This study investigates some of the basic aspects of conjugate, or coupled, heat transfer problems. The ultimate interest is in the improvement of an existing computational fluid dynamics (CFD) code by the inclusion of such a coupling capability. Many CFD codes in the past have treated the thermal boundary conditions of a bounding solid as the simple cases of either a surface across which there is no heat flux, or as a surface along which the temperature is a constant with respect to both space and time. These conditions are acceptable for some applications, but many real-world problems require a more-realistic treatment of the thermal wall condition. A thermal coupling may be accomplished by maintaining a continuous heat flux and temperature across the fluid-solid boundary. A heat flux is calculated on the fluid-side of the interface, and this is used as a boundary condition for a heat-conduction solver to calculate the temperature field within the solid and return an interface temperature to the fluid. This process is executed for each time-step iteration of the code, and, therefore, the temperature field of the solid and the fluid-solid interface temperature are allowed to evolve with time and space. A new heat-conduction solver is developed and coupled with an existing flow solver. For this reason, some of the study is devoted to the testing of the accuracy of the new heat-conduction solver on simple problems for which there exist analytical solutions. Additional coverage is devoted to the possibility of thermal communication between solid grid blocks. This is due to the fact that multiple grid blocking of the solid may be required for more complex geometries. For such cases, a similar procedure as that described for the fluid-solid interface is used to accomplish the solid-solid block-to-block communication. Relatively simple test cases of fluid-solid and solid-solid coupling are conducted; these cases are limited to two-dimensional grids. Other limitations include: the assumption of constant thermophysical properties for the solid, no consideration for thermal expansion of the solid, and no consideration for the radiation mode of heat transfer. The results indicate that the heat-conduction/flow solver shows potential.

This thesis presents a model for predicting the forced convective critical heat flux (CHF) for water over a wide range of thermal-hydraulic conditions which might be encountered during normal and accident operations of a light water nuclear reactor. The model is primarily composed from existing steady-state CHF correlations for tubes or tube and rod bundle geometries, and encompasses the following parametric ranges: 0.3 ≤ P (MPa) ≤ 16.0 6.0 ≤ D (mm) ≤ 30.0 100.0 ≤ G (kg/m2s) ≤ 8000.0 -0.30 ≤ X ≤ 1.0 The correlations used as the foundation of this model are the 1) Westinghouse-3 2) Biasi correlation, and the 3) Modified Barnett correlation The mode 1 presented is comp a red with available data, and the resultant model is illustrated as a 3-D surface in mass flux, quality, and CHF space to represent general CHF behavior.

New demands and tighter government legislations on greenhouse gases and pollutants, especially for those produced by diesel engines, there has been much focus on developing more efficient diesel engine designs and pollution control devices. There are several pollution control devices currently being implemented in diesel engines such as, diesel particulate filters, selective reduction catalyst, electrostatic filters, exhaust gas recirculation systems, etc. Diesel particulate matter is of particular importance especially when deposited because of its corrosive and thermal insulating nature. There are many complex mechanisms involved in fine particle deposition. This study will focus on the main deposition mechanisms such as convection, diffusion, thermophoresis and electric field effects. The objective of this study was to evaluate experimentally the mechanisms of diesel soot deposition in a rectangular (RWCS) and cylindrical (CWCS) wall cooled sections to evaluate thermophoretic effects. In additional, the coaxial cylindrical wall cooled section with additional with coaxial wire electrode was used to study applied electric field effect (CCWCSE) on soot deposition. A non-destructive Real-Time Neutron Radiography technique was used to evaluate the soot deposition thickness profiles inside the cooled sections. The experiments were conducted using diesel engine exhaust from a single cylinder diesel engine operated at fixed 2.4kW, at a exhaust gas mass flow rate of 20 kg/hr with exposure times ranging 0 to 3hrs, coolant temperatures from 20 to 40°C and exhaust gas temperatures from 250 and 270°C. The resulting Reynolds Number based on the mass flow rate per cross-sectional area times the hydraulic diameter was 6300 for the RWCS and 9000 for the CWCS and CCWCSE. The results show that for the RWCS, the soot deposition pattern qualitatively matched the cooling water channel outer wall surface temperature profile along with thicker deposition at the entrance region due to convection effects. For the ewes, the deposition was more uniformly distributed throughout the device. It was observed for both devices that as the mean soot deposition thickness increases with increasing exhaust gas exposure time and decreasing wall cooling temperature. Finally the experimental results for the CCWCSE shows that the soot deposition was enhanced by a positive or negative applied electric field. / Thesis / Master of Applied Science (MASc)

No description available.

No description available.

ASPECT is a new convection code that uses more modern and advanced solver methods than geodynamics legacy codes. I use ASPECT to calculate 2-dimensional Cartesian as well as 2- and 3-dimensional spherical-shell convection cases. All cases use the Boussinesq approximation. The 2D cases come from Blankenbach et al. (1989), van Keken et al. (1997), and Davies et al. (in preparation). Results for 2D cases agree well with their respective benchmark papers. The time-evolutions of the root mean square velocity (Vrms) and Nusselt number agree, often to within 1%. The 3D cases come from Zhong et al. (2008). Modifications were made to the simple.cc and harmonic_perturbation.cc files in the ASPECT code in order to reproduce the initial conditions and temperature-dependence of the rheology used in the benchmark. Cases are compared using both CitcomS and ASPECT with different levels of grid spacing, as well as comparing uniform grid spacing and the ASPECT default grid spacing, which refines toward the center. Results for Vrms, average temperature, and Nusselt numbers at the top and bottom of the shell range from better than 1% agreement between CitcomS and ASPECT for cases with tetragonal planforms and 7000 Rayleigh number to as much as 44% difference for cases with cubic planforms and 10^5 Rayleigh number. For all benchmarks, the top Nusselt number from ASPECT is farthest from the reported benchmark values. The 3D planform and radially averaged quantity plots agree. I present these results, as well as recommendations and possible fixes for discrepancies in the results, specifically in the Nusselt numbers, Vrms, and average temperature. / Master of Science

Glioblastoma multiforme (GBM) is the most common malignant brain tumor in adults and has a median survival of 13.4 months. Convection enhanced delivery (CED) has shown promise for the treatment of GBM by allowing intratumoral delivery of therapeutics, bypassing the blood brain barrier. A fiberoptic microneedle device (FMD) CED catheter enables simultaneous delivery of laser energy and therapeutic. The laser allows for heating of tissue in the region of infusion, called thermotherapy. Thermotherapy offers the advantages of increasing the volume of distribution (Vd) of the infusate, as well as facilitating intracellular penetration of the therapeutic. We hypothesize that heating of brain tissue will increase infusate Vd in ex vivo CED brain infusions. Methods: Formalin fixed mouse brains were infused by FMD-CED with Evans blue for 1 hour at 0.1 μl/min, at 22°C, 37°C and 42°C (n=4 brains/group). The Vd was determined and compared using one-way ANOVA. Results: FMD-CED performed at 42°C resulted in significantly higher mean Vd (4.90+2.2mm3; p =0.03) than those at 22°C (1.49+0.4 mm3), although no differences in Vd were observed between the other temperature groups. 42°C brains demonstrated interstitial and intracellular distribution, while rare intracellular distribution was noted in the other groups. Discussion: The Vd of FMD-CED infusions is facilitated by sub-lethal thermotherapy. This study indicates that thermotherapeutic enhancement of infusate Vd does not occur exclusively via vascular mechanisms. Thermotherapy facilitates advective-diffusion by decreasing interstitial fluid pressure and increasing transcellular fluid transport. These results were validated in a companion in vivo FMD-CED study in the rodent brain. / Master of Science

No description available.

Cooling of electronic components is one of the most important issues concerned in the electronic industry for design of equipment. Maintaining the temperature of an electronic device within its safe operating temperature limits is essential to operate the equipment safely with proper functionality. According to the Arrhenious law of failure rate, for a device with activation energy 0.65eV, every 10°C increase in temperature doubles the failure rate. Recent miniaturisation of components and high device heat dissipation rates lead to high heat fluxes, which cause temperature rise. Hence, there is an increasing need for research to achieve high heat removal rates and optimal design. Several cooling techniques are used for cooling of electronics based on the application and cooling rate requirements. Air-cooling of electronics has a wide range of applications due to its greater reliability, simplicity, easy maintenance, low cost, easy availability of coolant (air), and light weight. Air-cooling is also free from boiling and dripping problems. Air-cooling is used in applications such as avionics, cooling of personal computers, cooling of data centers, and in automobile electronics. In a typical electronic cooling application, cooling fluid is driven by the combination of external pressure forces and buoyancy forces. Based on the relative contribution of these forces towards the total driving force, the cooling techniques can be categorized as forced, natural or mixed convection cooling. However, in many of the electronic cooling situations, such as in the applications with very high heat fluxes, tall Printed Circuits Boards (PCBs) with low forced convection velocity, and in large scale applications such as data centers, the contributions of the buoyancy forces and external pressure forces for the total driving force are comparable, which results in a mixed convection situation. In the present study, mixed convection in vertical channels heated with five heating configurations, which represent typical electronic cooling applications, is studied numerically. The five different heating configurations are channels with flush-mounted continuous heater, flush-mounted strip heaters, flush-mounted square block heaters, protruding rib heaters and protruding square heaters. The first three configurations are categorised as flush-mounted heating configurations and the latter two configurations are categorised as protruded heating configurations. One of the channel walls represents the substrate on which the heaters are mounted and the heat sources represent the heat generating electronic components. Heat transfer under steady state conditions is considered in the study. The study includes laminar as well as turbulent heat transfer. For a systematic study of mixed convection, an analytical or semi-analytical formulation is desirable for a simplified model, as it can highlight the effect of relevant non-dimensional parameters on the heat transfer characteristics of a system. The results of a simplified model can be used for benchmarking the results of practical situations. Hence, before numerically solving the governing equations for mixed convection in channels, mixed convection boundary layer flows over a heated vertical plate is considered for study. Perturbation technique is used to solve the boundary layer equations with non-isothermal boundary conditions. The perturbation analysis is carried out for an arbitrarily variation of wall temperature or heat flux. Subsequently, the results are extended to find heat transfer rates in the cases of power-law variation of temperature and heat flux, as special cases. It is always required to design a cooling system to remove maximum possible amount of heat, keeping the device temperature within its safe operating limits. Hence, optimization of heat transfer in boundary layers is attempted, whose results can be used as guidelines to achieve optimal heat transfer in practical situations of channels with continuous as well as discrete heating. Similarity analysis is used for the optimization of heat distribution in boundary layer flows. In the similarity analysis, in the search of optimal heat transfer from the plate, the boundary layer equations are solved for various power-law heat flux variations and the appropriate power-law variation of optimal heat transfer is found. Similarly, the heat flux variation for optimal heat transfer is found for the cases of natural and forced convection, as they are the limiting cases of mixed convection. In the numerical part of the study, the generalised three-dimensional governing equations for the five heating configurations considered for the study are solved numerically with appropriate boundary conditions. Separation of natural, forced and mixed convection regimes is carried out in all the heating configurations using a criterion based on individual contributions of pressure force and buoyancy force towards the total driving force for the fluid movement. Heat transfer characteristics are studied in laminar as well as turbulent regimes in terms of parameters such as Grashof number, Reynolds number, Nusselt number, maximum temperature of heaters, pressure drop across the channel, and so on. The influence of conjugate effects on the heat transfer characteristics is studied by varying the substrate thermal conductivity. A systematic comparison of various effects such as the effect of discrete heating in plain channels, effect of discrete heating in channels with heated ribs, and the effect of three-dimensional protrusions on heat transfer, is achieved. The parameters in the individual configurations, which affect heat transfer, are explored for better cooling solutions. Optimal heat distribution among the heaters to minimise the temperature of the hottest heater for a given total amount of heat generation in the channel is found for all the channel configurations, which are heated either continuously or discretely. In the process of finding the optimal heat distribution among heaters, guidelines are taken from the optimal heat distribution in boundary layer flows. Compared to usual optimization approaches such as genetic algorithm, the present physics based optimisation procedure requires fewer runs to arrive at the optimal distribution. The fluid flow characteristics in all the three configurations with flush-mounted heaters are found to be similar. However, heat transfer characteristics in channels with flush-mounted square heaters differ from those in the other two flush-mounted channel configurations. Hot spots with higher temperatures are found at heater locations in channels with flush-mounted square heaters. The effect of substrate follows the same trend in all the flush-mounted configurations. At lower thermal conductivities, the maximum temperature decreases sharply with increasing thermal conductivity. However, at higher conductivities, the influence reduces. In all the flush-mounted configurations, heat transfer will not be influenced by substrate thermal conductivity increment at conductivities more than 150 times the fluid thermal conductivity. The fluid flow and heat transfer characteristics in channels with protruded heaters differ significantly from those in channels with flush-mounted heaters. The protrusions in the channels interact with the fluid flow and make it different from that of smooth channels. In turn, the protrusions affect heat transfer characteristics in the channels. The influence of the protrusions on the heat transfer and locations of hot spots in the domain is examined. Effect of thermal conductivity in channels with protruded square heaters is similar to that in channels with flush-mounted heaters. However, conductivity in channels with protruded rib heaters affects the heat transfer in a wider range of conductivities than in the other heating configurations. Unlike in the other configurations, at low thermal conductivities, maximum temperature does not drop sharply with increase of conductivity. In channels with protruded square heaters, staggering arrangement of heaters results in higher heat transfer rates than those with in-line heater arrangement. In all the configurations, pressure drop is found to be independent of Grashof number in the range of heat dissipation rates considered in the study. Heat transfer rates in turbulent region are much higher than the heat transfer rates in laminar regime. However, the pressure drops encountered are also high in the turbulent regime. Turbulent heat transfer results in a more uniform temperature distribution in channels. The cooling performances of the individual configurations are compared. For a given pressure drop the cooling performances decreases in the order of flush-mounted strip heating, protruded square heating, flush-mounted square heating, protruded rib heating. For a given inlet fluid flow rate, the cooling performances decreases in the order of protruded rib heating, protruded square heating, flush-mounted square heating, flush-mounted strip heating. However, for a given inlet fluid flow rate, the pressure drop increases in the order of increasing cooling performance.

The problem of laminar and turbulent conjugate mixed convection flow and heat transfer in shallow enclosures with a series of block-like heat generating components is studied numerically for a Reynolds number range of zero (pure natural convection) to typically 106, Grashof number range of zero (pure forced convection) to 1015 and various block-to-fluid thermal conductivity ratios, with air as the working medium. The shallow enclosure has modules consisting of heat generating elements, air admission and exhaust slots. Two problems are considered. In the first problem, the enclosure has free boundaries between the modules and in the second problem, there are partitioning walls between the different modules. The flow and temperature distributions are taken to be two-dimensional. Regions with the same velocity and temperature distributions can be identified assuming repeated placement of the blocks and fluid entry and exit openings at regular distances, neglecting end wall effects. One half of such rectangular region is chosen as the computational domain taking into account the symmetry about the vertical centreline. On the basis of the assumption that mixed convection flow is a superposition of forced convection flow with finite pressure drop and a natural convection flow with negligible pressure drop, the individual flow components are delineated. The Reynolds number is based on forced convection velocity, which can be determined in practice from the fan characteristics. This is believed to be more meaningful unlike the frequently used total velocity based Reynolds number, which does not vanish even in pure natural convection and which makes the fan selection difficult. Present analysis uses three models of turbulence, namely, standard k-ε (referred to as Model-1), low Reynolds number k-ε (referred to as Model-2) and an SGS kinetic energy based one equation model (referred to as Model-3). Results are obtained for aiding and opposing mixed convection, considering also the pure natural and pure forced convection limiting cases. The results show that higher Reynolds numbers tend to create a recirculation region of increasing strength at the core region and that the ranges of Reynolds number beyond which the effect of buoyancy becomes insignificant are identified. For instance, in laminar aiding mixed convection, the buoyancy effects become insignificant beyond a Reynolds number of 500. Results are presented for a number of quantities of interest such as the flow and temperature distributions, local and average Nusselt numbers and the maximum dimensionless temperature in the block. Correlations are constructed from the computed results for the maximum dimensionless temperature, pressure drop across the enclosure and the Nusselt numbers.