 = 1.86, while the ratio of average pressures is on the order of 2. That is, there is an incremental, which is associated to the maximum height attained by the fluid in the chamber. The major difference between both sets of data, the experimental and theoretical, is that the theoretical do not include much of the noise and random oscillations reported in the experimental data. Such noise, however, is of very low amplitude, in comparison with the maximum values attained. The practical applications of these results could be in the area of chamber design, so that the effects of the length of the chambers be taken into account. That is, such greater lengths for the fluid in the chamber would involve larger pressures and consequently, greater stresses. However, the analysis should include an overall perspective, that is, the shortening of the chambers would imply an increase in the number of chambers, for a certain total payload, and the superposition effect of pressures, should be considered. On the other hand, the analysis could be extended to characterize the effects of the distribution of the lengths of the different chambers along the axis of the tanker, as the different resulting forces could have different effects on the pitch response of the road tanker.
A model of the cargo – ship interaction has been presented, for a navigation environment in which there is no waves, in which the ship lateral stability depends only on the manoeuver performed and the characteristics of the ship and cargo. Several simplifications have been introduced in the model, including the circular bottom of the ship, which facilitates the location of the buoyancy force on the ship, and the analogy of the sloshing cargo motion to a simple pendulum. Two forms of damping were introduced (river waters with the ship´s hull and the friction of the liquid inside the tanker walls), while the sliding motion of the ship when turning has been assumed as negligible. The results suggest that the sloshing cargo influences the lateral stability of the river tanker, with increases in the maximum roll angle from 15% to 40%, as a function of the speed and the fill level. The maximum roll angle has been found to occur at a 75% fill level, regardless of the ship speed.
It was possible to achieve an error as 9% or even 0% at certain time steps, as shown in the graph above, the usage of UDF code has major importance in achieving the pressure Profile required, and it heat transfer between the bottle itself and the surroundings was taken into consideration which of course had a high influence on how the temperature of the air flask changes.
The results are based on data1. Figure 3 displays temperatures of the tank wall and of the gas phase over testing time. It can be seen that a complete coating strongly delayed the heating of tank wall and gas phase, whereas the partly coated tanks only had a minor influence on temperature development. There was no significant difference between a half coated and a thirdly coated tank measurable. Figure 4 shows the internal pressure of tanks over testing time. Only the fully coated tank enabled a low pressure over 90 min testing time. Hence, a complete coating is necessary to guarantee the fire safety of hazmat tanks and a partly coating is not sufficient.