Document pBk0jqpO4M3pwm6YVOYEqZOKj

American Society of Heating and Ventilating Engineers Guide, 1956 s H = heat to be carried off, in Btu per minute. Q = air flow in cubic feet per minute. D = inlet-outlet temperature difference in degrees Fahrenheit. ; For disposing of air impurities, the required air flow must be such that the outside air will dilute the impurities to a degree that they are no longer objectionable. For human occupancy, such as in auditoriums and classrooms, 10 cfm per person is usually taken as the minimum of outside air necessary for ventilation (see Chapter 3).' For garage ventilation, sufficient air must be admitted to dilute the carbon monoxide content of the indoor air to 1 in 10,000 (see Garage Ventilation in this Chapter). Air quantity and quality are not the only requirements. For human occupancy, air distribution is important. In ventilation the air distribu tion is almost entirely a matter of the number, the design, and the location of inlets and outlets. In locating openings, special precautions should be taken against the formation of dead air spaces or pockets within the zone of occupancy. Suggested methods for estimating the air flow due to temperature difference alone and to wind alone have already been given. It must be remembered that when both forces are acting together, even without interference, the resulting air flow is not equal to the sum of the two estimated quantities. The same openings have been assumed in both' cases, and since the resistance to flow through the openings varies ap proximately with the square of the velocity3, this resistance becomes a limiting factor as the flow through the openings is increased. Recent investigations1,2 show that the total flow is only 10 per cent above the flow caused by the greater force when the two forces are nearly equal, and this percentage decreases rapidly as one force increases above the other. Tests on roof ventilators indicate that this is too conservative in the direction of low total flow quantities, but there is in any case a large judgment factor involved. The wind velocity and direction, the outdoor temperature, or the indoor activities cannot be predicted with certainty, and great refinement in calculations is therefore not justified. When designing for winter conditions, an added variable is the heat lost by direct flow through walls and windows and by infiltration. 'Example 1. Assume a drop forge shop, 200 ft long, 100 ft wide, and 30 ft high. The cubical content is 600,000 cu ft, and the height of the air outlet over that of the inlet is 30 ft. Oil fuel of 18,000 Btu per lb is used in this shop at the rate of 15 gal per hour (7.75 lb per gal). Temperature differences are 10 F in summer and 30 F in winter; and the wind velocity is 5 mph in summer arid 8 mph in winter. What is the necessary area for the inlets and outlets, and what is the rate of air flow through the building? , Solution. The system must be designed for the summer conditions as these are the more severe. The heat to be removed per minute is: H = X 7.75 X 18,000 = 34,875 Btu. . By Equation 3, the air flow required to remove this heat with a temperature difference of 10 deg is: Q VH cD 13.5 X 34,875 0.24 X 10 . 196,172 cfm. This is true for turbulent flow only. It would be more correct to state that theresistance varies approxi mately with V* for high to moderate velocities, with V1 *s for moderate to low velocities, and with the first power of the velocity for very low velocities through small openings. 96 Chapter 4--Natural Ventilation . . ^ to i9.6 air changes per hour. The assumption is made that the average 1 his ,s *** difference between indoors and outdoors is the same as the temperature rise ^Theair from the inlet opening to the outlet opening. Actually, the latter difference is i j jq ^e value of 19.6 air changes per hour is conservative as it allows for more cooling than is necessary for an average temperature difference of 10 deg. i/ i ok 172 cfm are to be circulated by the force of the temperature difference alone, the area of opening would be, by Equation 2: Q_______ 196,172 A = 94 VH (!i ^~bj _ 9.4 V 30 X 10 ~ 1,205 ^ ft' If this area of openings were provided, a wind velocity of 5 mph, acting alone, would produce a flow according to Equation 1, of: Q = EA V = 0.50 X 1,205 X 5 X 88 = 265,100 cfm. If the inlet openings do not face the wind, but are at an angle with it, about half this amount may be considered to flow. A factor of judgment must now be exercised in making the selection of the area of openings to be specified. Apparently 1205 sq ft are a very generous allowance because either a direct wind of 5 mph or an average temperature difference of 10 deg acting alone will more than suffice to carry away the heat, and when the two forces are acting together, the system may have an excess capacity of 25 per cent to 50 per cent, especially if the outlets are made up partially of roof ventilators which employ the force of the wind for producing a suction effect. On the other hand, the wind may at times come from an unfavorable direction, or its velocity may fall below 5 mph or the building construction may not permit a full 2400. sq ft of inlet window area and an equal amount of monitor or roof ventilator outlet area. In case the two sets of openings are not equal, their effectiveness is reduced. From this example it must be apparent that while formulas may furnish a reliable guide, the final solution of a problem of natural venti lation requires a common sense analysis of local conditions to supplement and to modify the dictates of the formulas. GENERAL RULES A few of the important requirements in addition to those already outlined are: 1. Inlet openings should be well distributed, and should be located on the windward side near the bottom, while outlet openings are located on the leeward side near the top. Outside air will then be supplied to the zone of occupancy. 2. Direct short circuits between openings on two sides at a high level may clear the air at that level without producing any appreciable ventilation at the level of occupancy. 3- ventilators should be located 20 to 40 ft apart each way and preferably on the ridge of the roof. The closer spacings are used when ventilating rooms with low ceilings. 4. Greatest flow per square foot of total opening is obtained by using inlet and outlet openings of nearly equal areas. 1 t'ullLa,n ?nc*ustrial building where furnaces, that give off heat and fumes, are to be installed, it is better to locate them in the end of the building exposed to the prevailing wind. The strong suction effect of the wind at the roof near the windward end will then cooperate with temperature difference, to provide for the most active and satisfactory )a6PTI air. 97