Tài liệu MAKEUP AIR DEHUMIDIFICATION DESIGN MANUAL pdf

1/7/2003 1 MAKEUP AIR DEHUMIDIFICATION DESIGN MANUAL DE/DH 1/7/2003 2 MAKEUP AIR DEHUMIDIFICATION DESIGN MANUAL The energy crisis of the mid 1970’s gave birth to a movement to conserve energy. Over the ensuing years much has been done to reduce the energy consumption of new and existing buildings. Lighting efficiency has improved so much that today we use ½ the wattage without sacrificing lumens. Improved construction methods, better insulation and high efficiency windows have also helped reduce energy consumption. However, all of these measures have resulted in a reduction of Sensible heat gains while Latent heat gains have increased. This is the reason that humidity related issues have surfaced since the mid 1970’s. One of the methods for dealing with this issue is to dehumidify and “neutralize” the moisture level of outdoor air used for makeup. This can be partially done using Latent energy recovery devices, such as desiccant enthalpy rotors. However, dedicated dehumidification component is needed to reduce the outdoor air grain level equal to or lower than indoor grain level. It is important to note that a Latent energy recovery device alone can never bring the outdoor air humidity below that of indoors. Conventional makeup air dehumidifiers are and costly to operate. The refrigeration controls are sensitive, susceptible to failure and difficult for field technicians to troubleshoot. Nautica has resolved these problems by developing a more energy efficient and reliable makeup air dehumidification system. Driven by many years of practical refrigeration experience, the Nautica makeup air dehumidification system is designed to be simple and less expensive to install, operate, maintain, troubleshoot and service. Makeup air dehumidifiers have been around for several decades and the basic concept, to remove humidity by overcooling pool air, and then compensate with re-heating, has not changed. The Nautica dehumidifier uses a regenerative heat exchanger to reduce the load on the cooling coil by pre- cooling. This unique feature reduces energy consumption by up to 50%. Conventional makeup air dehumidifiers use hot refrigerant gas to reheat the air after cooling. This process use automatic solenoid valves, check valves and piping to route the refrigerant hot gas to the appropriate device. On paper it looks good. However, excessive amounts of costly refrigerant are needed to fill the system and the devices in the refrigerant circuit are subject to malfunction if a slight amount of dirt is present. Designing dehumidification systems for makeup air is a specialized area of HVAC design engineering. This design manual provides a simple method for sizing dehumidification equipment for makeup air. Nautica dehumidifiers utilize MSP® heat transfer technology, that is compatible with chilled water, or refrigerant based systems and can be served by a wide range of conventional chillers and condensing units, using any fuel source. KEY FEATURES AND BENEFITS BENIFIT EXPLANATION OF BENIFIT OPERATING SAVINGS Energy consumption up to one-half that of conventional dehumidification systems. No reheating to compensate for over-cooling. INSTALLATION SAVINGS Lower cooling load. Lower power requirements. HIGH RELIABILITY Eliminates complicated and temperamental refrigerant-side controls, reduces breakdowns, and simplifies troubleshooting. LOW MAINTENANCE Simple design results in reduced chance for breakdowns and low maintenance costs. DE/DH 1/7/2003 3 NAUTICA vs. CONVENTIONAL DEHUMIDIFICATION TECHNOLOGY FIGURE 1 CONVENTIONAL DEHUMIDIFIER COOLING COIL HEATING COIL FAN With conventional dehumidification technology (Figure 1, above), warm humid air, flows through a cooling coil where it is cooled and dehumidified. The dehumidified and cooled air is then reheated through a heating coil prior to entering the conditioned space. In the regenerative dehumidification technology (Figure 2, above), warm, humid air flows through the first pass of an air-to-air heat exchanger for pre-cooling and dehumidification by thermal exchange with the cooler leaving air. The air then passes through a cooling coil for final cooling and dehumidification. The dehumidified and cooled air is then drawn back through the opposite side of the air-to-air heat exchanger to be heated, prior to entering the conditioned space. FIGURE 2 REGENERATIVE DEHUMIDIFIER FAN PLATE HEAT EXCHANGER COOLING COIL CONDENSED MOISTURE As in conventional dehumidification, the regenerative technology uses ordinary refrigerants or chilled water. However, in the energy-efficient regenerative dehumidifier, a lower temperature air enters the cooling coil as a result of pre-cooling and dehumidification through the air-to-air heat exchanger. This innovative combination of an air-to-air heat exchanger with conventional cooling coil results in reduced compressor capacity, requiring half the energy for dehumidification compared with conventional dehumidification systems. DE/DH 1/7/2003 4 DH AND DE UNIT CONFIGURATIONS DH—DEHUMIDIFIER ONLY EVAPORATOR SUPPLY FAN MSP TM DEHUMIDIFYING COIL DE—WITH ROTARY HEAT EXCHANGER EVAPORATOR EXHAUST FAN SUPPLY FAN HEAT MSP TM DEHUMIDIFYING COIL ENTHALPY ROTOR Makeup air dehumidifier with rotary heat exchanger for energy recovery. DE—INTEGRAL UNIT EVAPORATOR EX HAUST FAN SUPPLY FAN COMPRESSOR HEAT MSP TM DEHUMIDIFYING COIL ENTHALPY ROTOR CONDENSER Totally self-contained air-cooled packaged unit for indoor or outdoor installation. DE—WITH PLATE HEAT EXCHANGER EXHAUS T FAN SUPPLY FAN HEAT MSP TM DEHUMIDIFYING COIL PLATE EXCHANGER EVAPORATOR Makeup air dehumidifier with plate heat exchanger for energy recovery. Features • Split or packaged units • Indoor & outdoor construction • Air-cooled, water-cooled or chilled water • Heat pumps—water and air source • Double-wall construction • Stainless steel drain pans • Internally isolated fans • Modular designs • All voltage options • Cooling option Options • Energy recovery ventilators—using plate or rotary exchangers • Hot water or steam heating coils • Direct or indirect gas heating • Electric heat • Integral F&B coils • Single point electrical connections • Unit mounted disconnect switch • Self-contained control system • High efficiency MSP® heat exchangers • Variable frequency drives • Roof curbs—isolation and standard DE/DH 1/7/2003 5 MAKEUP AIR DEHUMIDIFICATION DESIGN STRATEGY Makeup air dehumidifiers should be sized to deliver a desired dew point to the conditioned space. The delivered dew point should not exceed the space dew point except under maximum conditions. When outdoor conditions are at “maximum moisture load” the space relative humidity may be permitted to rise as high as 70%. The designer should be aware that mold growth and other humidity related problems would occur only under sustained high humidity conditions. Therefore, a good design will allow increased humidity during maximum load conditions. ASHRAE publishes three design conditions with three hours of occurrence for each. The worst condition for humidity control is “maximum wet-bulb with mean coincident dry bulb temperature” (WB/MCDB). Because these conditions occur infrequently, it is wise to use a coincident high indoor humidity to avoid “over- designing”. Nautica recommends using design conditions of WB/MCDB at 0.4% occurrence. Supply air dew point should be equal to that of the room with a relative humidity of 60% to 65%. This design strategy will result in indoor humidity between 50% and 55% during “normal” conditions. Humidity is expressed in two ways; absolute and relative. Relative humidity is a good measure of comfort in an indoor environment because the temperature is stable. However, outdoor air temperature is constantly changing and relative humidity, by itself, is meaningless without knowing its temperature. Absolute humidity, on the other hand, only changes when moisture is added or subtracted from air. It is a more appropriate condition to work with in humidification and dehumidification design. Absolute humidity is expressed as dew point, grains/pound or pounds/pound. DATA ENTRY FORM VENTILATION AIR CFM CFM Tables 1 & 2 SUMMER DB GR INDOOR AIR CONDITIONS WINTER DB GR Table 3 SUMMER DB GR OUTDOOR CONDITIONS WINTER DB RH Table 4 DE/DH 1/7/2003 6 TABLE 1 – OUTDOOR AIR REQUIREMENTS FOR VENTILATION Outdoor air Outdoor air Application Cfm /person Cfm /sq ft Application Cfm /person Cfm /sq ft Food and Beverage Service Specialty Shops ----- Dining rooms 20 ----- Barber 15 ----- Cafeteria, fast food 20 ----- Beauty 25 ----- Bars, cocktail lounges 30 ----- Reducing salons 15 ----- Hotels, Motels, Resorts Dormitories Cfm/room Florists 15 ----- Bedrooms ----- 30 Clothiers, furniture 0.30 Living rooms ----- 30 Hardware, drugs, fabric 15 ----- Baths ----- 35 Supermarkets 15 ----- Lobbies 15 ----- Pet shops 1.00 Conference rooms 20 ----- Sports and Amusement ----- Assembly rooms 15 ----- Spectator areas 15 ----- Dormitory sleeping areas 15 ----- Game rooms 25 Gambling Casinos 30 ----- Ice arenas (playing areas) 0.50 Offices ----- Swimming pools (pool and deck area) 0.50 Office space 20 ----- Playing floors(gymnasium) 20 ----- Reception areas 15 ----- Ballrooms and discos 25 ----- Telecommunication centers and data entry 20 ----- Bowling alleys (seating areas) 25 ----- Conference rooms 20 ----- Theaters ----- Public Spaces Cfm/sq ft Ticket booths 20 ----- Corridors and utilities ----- 0.05 Lobbies 20 ----- Public restrooms, cfm/wc or urinal 50 ----- Auditorium 15 ----- Locker and dressing rooms ----- 0.50 Stages, studios 15 ----- Smoking lounge 60 ----- Transportation ----- Elevators ----- 1.00 Waiting rooms 15 ----- Retail Stores, Sales and Show Room Floors ----- Platforms 15 ----- Basement and street ----- 0.30 Vehicles 15 ----- Upper floors ----- 0.20 Workrooms ----- Storage rooms ----- 0.15 Meat processing 15 ----- Dressing rooms ----- 0.20 Malls and arcades ----- 0.20 Shipping and receiving ----- 0.15 Warehouses ----- 0.05 Smoking lounge 60 ----- Table 1 prescribes supply rates of acceptable outdoor air required for acceptable indoor air quality. These values have been chosen to dilute human bioeffluents and other contaminants with an adequate margin for safety and to account for health variations among people and varied activity levels. Source: ASHRAE Standard 62-2001 DE/DH 1/7/2003 7 TABLE 2 – OCCUPANCY ESTIMATES** Occupancy Occupancy Application Persons /100 sq ft Application Persons /100 sq ft Food and Beverage Service Specialty Shops Dining rooms 70 Barber 25 Cafeteria, fast food 100 Beauty 25 Bars, cocktail lounges 100 Reducing salons 20 Hotels, Motels, Resorts Dormitories Florists 8 Lobbies 30 Hardware, drugs, fabric 8 Conference rooms 50 Supermarkets 8 Assembly rooms 120 Dormitory sleeping areas 20 Sports and Amusement Gambling Casinos 120 Spectator areas 150 Offices Game rooms 70 Office space 7 Playing floors (gymnasium) 30 Reception areas 60 Ballrooms and discos 100 Telecommunication centers and data entry 60 Bowling alleys (seating areas) 70 Conference rooms 50 Theaters Public Spaces Ticket booths 60 Smoking lounge 70 Lobbies 150 Elevators Auditorium 150 Retail Stores, Sales and Show Room Floors Stages, studios 70 Basement and street 30 Transportation Upper floors 20 Waiting rooms 100 Storage rooms 15 Platforms 100 Malls and arcades 20 Vehicles 150 Shipping and receiving 10 Workrooms Warehouses 5 Meat processing 10 Smoking lounge 70 **Estimated Maximum (Net occupiable space), Source: ASHRAE Standard 62-2001 TABLE 3 - TYPICAL ROOM GRAIN CONDITIONS ROOM TEMPERATURE DB ROOM HUMIDITY RH 70º 75º 80º 50% 56.81 67.42 79.76 55% 62.57 74.28 87.90 60% 68.35 81.16 96.07 65% 74.15 88.06 104.27 70% 79.95 94.98 112.49 DE/DH 1/7/2003 8 TABLE 4a - PEAK CLIMATE CONDITIONS FOR MAKEUP AIR DEHUMIDIFICATION DESIGN DB GR/LB DB DB GR/LB DB STATE/CITY ELEV. WINTER SUMMER STATE/CITY ELEV. WINTER SUMMER ALABAMA Talkeetna 358 -28 71 64 Anniston 610 19 143 84 Valdez 33 4 60 59 Birmingham 630 18 135 83 Yakutat 30 -3 67 58 Dothan 400 28 144 83 ARIZONA Huntsville 643 15 135 83 Flagstaff 7,011 1 93 65 Mobile 220 26 142 83 Kingman 3,389 22 112 77 Montgomery 203 24 139 85 Page 4,278 20 92 74 Muscle Shoals/Florence 551 16 137 82 Phoenix, Int'I Airport 1,106 34 118 82 Ozark, Fort Rucker 299 28 146 85 Phoenix, Luke AFB 1,089 35 130 85 Tuscaloosa 171 20 142 84 Prescott 5,043 15 104 71 ALASKA Safford, Agri Center 3,117 21 111 77 Adak, NAS 13 19 59 58 Tucson 2,556 31 116 76 Anchorage, Elmendorf AFB 213 -13 69 62 Winslow 4,882 10 95 71 Anchorage, Fort Richardson 377 -19 69 64 Yuma 207 40 136 87 Anchorage, lnt'I Airport 131 -14 68 62 ARKANSAS Annette 112 13 71 65 Blytheville, Eaker AFB 256 12 149 88 Barrow 13 -41 53 54 Fayetteville 1,250 6 136 85 Bethel 151 -28 68 62 Fort Smith 463 13 134 85 Bettles 643 -49 72 66 Little Rock, AFB 312 16 141 86 Big Delta, Ft. Greely 1,283 -45 70 65 Texarkana 390 20 143 85 Cold Bay 102 6 62 56 CALIFORNIA Cordova 43 -4 67 63 Alameda, NAS 13 40 85 70 Deadhorse 56 -36 61 62 Arcata/Eureka 217 30 78 64 Dillingham 95 -20 67 62 Bakersfield 492 32 92 84 Fairbanks, Eielson AFB 548 -33 74 66 Barstow/Daggett 1,926 28 103 81 Fairbanks, Int'l Airport 453 -47 72 65 Blue Canyon 5,285 21 74 70 Galena 151 -33 73 66 Burbank/Glendale 774 39 108 80 Gulkana 1,578 -44 63 62 Fairfield, Travis AFB 62 31 85 76 Homer 72 0 64 59 Fresno 328 30 92 85 Juneau 23 4 70 63 Lancaster/Palmdale 2,346 22 92 80 Kenai 95 -22 64 59 Lemoore, Reeves NAS 236 30 101 89 Ketchikan 95 13 74 64 Long Beach 39 40 101 76 King Salmon 49 -24 66 61 Las Angeles 105 43 99 75 Kodiak, State USCG Base 1 12 7 67 61 Marysville, Beale AFB 112 31 86 85 Kotzebue 16 -36 70 64 Merced, Castle AFB 187 30 90 81 McGrath 338 -47 69 63 Mount Shasta 3,543 16 76 74 Middleton Island 46 18 57 56 Mountain View, Moffet NAS 39 36 83 74 Nenana 361 -51 69 65 Ontario 942 35 113 80 Nome 23 -31 64 61 Oxnard, Pt. Mugu NAWS 7 39 103 74 Northway 1,722 -34 66 62 Paso Robles 837 26 81 76 Port Heiden 95 -6 57 59 Red Bluff 354 29 94 82 Saint Paul island 30 -2 55 52 Riverside, March AFB 1,539 34 104 79 Sitka 66 16 74 62 Sacramento, Mather Field 95 30 80 79 Source: ASHRAE Handbook of Fundamentals 1997 DE/DH 1/7/2003 9 TABLE 4b - PEAK CLIMATE CONDITIONS FOR MAKEUP AIR DEHUMIDIFICATION DESIGN DB GR/LB DB DB GR/LB DB STATE/CITY ELEV. WINTER SUMMER STATE/CITY ELEV. WINTER SUMMER CALIFORNIA CONT'D Miami. Int'I Airport 13 46 144 83 Sacramento, McClellan AFB 75 31 85 84 Miami, New Tamiami A 10 45 145 83 Sacramento, Metro 23 31 84 82 Milton, Whiting Field NAS 200 28 148 86 Salinas 85 33 82 69 Orlando 105 37 142 83 San Bernardino, Norton AFB 1,158 34 107 83 Panama City, Tyndall AFB 16 33 160 86 San Diego, Int'l Airport 30 44 111 77 Pensacola, Sherman AFB 30 28 150 85 San Diego, Miramar NAS 420 39 104 78 Saint Petersburg 10 43 156 86 San Francisco 16 37 76 67 Sarasota/Bradenton 30 39 153 87 San Jose Int'l Airport 56 35 85 77 Tallahassee 69 25 142 83 Santa Barbara 10 34 96 74 Tampa, int'I Airport 10 36 144 85 Santa Maria 240 32 80 70 Valparaiso, Eglin AFB 85 30 149 85 Stockton 26 30 83 78 Vero Beach 26 39 141 85 Victorville George AFB 2,874 27 102 78 West Palm Beach 20 43 143 84 COLORADO GEORGIA Alamosa 7,543 -17 87 62 Albany 194 27 141 83 Colorado Springs 6,171 -2 92 66 Athens 810 20 133 82 Craig 6,283 -20 77 66 Atlanta 1,033 18 133 82 Denver 5,331 -3 96 69 Augusta 148 21 135 84 Eagle 6,539 -13 88 64 Brunswick 20 30 147 86 Grand Junction 4,839 2 93 70 Columbus, Fort Benning 233 23 142 85 Limon 5,364 -6 96 67 Columbus, Metro Airport 397 23 139 82 Pueblo 4,721 -1 104 71 Macon 361 23 136 83 Trinidad 5,761 -2 96 71 Marietta, Dobbins AFB 1,070 21 134 82 CONNECTICUT Rome 643 15 134 83 Bridgeport 16 8 126 79 Savannah 49 26 139 84 Hartford, Brainard Field 20 2 228 71 Valdosta, Moody AFB 233 30 142 85 Windsor Locks. Bradley Fld 180 3 119 81 Valdosta, Regional Airport 203 28 144 83 DELAWARE Waycross 151 29 134 84 Dover, AFB 30 14 141 84 HAWAII Wilmington 79 10 132 82 Ewa, Barbers Point NAS 49 59 126 83 FLORIDA Hilo 36 61 130 79 Apalachicola 20 31 148 85 Honolulu 16 61 125 80 Cape Canaveral NASA 10 38 145 84 Kahului 66 59 127 80 Daytona Beach 36 34 141 84 Kaneohe, MCAS 10 67 138 81 Fort Lauderdale/Hollywood 23 46 147 85 Lihue 148 60 132 80 Fort Myers 16 42 147 84 Molokai 449 60 128 80 Gainesville 151 30 143 84 IDAHO Hlomestead AFB 7 48 150 87 Boise 2,867 2 79 72 Jacksonville, Cecil Field NAS 82 31 138 84 Burley 4,150 -5 90 75 Jacksonville, Int'I Airport 30 29 142 85 Idaho Falls 4,741 -12 88 71 Jacksonville, Mavport Naval 16 34 147 86 Lewiston 1,437 6 76 72 Key West 20 55 149 85 Mountain Home, AFB 2,995 0 79 71 Melbourne 36 38 155 86 Mullan 3,317 -1 86 69 Source: ASHRAE Handbook of Fundamentals 1997 DE/DH 1/7/2003 10 TABLE 4c - PEAK CLIMATE CONDITIONS FOR MAKEUP AIR DEHUMIDIFICATION DESIGN DB GR/LB DB DB GR/LB DB STATE/CITY ELEV. WINTER SUMMER STATE/CITY ELEV. WINTER SUMMER IDAHO CONT'D Wichita, Airport 1,339 2 129 83 Pocatello 4,478 -7 83 70 Wichita, McConnell AFB 1,371 2 133 84 ILLINOIS KENTUCKY Belleville, Scott AFB 453 3 141 87 Bowling Green 548 7 136 84 Chicago, Meigs Field 623 -4 132 84 Covington/Cincinnati Airport 876 1 132 84 Chicago, O'Hare Int'I .A 673 -6 130 84 Fort Campbell, AAF 571 9 143 85 Decatur 682 -2 140 86 Fort Knox, Godman AAF 755 9 138 85 Glenview, NAS 653 -3 330 85 Jackson 1,381 7 135 83 Marseilles 738 -5 135 85 Lexington 988 4 130 83 Moline/Davenport IA 594 -8 134 85 Louisville 489 6 134 85 Peoria 663 -6 137 85 Paducah 413 7 143 86 Quincy 768 -4 138 84 LOUISIANA Rockford 741 -10 132 84 Alexandria, England AFB 89 27 147 86 Springfield 614 -4 139 86 Baton Rouge 69 27 145 84 West Chicago 758 -7 138 85 Bossier City, Barksdale AFB 167 22 144 84 INDIANA Lafayette 43 28 146 84 Evansville 387 3 137 86 Lake Charles 33 29 148 84 Fort Wayne 827 -4 131 83 Leesville, Fort Polk 328 27 144 83 Indianapolis 807 -3 137 84 Monroe 79 22 147 86 Lafayette, Purdue Univ 607 -5 139 85 New Orleans, lnt'l Airport 30 30 151 86 Peru, Grissom AFB 810 -3 142 85 New Orleans, Lakefront A 10 35 150 85 South Bend 774 -2 130 83 Shreveport 259 22 139 84 Terre Haute 584 -3 144 86 MAINE IOWA Augusta 351 -3 113 77 Burlington 699 -4 136 85 Bangor 194 -7 111 78 Cedar Rapids 869 -11 136 84 Brunswick, NAS 75 -2 111 78 Des Moines 965 -9 133 85 Caribou 623 -14 112 76 Fort Dodge 1,165 -13 133 84 Limestone, Loring AFB 745 -13 107 75 Lamoni 1,122 -6 134 83 Portland 62 -3 114 79 Mason City 1,214 -15 135 84 MARYLAND Ottumwa 846 -5 136 84 Camp Springs, Andrews AFB 282 13 134 83 Sioux City 1,102 -11 135 86 Baltimore, BWI Airport 154 11 132 83 Spencer 1,339 -16 134 84 Lex Park, Patuxent River NAS 39 16 136 84 Waterloo 879 -14 132 84 Salisbury 52 13 144 84 KANSAS MASSACHUSETTS Concordia 1,483 -4 133 84 Boston 30 7 119 80 Dodge City 2,592 0 120 79 East Falmouth, Otis Angb 131 11 125 78 Ft Riley, Marshall AAF 1,066 -2 136 86 Weymouth, S Weymouth NAS 161 6 129 82 Garden City 2,890 -3 118 79 Worcester 1,010 0 119 78 Goodland 3,688 -3 111 74 MICHIGAN Russell 1,864 -4 126 83 Alpena 692 -7 116 79 salina 1,273 -3 132 85 Detroit, Metro 663 0 125 83 Topeka 886 -2 139 87 Flint 764 -2 125 83 Source: ASHRAE Handbook of Fundamentals 1997 [...]... condensing unit supply and exhaust fans, MSP® Series DHxx (Makeup air dehumidifier without energy recovery): supply fan, MSP® dehumidifying coil, heater, controls, condensing unit Modular makeup air dehumidifier Single supplier for single source responsibility shall provide all components for makeup air dehumidifier system Unit shall include: MSP® dehumidification coil section, separate supply fan, heater,... furnished with a unitary dehumidifying coil Coil to comprise a cooling coil for dehumidifying the air, air- to -air heat exchangers for precooling and reheating the air and a manifold assembly to direct the air through its intended path Dehumidifiers using hot gas for reheat shall not be acceptable Air- to -Air heat exchanger shall be stationary, plate-type utilizing MSP® (multiple small plate) technology... motorized low leak outside air damper on inlet of energy recovery section Provide gravity-type damper for exhaust air on discharge of energy recovery sections Outside air damper shall be provided with end switch interlocked with supply fan Provide air inlet and discharge hoods CONTROL SYSTEM Control system shall be designed to optimize energy consumption and provide control of outside air delivery dewpoint...TABLE 4d - PEAK CLIMATE CONDITIONS FOR MAKEUP AIR DEHUMIDIFICATION DESIGN STATE/CITY ELEV DB GR/LB WINTER DB STATE/CITY SUMMER ELEV DB GR/LB DB St Louis, Int'l Airport 564 WINTER 2 138 85 804 0 126 81 Warrensburg whiteman AFB 869 1 139 86 1,079 -9 116 79 MONTANA 600 9 113 82 Billings 3,570 -13 83 71... 285 16 1,165 -10 111 78 Bristol Chattanooga Crossville Memphis DE/DH 1/7/2003 143 87 Montpelier/Barre Source: ASHRAE Handbook of Fundamentals 1997 13 TABLE 4g - PEAK CLIMATE CONDITIONS FOR MAKEUP AIR DEHUMIDIFICATION DESIGN STATE/CITY ELEV DB WINTER GR/LB DB SUMMER VIRGINIA STATE/CITY ELEV DB WINTER GR/LB DB SUMMER Cody 5,095 -14 76 70 69 12 139 86 Gillette 4,035 -16 88 73 Hampton, Langley AFB 10 21 141... evaluated by engineer twelve days prior to bidding PRODUCT The makeup air dehumidifier shall be a (Pick One - PACKAGED, SPLIT, MODULAR) system Unit will require a single electrical connection Disconnect switch(es) shall be furnished by Division 16 contractor Unit shall include the following components: (PICK APPROPRIATE PARAGRAPH) – Series DExx (Makeup air dehumidifier with energy recovery): dehumidifying coil,... 83 NEW JERSEY 1,270 3 66 8 131 81 Spickard/Trenton Springfield DE/DH 1/7/2003 134 84 Atlantic City Source: ASHRAE Handbook of Fundamentals 1997 11 TABLE 4e - PEAK CLIMATE CONDITIONS FOR MAKEUP AIR DEHUMIDIFICATION DESIGN STATE/CITY ELEV DB WINTER GR/LB DB STATE/CITY SUMMER ELEV DB GR/LB DB 1,188 WINTER 18 133 80 Millvile 82 10 134 81 Jacksonville, New River Mcaf 26 23 145 86 Newark 30 10 127 81 New... 84 Medford 1,329 21 81 75 Greensboro 886 15 13 30 76 65 Asheville DE/DH 1/7/2003 132 82 North Bend Source: ASHRAE Handbook of Fundamentals 1997 12 TABLE 4f - PEAK CLIMATE CONDITIONS FOR MAKEUP AIR DEHUMIDIFICATION DESIGN STATE/CITY ELEV DB WINTER GR/LB DB OREGON CONT'D Pendleton Portland Redmond Salem Sexton Summit STATE/CITY SUMMER Nashville ELEV DB GR/LB DB 591 WINTER 10 SUMMER 134 83 1,496 3 74... 114 73 Philadelphia, Int'I Airport 30 11 132 83 Fort Worth, Carswell AFB 650 18 141 85 Philadelphia, Northeast A 121 11 135 83 Fort Worth, Meacham Field 709 19 135 83 Philadelphia, Willow Gr NAS 361 10 131 83 Guadalupe Pass 5,453 13 102 71 Pittsburgh, Allegheny Co A 1,253 4 122 79 Houston, Hobby Airport 46 29 147 84 Pittsburgh, Int'l Airport 1,224 2 121 80 Houston, Inter Airport 108 27 144 83 WiIkes-Barre/Scranton... lnt'l Airport 449 23 78 71 Spokane, Fairchild AFB 2,461 1 77 68 Stampede Pass 3,967 3 70 63 322 18 79 71 1,204 4 82 74 WASHINGTON Tacoma, McChord AFB Walla Walla Wenatchee 1,243 3 78 75 Yakima 1,066 4 78 75 2,858 5 120 75 981 6 129 81 1,998 -2 121 78 WEST VIRGINIA Bluefield Charleston Elkins Huntington 837 6 132 82 Martinsburg 558 8 130 81 Morgantown 1,247 4 124 79 Parkersburg 860 4 132 82 Eau Claire . 1/7/2003 1 MAKEUP AIR DEHUMIDIFICATION DESIGN MANUAL DE/DH 1/7/2003 2 MAKEUP AIR DEHUMIDIFICATION DESIGN MANUAL The energy crisis of. reliable makeup air dehumidification system. Driven by many years of practical refrigeration experience, the Nautica makeup air dehumidification system is designed