In a crowded building space with no air conditioning, heat and moisture emissions from occupants can result in heat stress in the indoor environment, which in turn, causes thermal strain on the human body. In the present paper, a 61-node thermoregulation model is coupled with a thermal environment model of ventilated space to simulate both the thermal conditions and occupant's responses. The coupling model is validated with experimental data at high occupant density in a thermal environmental chamber.
A three-dimensional numerical model is used for a turbulent buoyant jet. The standard k-E model has been modified to focus on the buoyancy-production term. The usual and modified buoyancy production coefficients are used for comparisons with experimental data reported in the literature. Imported numerical results are obtained with the modified coefficient for the stack-exit velocities and temperatures. The effects of these parameters on flow characteristics are discussed.
A literature survey was conducted to identify measured airtightness values for various types of large buildings including Multi-Unit Residential Buildings (MURBs); offices; schools; commercial, industrial and institutional structures. Data was identified for 192 buildings in Canada, the United States, Great Britain and Sweden.
This study compares the characteristics of two tracer gases - sulphur hexafluoride (SF 6), and nitrous oxide (N20) – whose densities are different from that of air (i.e. 5.11 and 1.53, respectively). The study is based on exclusively experimental work; and concerns the behaviour of the two gases with regard to their distribution and dispersion in an experimental cell, incorporating into the comparison method an index that is intended to characterise the ventilation of an enclosed space, namely ventilation etfectiveness,
Two-dimensional numerical simulations have been undertaken for the steady turbulent fluid flow in a room containing a fume cupboard which is attached to a wall and a ventilation duct which is situated in the ceiling of the room, see figure 1. The wall opposite to the fume cupboard is assumed to be porous and a fully developed fluid velocity profile is applied far upstream. The calculated flow is considered to be that which is actually found in the central plane of a practical fume cupboard.