Document b52wQ918rZ0QmGR8LEweEJrNk

624 CHAPTER 42 1960 Guide PARTS or MOISTURE PER MILLION PARTS ORT- AIR 6T VOLUME Fig. 9.... Moisture Content of Air at One Atmosphere Pressure Fig. 9 shows the moisture content of air at one atmosphere pressure. SORPTION DEHUMIDIFIERS FOR ELEVATED PRESSURES The same sorption principles which pertain to low-pres sure (approximately atmospheric) dehumidification apply to drying of high-pressure air, process gases, etc. The sorbents described previously can be used with equal effectiveness. - Equipment design may vary considerably in detail, but most basic adsorption units utilize dual bed construction for continuous operation. and either internal or external beat source with air or process gas as reactivation purge for liberating previously adsorbed moisture. A single ad- Fig. 10... .Typical Performance Data for Solid Sorption Dehumidifiers at Elevated Pressures sorbent bed may be used for intermittent drying require ments. Absorption units are generally constructed in the aamft maimer as atmospheric pressure units, except that they are enclosed in vessels suitable for the operating pres sure. Either compressing of the gas to be dehumidified or pre cooling by water, brine, or refrigeration will reduce the total moisture load to be handled by the sorbent permitting use of smaller drying units and permitting lower dew-point performance. The performance of the complete system consisting of precooler and sorbent dryer must be investi gated at various temperatures to determine the most eco nomic operating level. Applications include drying compressed air for processing, testing, and instrument use. Drying of air and gases have made many processes possible or effective in the chemical, petroleum, and steel industries. Typical performance data for solid sorption dehumidifiers for 'pressures up to 200 prig are shown in Fig. 10. A dew-point conversion chart is shown in fig. 11. This chart is of value to determine changes in air dew points due to compression or expansion. USES OF SORPTION DEHUMIDIFIERS Sorption- dehumidification equipment is used where it is desirable to control the removal of moisture from the air independent of the dry-bulb temperature of the air. Such a procedure is required in many industrial processes where the relative humidity must be controlled during the manu facture and preservation of the product. In comfort air-conditioning dehumidification, with cooling, may serve advantageously under certain design conditions Dehumidification by Sorbent Materials 625 such as high moisture load in comparison to sensible heat load, high ratio of fresh air to recirculated air, and in ternal load variation. Sorption type dehumidification, in combination with re frigeration, is applied in industrial areas requiring either dew-point or dry-bulb temperatures below the freezing point of water, eliminating the formation of frost or ice on refrigeration coils. This particular function is illustrated by its use in wind tunnels to produce dew points as low as --60 F. It is also employed in low temperature process tunnels and chill rooms. Other applications include supplying dry air to prevent condensation of moisture on cold surfaces, dehumidification of warehouses or storage rooms for military supplies as well as certain commercial products, and maintaining a dry atmos phere in cargo holds on ships. A more recent development is found in the dehumidification of underground caves. water surface being 100 fpm. Determine the quantity and con dition of the dehumidified air to be supplied to the room. Solution: The internal moisture gain consists of items 1 to 5. .,, 1. rrom occupants: Qi*in per Minute 4 X 1800/60 = 120 1800 grains per person per hour is obtained from Fig. 7, Chapter 6, by interpolation between curves C and D. 2. From burned gas: 15 X 650/60 = 162 1 cu ft natural gas produces approximately 650 grains of moisture. 3. From exposed water surface: 2 X 20 * 40 Evaporation from water surface is assumed to be 20 grains per (minute) (square foot) at 87 F water with air movement of 100 fpm. 4. From infiltration: X (118.4 - 34.1) - 696 MOISTURE LOAD CALCULATIONS The application of dehumidification equipment to main tain spaces at low dew point requires careful calculation of the internal moisture gain in the room from all sources. The internal moisture gain consists of latent load from the occupants, process load from any products which give up moisture, exposed water surfaces in the space, open gas flame, water-vapor migration through cracks around the doors, windows, and other openings in the room (infiltra tion), and moisture transmitted through the building sur faces. The latent load from people, exposed water surfaces, open gas flame, and moisture , transmitted through building surfaces are found in the appropriate Guide chapters. The internal latent load due to water-vapor transfer through cracks, conveyor slots, and open doors has not been standard ized and is generally calculated by engineers on the basis of judgment and experience. Calculation of the dehumidification required to maintain lower than normal moisture content in a given room begins with determination of the rate of moisture gain in the room from all sources. It is common practice, when maintiiininjT a low humidity ratio, to recirculate a large percentage of the air in the room through the dehumidifier, and to add only enough outdoor air to meet the needs of the problem. The humidity ratio of the mixture of outdoor and recirculated air and the dehumidifier performance data can be used to calculate the humidity ratio of the air leaving the dehumidi fier. The difference between the humidity ratio of the air in the room and that of the dehumidified air entering the room represents the effective dehumidification per pound of air. The rate of internal moisture gain in grains per minute, divided by the effective dehumidification in grains per pound of air, equals the air quantity required in pounds per minute. The following typical example using arbitrary values shows a general method of determining the dehumidifying require ments. Sensible heat determination considerations are dis cussed in other chapters, and are purposely omitted here. One air change, 6000 cu ft, assumed per hour (see Chapter 11). 5. Moisture transmitted through room surface: ~ X 3 x (0.783 - 0.176) - 67 Permeability assumed to be 3 grains per (square foot) (hour) (inch Hg vapor-pressure difference on two sides of wall). Total moisture gain from internal sources 1085 Let ? be the air delivered to the room, pounds per minute. Let it be assumed for this problem that 85 percent of the air is recirculated and 15 percent is outdoor air. Enough air must be supplied to replace leakage from the system or to satisfy normal ventilating requirements for the occupants of the room as given in Chapter 6, whichever is greater. The amount is estimated from experience or obtained by test. The humidity ratio of the mixture of recirculated and out door air entering the dchumidifier is then: 0A5y(24J) + 0.157(118.4) 0.85? + 0.15? TM 38.3 grains per pound entering dehumidifier. From the manufacturer's performance data for the dehumidifier to be used it is determined that with 38.3 grains per pound of entering air the leaving condition is 6.5 grains per pound. Effective dehumidification in the room is 24.1 -- 6.6 or 17.6 grains per pound of supply air. an... . 1085 grains per minute ............... The { 17.6 grains per pound " 616 lb *lr >" n"nute minimum that must be supplied to the room to maintain 30 F dew point. Note that this value represents the minimum requirement for the arbitrary conditions set forth and that in practice, safety margins should be added to the outdoor air percentage value and to the calculated internal moisture gain. VAPOR TRANSFER TO DEHUMIDIFIED SPACE muwr conditions 01 ra jr and 20 percent relative humidil TM 7* ,lm8&5LISu?dIf ir, 30 F dew point, in a nx 20 ft x 30 ft x 10ft high, having a total wall, ceiling, and fle surface area of 2200 sq ft. Outdoor design conditions are 72 dew point (118.4 grains per pound). Internal sources of moisture are: 4 occupants: an open m ural gas burner using 15 cu ft of natural gas per hour: an op top water tank, having an area of 2 sq ft exposed surface which water is maintained at 87 F, with air movement over t The walls enclosing a dehumidified space are subjected to a vapor-pressure differential. The pressure of the vapor outride the walls tends to force moisture through the walls into the dehumidified zone of relatively low vapor pressure. As this process can be an unnecessary load on the de humidifying equipment, provisions should be made for keep ing the vapor transfer to a minimum Also, if the space is cooled below the ambient dew point,"there is a possibility that condensation may occur within the walls, unless vapor