<p>There are two main ways of measuring particle emission from wood combustion. Firstly, particles can be sampled directly in the chimney. Secondly, a dilution tunnel can be used, thus cooling the flue gases parallel to diluting. The purpose of this work is to investigate the differences between both measurements and establish which is the best method to measure particle emission from wood combustion. The approach is to perform particle emission measurements in the chimney and in a dilution tunnel simultaneously during the combustion of wood in a small-scale appliance. Moreover, Flame Ionization Analysis will be carried out to understand the contribution of condensed organic compounds to the total particulate matter emission. The particle emission measured in the dilution tunnel was between 5 and 12 times higher than in the chimney. The more unfavourable combustion conditions, the larger the difference between both measurements was seen. The results also show a factor of about 2,5 between both particle emission measured in the stack and Total Hydrocarbon content in the flue gas and particle emission measured in the dilution tunnel, indicating that about 35 % of the hydrocarbons measured in the stack with the Flame Ionization Detector condense along the dilution tunnel accounting for approximately 85 % of the total particle emission found at this location.</p>

<p>The cross-flow turbine is unique due to the generation of power during two stages. The water flows through the rectangular cross-section nozzle and enters the runner, where the first stage power is generated. The water then flows diametrically through the center of the runner, before it hits the blades on the way out, generating the second stage power. This type of turbine is often used in small hydropower plants located in less-developed countries. The turbine has a simple design, which is economical and easy to manufacture. A cross-flow turbine manufactured by Remote HydroLight in Afghanistan was installed in The Waterpower Laboratory at The Norwegian University of Science and Technology in September 2008. During the fall of 2008, efficiency measurements were performed on the turbine. A maximum efficiency of 78.6% was obtained at 5 meter head. However, although the efficiency is high for a turbine with such a simple design, there is a desire to improve it for better utilization of the resources. An open question is if the flow through the runner behaves like the manufacturers of this turbine type claim. It is therefore of interest to investigate the flow pattern through the runner and the distribution of torque transferred during the two stages. This is the objective of this thesis. Two experiments are performed in this thesis. The objective of the first experiment was to visualize the flow through the runner with use of a high-speed camera. This required an extensive remodeling of the turbine in order to obtain a clear view of the flow. However, the high--speed camera had to be replaced by a single-lens reflex camera and stroboscopes, due to low quality pictures. The second experiment measured the torque transfer to the runner by the use of strain gages. The strain gages could not be calibrated within the time frame of this thesis, but a relative measure of the distribution of torque was obtained. During both experiments the efficiency was measured, but the main objective was to determine the flow pattern and torque transfer through the runner. The results show that the turbine works well for large nozzle openings. The water enters the runner close to the nozzle outlet, leading to a cross flow entering the inside of the runner at a short distance from the nozzle. This gives good conditions for the flow, as the direction of the absolute velocity when entering the second stage corresponds well with the blade inlet angle. At best efficiency point the second stage contributes to 53.7% of the total amount of torque transferred. With decreasing nozzle opening, the cross flow enters the inside of the runner further away from the nozzle. This give a direction of the cross flow which corresponds poorly with the inlet angle of the blades at the second stage, which increases the incidence losses and gives a lower efficiency.</p>

Abstract Motivation There is, at the present time, no submerged molasses pump on the market that is designed specifically for cargo tankers. Due to this I, find it interesting to look into the possibilities of installing a molasses pump in cargo tankers to transport molasses instead of transporting molasses in containers as it is done today. It is challenging to come up with a new product, and the motivation of actual be able to release a pump for the international marked is indescribable. Problem The goal is to make a prototype of a submerged pump specifically made for pumping molasses that can fulfill the customer requirements for flow and pressure. Obtaining reliable test result and demonstration of the pump is desirable before the new product is set into production. Approach Molasses is a very special and complex cargo, due to the complexity, 8cdot10^{3}kg of molasses was ordered from Australia. Then it was possible to do several tests on the actual molasses which the current market is for. Different pump designs have to be evaluated and then some design can be put into prototyping. The prototypes needs to go through several test so as much knowledge as possible can be gained before the pump is released on the market. Conclusion There is definitely a large market for transporting molasses by cargo tankers. There are already several orders for a molasses pumping system. Molasses seems to be a more complicated cargo pump then first assumed because of its big variations in viscosity due to temperature and different batches. There are many unknown factors involved in pumping molasses and as further it was dogged in to the problems new ones occurred. But the problems have been solved, some has been hard to solve. After three prototypes the customers requirements were finally achieved, and then all the hard work has finally given result. Even if the pump design is ready for the first order, many new question have arrived and this is the motivation to continue with the process that has already started. Especially interesting is the new technology that will be available next year regarding CFX a motivation factor to keep trying to rise the efficiency.

Kirne Power Plant is a planned expansion of Khimti I Hydro Power Plant in Nepal. During the monsoon period there is a lot of excess water, and the the plan is to utilize this water in an extra power plant during the monsoon. The same tunnel as for Khimti I is to be used for the whole volume flow. A new external pressure shaft is planned for the water down to the new power house of Kirne. The hydrology is studied in this thesis, and a flow of 11 m3/s can be utilized in Kirne through 80% of the monsoon, through the rest of the period, the flow is lower, on the average. The flow limit is found based on the head loss and surges in the water way. The sediment basin will have to be doubled in size to handle the doubling of the volume flow. The placing of the basin can be on the opposite riverbank of the existing settling basin. Another possibility is to build the planned power plant Khimti II upstream Khimti I, and handle the sediments there. Excavation of a volume of 170 m3 is necessary at the top of the surge shaft, to give room for the upsurges. The down-surges are reduced by prolonging the opening time of the turbines and valves. The new pressure shaft will be a 1800 meter long external shaft of steel, with an optimal pipe diameter of 2,16 meter. The shaft will be external due to difficult conditions in the rock, and experiences of the building of Khimti I. It will be shown that the best solution for Kirne is to install one Pelton turbine wiht five nozzles, or two Pelton turbines with three nozzles each, in the power plant. Two Pelton turbines will give a better production than one, but at the same time the costs of the power house, and the turbines will increase. The size of the turbine will be 64 MW for one turbine, and 32 MW each, if two smaller turbines are chosen. The production will be about 240 GWh depending of the flow through the year, which can be up to 30% less than the average. The income of Kirne will be about 13-14 MUSD, depending on the final choices. In order to finish this thesis, a lot of assumptions are made. The power evacuation and agreements with locals and national governments are not investigated. This is done to narrow the scope of the thesis, but at these points, the largest risks of the project are placed.

Abstract This dissertation has been produced during the spring semester of 2008 to serve to the requirements for the degree of “Master of Technology” at the Norwegian University of Science and Technology (NTNU). The thesis has been written at the department of Energy and Process Engineering, with supervision of Professor Helge I. Andersson from the Fluid Dynamics department. The thesis has the title “Computation of Impinging Gas Jets”, and aims to investigate the Impinging Jet Flow (IJF) problem presented in section[2] by means of Computational Fluid Dynamics (CFD). For the work of this thesis the commercially available program package of FLUENT 6.3, and Gambit 2.4 was used for all the simulation and geometry generation tasks. The specific IJF case treated in the thesis work, is the Single Round Nozzle (SRN ) IJF geometry explained in section[2.2] , and displayed in Figure 2.2 . The numerical simulations were carried out by means of 2D and 3D Reynolds Averaged Navier Stokes ( RANS) simulations , and Large Eddy Simulation (LES) with related theory described in the theory section[3]. The work with the simulations of this thesis can roughly be divided into two main components. Firstly there is the part comprising all tasks and operations involved in creating and running the simulations, about which relevant information is provided in section[4]. Secondly, there is the work involving all the tasks related to gathering, interpreting, and analyzing the yielded simulation results. These tasks and their results are mainly treated in sections[5 to 9]. Both numerical and experimental reference IJF cases were used in this thesis work. The reference cases were at first used to guide the beginning of the simulation effort (Figure 6.1). In the later stages of the thesis, the reference results were used to analyze and interpret the results of the thesis simulations. Overall the results from the RANS simulations of this thesis, are found to give good agreement with the reference simulations and experiments, within the limits of what can be expected from the RNG k-ε model which was used. The LES simulations on the other hand, proves to be far more demanding both computation wise, and in relation to issues concerning simulation preparations and setup. In addition the LES simulation is found to be outperformed by the RANS simulations in some regions of the IJF geometry. When analyzed, it is found that this is probably caused by an unfortunate combination of regions with low local mesh quality, and a quite mesh sensitive feature in the Sub Grid Scale model. Nevertheless the LES simulation is found to provide results of good agreement with experimental data in some of the most difficult regions to simulate on the IJF geometry. In this region the LES simulation is also found to outperform the RANS simulations.

There are two main ways of measuring particle emission from wood combustion. Firstly, particles can be sampled directly in the chimney. Secondly, a dilution tunnel can be used, thus cooling the flue gases parallel to diluting. The purpose of this work is to investigate the differences between both measurements and establish which is the best method to measure particle emission from wood combustion. The approach is to perform particle emission measurements in the chimney and in a dilution tunnel simultaneously during the combustion of wood in a small-scale appliance. Moreover, Flame Ionization Analysis will be carried out to understand the contribution of condensed organic compounds to the total particulate matter emission. The particle emission measured in the dilution tunnel was between 5 and 12 times higher than in the chimney. The more unfavourable combustion conditions, the larger the difference between both measurements was seen. The results also show a factor of about 2,5 between both particle emission measured in the stack and Total Hydrocarbon content in the flue gas and particle emission measured in the dilution tunnel, indicating that about 35 % of the hydrocarbons measured in the stack with the Flame Ionization Detector condense along the dilution tunnel accounting for approximately 85 % of the total particle emission found at this location.

A wind tunnel study of speed-up effects above the very crest of a sharp-edged escarpment and a hill peak in a simulated atmospheric boundary layer has been carried out. It was desired to do a part-deep simulation of an atmospheric boundary that could be found above sea or coastal area exposed to the open sea. Because of the limited work section length was it used a modified roughness, barrier and mixing-device developed by Counihan to accelerate the boundary layer growth. The mean velocity, integral length scales, power spectrum and turbulence intensity in the simulated boundary layer were compared with full scale empirical data. It showed good agreement except for the turbulence intensity which was too low. Speed-up effects for the mean horizontal velocity and the longitudinal turbulence intensity above the very crest of an escarpment and a hill peak were investigated in the simulated atmospheric boundary layer. From the results it was observed that the speed-up effect gave a decrease in the turbulence intensity and a more uniform profile with height. A considerably increase of the horizontal mean velocity in the lowest part of the flow was also observed. Scaled-up data from the wind tunnel experiment were compared with estimations from the Norwegian standard and potential flow with varying degree of agreement.

The cross-flow turbine is unique due to the generation of power during two stages. The water flows through the rectangular cross-section nozzle and enters the runner, where the first stage power is generated. The water then flows diametrically through the center of the runner, before it hits the blades on the way out, generating the second stage power. This type of turbine is often used in small hydropower plants located in less-developed countries. The turbine has a simple design, which is economical and easy to manufacture. A cross-flow turbine manufactured by Remote HydroLight in Afghanistan was installed in The Waterpower Laboratory at The Norwegian University of Science and Technology in September 2008. During the fall of 2008, efficiency measurements were performed on the turbine. A maximum efficiency of 78.6% was obtained at 5 meter head. However, although the efficiency is high for a turbine with such a simple design, there is a desire to improve it for better utilization of the resources. An open question is if the flow through the runner behaves like the manufacturers of this turbine type claim. It is therefore of interest to investigate the flow pattern through the runner and the distribution of torque transferred during the two stages. This is the objective of this thesis. Two experiments are performed in this thesis. The objective of the first experiment was to visualize the flow through the runner with use of a high-speed camera. This required an extensive remodeling of the turbine in order to obtain a clear view of the flow. However, the high--speed camera had to be replaced by a single-lens reflex camera and stroboscopes, due to low quality pictures. The second experiment measured the torque transfer to the runner by the use of strain gages. The strain gages could not be calibrated within the time frame of this thesis, but a relative measure of the distribution of torque was obtained. During both experiments the efficiency was measured, but the main objective was to determine the flow pattern and torque transfer through the runner. The results show that the turbine works well for large nozzle openings. The water enters the runner close to the nozzle outlet, leading to a cross flow entering the inside of the runner at a short distance from the nozzle. This gives good conditions for the flow, as the direction of the absolute velocity when entering the second stage corresponds well with the blade inlet angle. At best efficiency point the second stage contributes to 53.7% of the total amount of torque transferred. With decreasing nozzle opening, the cross flow enters the inside of the runner further away from the nozzle. This give a direction of the cross flow which corresponds poorly with the inlet angle of the blades at the second stage, which increases the incidence losses and gives a lower efficiency.

The fundamental principles of acoustics and of aeroacoustic noise generation are described, along with specific examples relevant for helicopter rotors. The acoustic analogy approach to computing the propagation of sound is presented, and details are given on the Ffowcs Williams-Hawkings (FW-H) equation. Using an incompressible, laminar Navier-Stokes solver in textsc{Fluent} the flow field around a circular cylinder and a NACA 0015 airfoil is computed. The solution of the flows are then used as the input for a simplified FW-H equation. The simulation results are validated by comparing both the flow parameters and the acoustic solution to numerical data from two different numerical studies. The validation leads to the conclusion that the method used is suitable for the both the flow and noise prediction. The pressure fluctuations are dominated by convected pressure fluctuations in the flow itself, not that radiated from the source. Due to this the FW-H method was not properly validated by the test cases, and no conclusions can be drawn as to its accuracy.

A wind tunnel study of speed-up effects above the very crest of a sharp-edged escarpment and a hill peak in a simulated atmospheric boundary layer has been carried out. It was desired to do a part-depth simulation of an atmospheric boundary that could be found above sea or coastal area exposed to the open sea. Because of the limited work section length it was used a modified roughness, barrier and mixing-device method developed by Counihan to accelerate the boundary layer growth. The mean velocity, integral length scales, power spectrum and turbulence intensity in the simulated boundary layer were compared with full scale empirical data. It showed good agreement except for the turbulence intensity which was too low. Speed-up effects for the mean horizontal velocity and the longitudinal turbulence intensity above the very crest of an escarpment and a hill peak were investigated in the simulated atmospheric boundary layer. From the results it was observed that the speed-up effect gave a decrease in the turbulence intensity and a more uniform profile with height. In addition, it was observed a considerably increase of the horizontal mean velocity in the lowest part of the atmospheric boundary layer. Scaled-up data from the wind tunnel experiment were compared with estimations from the Norwegian standard and potential flow with varying degree of agreement.