Document vBB51zJOMDEZqGq4jXk8VQ6nR

250 CHAPTER 21 1962 Guide And Data Book perceptible air flow will exist except in the immediate area of the hood. Exterior Hoods Where enclosure of the proces is impracticable, the air flow pattern in front of the hood must be such that capture velocities required to convey the contaminant to the hood opening will be maintained in the area of contaminant generation. The method for determining, approximately, the quan tity of air that must be exhausted from an unobstructed hood, without flanges, to produce design capture velocities at the point or origin, is given in Equation 1: Q - Vx(10X' + A) (1) where Q -- quantity of air exhausted, cubic feet per minute. Vx " air velocity at X-distance in feet from the hood and and on the center line of the hood, feet per minute. ' X distance along the hood center line, from the face of the hood to the point where the air velocity is Vs feet per minute, feet. A -- area of the hood opening, square feet. Fig. 1 shows lines of equal velocities (velocity contours) for a rectangular hood opening with a side ratio of onehalf. The velocities are expressed as percentages of the velocity at the opening. Studies have established the principle of similarity of contours which states that the positions of the velocity contours for any hood (when the contours are expressed in terms of the average velocity at the hood opening) are purely functions of the shape of the hood. Extensive studies*' ** " have revealed variations in values of such velocity contours for long narrow slots and for hoods with one or more planes shielded against air flow. For smaller hoods, flanges which are usually 3 to 6 in. wide surrounding the hood opening usually will improve Fig. 1 .... Velocity Contours for Rectangular Opening with a Side Ratio of One-Half. Contours are Expressed as Percentages of the Velocity at the Opening Table 2 .... Summary of Exhaust Rates Required with Common Types-of Exterior Hoods Applied to Cold Processes Only" X-Oidonce fad*s Sioplt Opening, vift or aa'thard Flange or Taper, but No None ffcrnfcfng Opening!* Simple ftectongwlor Opto, fag Ranked by Ffej* FeroOei to Ajcjjh Htotf Rate Cfm Exheod Rate Cfm 2 25-75 4 50-100 6 100-200 6 200-400 10 300-600 25-60 50-75 75-150 150-300 200-400 12 400-800 15 600-1200 18 900-1500 21 1200-1800 24 1500-2200 300-600 400-800 600-900 700-1000 800-1200 30 2500-3500 1200-1800 36 3000-4500 1500-2200 42 4000-6000 2000-3000 48 5000-7000 2500-3500 .X-Dutanc* Single dot* fooled by poroOei plane on which eoateauaatioa procwti scan For X^btonce (Le-, width of plane! always leu (baa H length of dof Less than 2 ft More than 2 ft Exhaust rate 125 to 150 cfm per sq ft of plane area. Exhaust rate 75 to 125 cfm per sq ft of plane area. * tUiora to dmple hood opening that perform in accordance with Equation 1. * Baton to hood harts* a complete ftanhtn* plane parallel to ana which pre vents tow cd air from haU of normalair supply acne, and petfonaa in accordaoca with the equation, 0 -- V* (3X* + A). Example: rectangular hood opening rertia* on bench top. Indudea tingle alota, ao flanked, for X-dbtancc pester thaa ii slot length. * If X-distance is pester thaa Vi slot length, oousittei it as a single opening by* plane (see upper right column). With exhaust rate divided befogs 3 alota, an additional safety (actor is provided. From flea* nd Fiscssg VcitilaKw, by W. C. L Heaeon (Industrial Prom, New Ycck). the air flow in front of the hood and will reduce the air volume required to provide desired capture velocities by as much as 25 percent. The exhaust volume calculated for an exterior hood by different designers may vary greatly due to their selection of different empirical design velocities. Usually capture ve locity design values are in the 50 to 200 fpm range. The exhaust rates calculated for large exterior hoods may become needlessly large if the capture velocity is selected blindly. Whether on not an individual particle or a small wisp of gas or smoke in motion away from the hood is captured before it escapes from the tone of in fluence created by the hood is determined not only by the specific air velocity (design capture velocity) at the im mediate point of contaminant release but also by the depth of the moving air curtain it must traverse before it gets beyond the influence of the hood. The capturing force of the air flow in front of any exhaust hood is the summa tion of all the separate velocities beyond (away from the hood) the point of contaminant release multiplied by the distance through which each velocity acts; i-c., force Industrial Exhaust Systems 251 rigies distance, the force being a function of the velocity. For large hoods, or more accurately for large exhaust rates, the depth of the zone of influence is much greater than for st"*11 exhaust rates and, also for the former, the (}iStance between successive velocity contours is greater, further effectiveness for larger volumes can be obtained where the air supply source produces a sweeping flow toward the tone of contaminant release. Table 2 presents design data by Hemeonu applicable to exterior hoods employed for exhausting contaminants originating in a cold process only. These values are based on Equation 1 wherein varying values of Vx have been employed according to a scale that takes account of ve locity depth factors discussed in the preceding paragraph, Bed where X-distance is taken as -the distance from the hood face to the point where any high velocity air cur rents engendered by the contaminating process itself have expended their energy. In addition, the ranges of exhaust volumes which have been found satisfactory in practice for many operations are reported in Table 3. These data provide a means of checking the calculated rates for specific applications. SPECIAL EXHAUST REQUIREMENTS It is important to note that certain operations may require exhaust volumes in excess of the quantities based on design data from Table 1 and Equation 1. Typical reasons for increased ventilation rates include: 1. Induced air flow caused by the thermal or stack effect from sources of extreme heat. 2. Induced air flow caused by falling granular material in huge quantities through considerable height, or by internal rotating parts such as some types of crushers, knives, or mace/atoia (See discussion in later section Induced Air Flow and Table 4.) 3. Exhaust volumes insufficient to dilute mixtures of com bustible vapor and air to less than 20 percent of the lower ex plosive limit of the combustible. 4. Room air currents caused by cross drafts, spot cooling, motion of machinery or operators. Cross drafts are of great significance in the exhaust of hot processes with high canopy hoods. 5. Design volumes, especially in the case of exoea heat con trol and solvent vapors, may be based on dilution systems where exhaust volumes are selected to keep contaminant concentra tions below dftrign levels. See Reference 3, Chapter 10 of the 1961 Gums And Data Book. 6. Local or State regulations may specify larger exhaust vol umes for specific operations. Exhaust volume requirements for many specific opera tions have been listed in Tables 3, 5, 6, and 7. Exhaust of Hot Processes In designing local exhaust hoods for hot processes, it is necessary to estimate the rate of -delivery of hot air to the hood by the convection column. The exhaust ca pacity should exceed this by an amount sufficient to create a velocity in the air flowing into the envelope sur rounding the convection column that will prevent escape of the heated air at the edges of tire hood. Unless distances from the heat source to the receiving hood are small (possibly under 3 ft), the quantity of heated air entering the hood is increased substantially by the induction and turbulent mixing of large quantities of room air as the hstance above the heat source increases. Unless the ex haust hood rn handle this total volume, spillage of con taminated mixture will occur. The exhaust rate for satisfactory control of hot proc esses nan be- kept at a minimum by enclosing the hot processes as completely as possible and exhausting from the top of the enclosure. Low canopy hoods rank next to enclosures in economy of air flow. High canopy hoods must handle greatly in creased amounts of air over that in the heated stream itself, in order to receive and dispose of the air entrained by the convection column from far below. Where lateral exhaust ventilation must be employed, the air flow toward the hood has to overcome the tendency of the heated sir to rise and must sweep it into the hood. Consequently, the required exhaust air flow is very much larger than for hoods that simply capture the upward flow of heated air. A combination of an exhaust hood with a positive jet of air blown across the top of the equipment and directed into the hood may be required above large pieces of equipment. Hemeos has suggested1* design Equations 2 to 6 which follow for various types of hoods. Equation 2 is suggested for estimating the flow of heated air rising from the top of a hot body: where V, - 29 v'X A,11, (2) q ~ air flow rate at upper limits of hot body, cubic feet per minute. Ap -- cross-sectional area of air stream at upper limits of hot body, square feet. U -- height of hot body, feet. H, = convections! heat transfer rate, Btu per minute. The area A, may be approximated from the dimensions of the hot body. For horizontal rods, the width of the stream is practically the diameter of the rod. For vertical planes, the air stream appears to thicken at an angle of 4 to 5 deg with the plane. For horizontal planes, the area of the air stream may be taken as equal to the area of the plane itself. In the case of horizontal plates, in the absence of better experimental information, l may be taken as equal to the horizontal diameter. Chapter 4 of tire 1961 Guide And Data Book furnishes information which may be used in estimating the heat transfer rate H*. The flow rate, , of heated air entering the hood after turbulent mixing and dilution have taken place may be' approximated for low canopy hoods above horizontal sur faces and where no heat from, steam is involved, as where q. - 5.4 At* 4 (Af)w* (3) A, " surface area of hot body, square feet. At - the temperature difference, hot body to room air, Fahrenheit degrees. Similarly, where the heat is furnished by steam from a tank of hot water, 5.- 290 A. -Vud ---- (4) where G ** the rate of steam formation, pounds per (square foot water surface) (minute). (Continued on p. t65)