Indoor Air Dehumidifier Design Manual

DR 1/7/2003

INDOOR AIR

DEHUMIDIFICATION

DESIGN MANUAL

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INDOOR 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 indoor air. Conventional indoor air dehumidification systems move large volumes of air and are 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 indoor air dehumidification system. Driven by many years of practical refrigeration experience, the Nautica indoor air dehumidification system is designed to be simple and less expensive to install, operate, maintain, troubleshoot and service, and to provide a higher level of comfort.

Indoor air dehumidifiers have been around for several decades and the basic concept, to remove humidity by

overcooling the 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% and allows airflow to be cut by up to 70%, while removing the same amount of moisture as conventional dehumidifiers.

The refrigerant-side of the system is straight forward, without complicated controls. A small refrigerant charge is used and the system is easy to troubleshoot and repair.

Conventional indoor air dehumidifiers reject heat by routing hot refrigerant gas to a reheating coil. 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 indoor air is a specialized area of HVAC design engineering. This design manual provides a simple method for sizing dehumidification equipment for indoor 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

BENEFIT EXPLANATION OF BENEFIT

OPERATING SAVINGS Energy consumption is up to one-half that of conventional dehumidification systems. No reheating to compensate for over-cooling.

INSTALLATION SAVINGS Smaller equipment and ductwork. Lower power requirements. IMPROVED COMFORT Lower humidity promotes greater comfort, and at higher temperatures

HIGH RELIABILITY Complicated and temperamental refrigerant-side controls are eliminated, reducing breakdowns, and simplifying troubleshooting.

WIDE RANGE OF SIZES Precise matching of dehumidification equipment to the load. MULTIPLE OPTIONS Dehumidification only, cooling, and heating options also available.

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NAUTICA vs. CONVENTIONAL DEHUMIDIFICATION TECHNOLOGY

FIGURE 1 CONVENTIONAL DEHUMIDIFIER

COOLINGCOIL

HEATINGCOIL

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.

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DR UNIT CONFIGURATIONS

SELF CONTAINED (INTEGRAL) UNIT

COND

MSPTM

COIL

OUTDOOR AND INDOOR UNITS, SELF CONTAINED UNITS

SPLIT SYSTEM

MSPTM

COIL

SPLIT UNITS, AIR AND WATER COOLED

PACKAGED OUTDOOR

MSPTM

COIL

OUTDOOR UNITS, AIR AND WATER COOLED

CHILLED WATER

MSPTM

COIL

OUTDOOR AND INDOOR UNITS, CHILLED WATER

PACKAGED WATER COOLED

OUTDOOR AND INDOOR UNITS, WATER COOLED

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

Options • Hot water or steam heating coils • Indirect gas heating • Electric heat • 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 • Temperature control option

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INDOOR AIR DEHUMIDIFICATION DESIGN STRATEGY

Indoor air dehumidifiers are designed to remove a specific amount of moisture from the air. The amount of moisture to be removed must be calculated. This manual offers a practical method for calculating the moisture load in commercial/industrial applications.

There are two basic areas where moisture load must be considered.

Moisture generated from indoors: People produce moisture and this varies with the level of activity. Showers, pools, fountains and some commercial processes may also contribute to moisture generated from within a building.

Moisture generated from outdoors: Outdoor air contains large amounts of moisture, especially in summer. This moisture-laden air “infiltrates” the building through opening and closing of doors and through cracks and crevices in a building envelope. The amount of

infiltration varies with the age and integrity of construction and tightness of windows.

Ventilation air also must be considered in moisture load calculations. Ventilation air is typically introduced through air conditioning and heating units. Sufficient ventilation can cause a building to be under “positive pressure”. However, exhaust from bathrooms and other locations will counter the effects of ventilation and cause a building to go under “negative” or “neutral” pressure”. Proper estimation of moisture load requires a thorough study and evaluation of exhaust/ventilation in addition to integrity of construction for estimating infiltration moisture load.

State or local codes may supersede the data in the tables herein. Code compliance is especially important for hospitals and health care facilities or for any application that exposes humans to toxic fumes. Refer to codes and/or the Industrial Ventilation handbook.

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DATA ENTRY FORM DATA

REQUIRED GET DATA

FROM QUANTITY FORMULA LATENT LOAD

BTUH LINE

VENTILATION

Ventilation rate Building survey & Tables 1 & 5 CFM CFM x .68 x (outdoor

grains-indoor grains) A

INFILTRATION Exhaust rate Building survey CFM B

Leakage Building survey & Table 2 CFM CFM x .68 x (outdoor

grains-indoor grains) C

Door traffic Building survey & Table 3 CFM CFM x .68 x (outdoor

grains-indoor grains) D

INTERNAL

Occupants Building survey & Table 4 No. No. Occupants x latent

factor (Table 4) E

Other F TOTAL LATENT LOAD Add lines A - F G

MOISTURE LOAD IN LBS/HR Line G /1,050 H

CALCULATION PROCEDURE

1) Determine ventilation rate: Using site survey data with input from tables 1 and 5, calculate the required ventilation rate and enter on line A

2) Determine infiltration air volume: a) Exhaust rate: Using site survey data calculate the total exhaust rate and enter on line B. b) Leakage: Using site survey data and Tables 2 and 3, determine infiltration leakage and enter on line C.

However, before using the Tables, a system design decision must be made in regard to the use of ventilation. The following cases are possible: i) Case 1 - The space is pressurized by the ventilation air and the infiltration is eliminated or reduced. ii) Case 2 - The space is at neutral pressure and the air handling system does not affect infiltration.

(1) This can occur if there are no exhausts or ventilation. (2) This can occur if the ventilation CFM equals the exhaust CFM.

iii) Case 3 - The space is under negative pressure from the exhaust systems associated with the space, and infiltration is increased. (1) This can occur if the space is exhausted and ventilation is not used to replace the exhausted air. (2) This can occur if the space is exhausted and ventilation replaces only part of the quantity of air exhausted.

c) Door traffic: Using site survey data, calculate infiltration due to door traffic and enter on line D. 3) Determine latent load due to ventilation: Using formula (CFM x .68 x ∆Grains) calculate latent load from ventilation

and enter on line C. 4) Determine latent load due to infiltration: Using formula (CFM x .68 x ∆Grains) calculate latent load from ventilation

and enter on line C. 5) Determine latent load due to internal gains:

a) Occupants: Using site survey data and table 5, calculate the latent load due to occupants and enter on line E. b) Other internal loads: Using site survey data calculate other loads that may contribute to the moisture load and enter

on line E. Note: Contact Nautica for help with unusual conditions.

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DEHUMIDIFICATION LOAD CALCULATION TABLES

TABLE 1 – OUTDOOR AIR REQUIREMENTS FOR VENTILATION

Outdoor air Outdoor airApplication Cfm

/personCfm /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 ----- 0.30Living rooms ----- 30 Hardware, drugs, fabric 15 -----Baths ----- 35 Supermarkets 15 -----Lobbies 15 ----- Pet shops ----- 1.00Conference 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) ----- 0.50Office 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 62-1999

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TABLE 2 - INFILTRATION IN LOW RISE COMMERCIAL BUILDINGS (Excluding Door Traffic) SPACE PRESSURIZED

CASE 1 NEUTRAL PRESSURE

CASE 2 NEGATIVE PRESSURE

CASE 3 The Table 13A air change values do not include door traffic. Add the Table 13B door infiltration to determine the total infiltration.

Outside air allows the supply CFM to exceed the return and exhaust CFM

No outside air or exhaust or outside air CFM equals exhaust CFM.

Exhaust and no outside air or exhaust exceeds outside air.

AIR CHANGES PER HOUR ... (AC/HR) Low Exhaust CFM

Note (2) 7-1/2 mphSummer

15 mph Winter

7-1/2 mphSummer

15 mph Winter

0.0 0.0 0.3

0.0 0.3 0.5

Tight construction Average construction Poor construction Loose construction Do not pressurize

0.2 0.4 0.6

1.2-1.8

0.3 0.6 1.0

2.0-3.0

Add the net space exhaust CFM to the Case 2 infiltration CFM

High Exhaust CFM Note (2)

7-1/2 mphSummer

15 mph Winter

Tight construction Average construction Poor construction Loose construction

It is not economical to pressurize the space when exhaust CFM exceeds 10 percent of the supply CFM.

0.2 0.4 0.6

1.2-1.8

0.3 0.6 1.0

2.0-1.8

Make-up air is recommended. See case 2, out-side CFM equals exhaust CFM.

DESIGN INFILTRATION CFM Table 13A infiltration CFM = (AC/Hr x Volume Of Space) /60 Total infiltration = Table 13A + Table 13B

HIGH RISE BUILDINGS The stack effect is significant in high-rise buildings and infiltration must be analyzed by the methods outlined in the ASHRAE Fundamentals Manual.

RESTAURANTS The dining area should be slightly pressurized The excess air supplied to the dining area is usually allowed to ex filtrate through the kitchen. The kitchen may require additional make up air to offset the exhaust air. Data extracted from ACCA Commercial Load Calculation manual N, table 13A

Notes on table3: (1) High rise buildings - above 3 stories (2) Low exhausts CFM - toilet and minor exhaust system CFM is less than 20% of the total supply CFM. (3) Use Table 3 for individual rooms or zones or for the entire structure. Note the simultaneous infiltration for the entire building

will be about 50% of the total of the individual room infiltration. (4) Construction definitions:

Tight construction: Non-opening windows or best quality windows; penetrations in envelope sealed, vapor barrier Average construction: Standard quality windows, major penetrations sealed, vapor barrier, glass area less than 20% of

wall area. Poor construction: Below standard windows, no vapor barrier, some unsealed crackage in the skin. Or, average

construction with operable glass exceeding 20% of the wall area Loose construction: Obvious crackage at windows and doors, unsealed cracks in the skin, no vapor barrier, and

considerable loosely fitting glass.

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TABLE 2 - EXAMPLE Example 1, Space pressurized Average construction; 27,000 Cu Ft volume Outdoor air required for occupants = 240 CFM Exhaust systems = 240 CFM Sensible load in space = 81,700 Btuh (Line 6 on N-1 form)

350 CFM is greater than 240 CFM. Occupants determine 350 CFM outdoor air requirement.

Approximate design TD = 18F Approx. supply CFM = 81700/ (1.1 x 18) = 4126 CFM

240 CFM is less than 10 percent of 4126 CFM Low exhaust CFM; OK to pressurize Summer AC/Hr 0.00 or (0.00 x 27000)/60 = 0 CFM Winter AC/Hr = 0.30 or (0.30 x 27000)/60 = 135 CFM

Ventilation required at OA damper = 350 CFM

Example 2, Neutral pressure Average construction; 27,000 Cu Ft volume Outdoor air required for occupants = 350 CFM Exhaust systems = 670 CFM Sensible load in space = 81,700 Btuh (Line 6 on N-1 form)

670 CFM is greater than 350 CFM. Exhaust systems determine 670 CFM outdoor air requirement

Approximate design TD = 18F Approx supply CFM = 81700/ (1.1 x 18) = 4126 CFM

670 CFM is approximately 16 percent of 4126 CFM Make up air is not required

Summer AC/Hr = 0.40 or (0.40 x 27000)/60 = 180 CFM Winter AC/Hr = 0.60 or (0.60 x 27000)/60 = 270 CFM

Ventilation required at OA damper = 670 CFM

TABLE 3 DOOR INFILTRATION CFM Per Door

TOTAL ENTRANCES & EXITS PER HOUR PER DOOR (TRAFFIC RATE) @ TYPE OF DOOR SEASON

None 5 10 20 50 100 200 Winter 240 280 310 380 590 940 1640

Double Door - Glass, Wood, or Metal 1/8" Crack No vestibule Summer 140 160 180 220 340 540 940 Winter 150 170 190 230 350 660 1310

Double Door- Glass, Wood, or Metal 1/8" Crack With vestibule Summer 90 100 110 130 200 380 750 Winter 110 120 130 140 180 250 400 Revolving Door Summer 70 75 80 90 110 150 220 Winter 20 60 90 160 370 - Single Door - Glass, Wood or Metal Summer 10 30 50 90 210 - Winter 500 1,000 1,500 - - - 8 x 8 Segmented O.H. Door Summer 300 600 900 - - - Winter 800 1,600 2,300 - - - 12 x 10 Segmented O.H- Door Summer 500 1,000 1,400 - - - Winter 1,200 3,000 4,800 - - - 12 x 20 Segmented O.H. Door Summer 700 1,800 2,900 - - -

Average occupancy TRAFFIC RATE = # of doors x average length of stay

Data extracted from ACCA Commercial Load Calculation manual N, table 13B Notes: (1) A "double door" is considered as one door, when the traffic rate is calculated, take value directly from table. (2) Values shown assume that the wind is blowing directly at the door and no other windows or doors are open.

TABLE 3 - EXAMPLE Winter Summer

CFM per double door 660 380 CFM per revolving door 250 150

Winter Summer

4 Double doors 2640 1520 2 Revolving doors 500 300

Department store, first floor; 30,000 Sq Ft Four sets of double doors with vestibules Two revolving doors Manager estimated Saturday occupancy = 300 Manager estimated length of stay = 1 Hr. 300 x 2 Traffic Rate = --------------------- = 100 6 x 1.00

Total door CFM 3140 1820

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TABLE 4- HEAT GAIN FROM OCCUPANTS APPLICATION DEGREE OF ACTIVITY SENSIBLE BTUH LATENT BTUH

Assembly hall, Church or School or Auditorium, Theater/Matinee Seated, at rest 210 140

Funeral Parlor Seat, very light work 230 190 Bank Standing, slow walk, light work 315 325 Barber shop Seated, very light work 230 190 Beauty parlor Seated, very light work 230 190 Bowling alley Bowling or medium heavy work 635-1,000 1,165-2,000 Conference room Moderately active work 255 255 Cocktail lounge, bar, tavern Standing, slow walk, light work 315 325 Department stores, retail shops Standing, slow walk, light work 315 325 Drug store; Pharmacist’s work area Sales area

Light bench work Standing, slow walk, light work

345 315

435 325

Dormitory Seated, very light work 230 190 Factory 3 mph walk; moderate work 565 1035 Food services: Dining room Cafeteria, short order, drive-in Kitchen

Seated, eating Seated, eating Light bench work

255 255 345

325 325 435

Garage, (repair) 3 mph walk; moderate work 565 1035 Gymnasium; Spectators Participants

Seated, very light work Bowling or medium heavy work

230 635-1,000

190 1,165-2,000

Hospitals or nursing homes Rooms and wards Operating room

Seated, very light work Light bench work

230 345

190 435

Hotel or motel; Bedroom or suite Lobby Conference room Ballroom

Seated, very light work Standing, slow walk, light work Moderately active work Moderate dancing

230 315 255 405

190 325 255 875

Laboratory Light bench work 345 435 Library Moderately active work 255 255 Locker rooms Standing, slow walk, light work 315 325 Office Private or semi private General Conference room Reception/lobby

Seated, very light work Moderately active work Moderately active work Standing, slow walk, light work

230 255 255 315

190 255 255 325

Recreation facilities; Pool room Racket ball or tennis courts Swimming pools (spectators)

Light bench work Sports or very heavy work Seated, very light work

345 1,000-2,000

230

435 1,150-3,000

190 Restaurant or cafeteria Dining Area Kitchen

Seated, eating Light bench work

225 345

325 435

Restrooms, public Seated, at rest 210 140 School rooms Classrooms Laboratory Shop

Seated, very light work Standing, slow walk, light work Light bench work

230 315 345

190 325 435

Notes: (1) Based on the normal percentage of men, women and children for the application listed. Source 1985 ASHRAE fundamentals

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TABLE 5 – OCCUPANCY ESTIMATES**

Occupancy OccupancyApplication 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

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TABLE 6a - 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

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TABLE 6b - PEAK CLIMATE CONDITIONS FOR MAKEUP AIR DEHUMIDIFICATION DESIGN DB GR/LB DB DB GR/LB DB 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


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TABLE 6c - PEAK CLIMATE CONDITIONS FOR MAKEUP AIR DEHUMIDIFICATION DESIGN DB GR/LB DB DB GR/LB DB 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


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TABLE 6d - PEAK CLIMATE CONDITIONS FOR MAKEUP AIR DEHUMIDIFICATION DESIGN DB GR/LB DB DB GR/LB DB STATE/CITY ELEV.


WINTER SUMMER MICHIGAN CONT'D St. Louis, Int'l Airport 564 2 138 85 Grand Rapids 804 0 126 81 Warrensburg. whiteman AFB 869 1 139 86 Hancock 1,079 -9 116 79 MONTANA Harbor Beach 600 9 113 82 Billings 3,570 -13 83 71 Jackson 1,001 -3 134 83 Bozeman 4,475 -20 83 69 Lansing 873 -3 127 81 Butte 5,545 -22 76 61 Marquette, Sawyer AFB 1,220 -11 113 77 Cut Bank 3,855 -21 77 67 Marquette/Ishpeming, A 1,424 -13 111 77 Glasgow 2,297 -22 91 74 Mount Clemens, Angb 581 3 131 83 Great Falls, lnt'l Airport 3,658 -19 81 69 Muskegon 633 3 122 80 Great Falls, Malmstrom AFB 3,527 -17 84 71 Oscoda, Wurtsmith AFB 633 0 120 80 Havre 2,598 -25 84 72 Pellston 719 -9 115 78 Helena 3,898 -18 80 68 Saginaw 669 0 132 83 Kalispell 2,972 -12 82 69 Sault Ste. Marie 725 -12 111 76 Lewistowm 4,167 -18 85 71 Seul Choix Point 591 0 106 74 Miles City 2,628 -19 95 76 Traverse City 623 -3 117 80 Missoula 3,189 -9 82 68 MINNESOTA NEBRASKA Alexandria 1,424 -20 123 82 Bellevue, Offutt AFB 1,047 -5 141 85 Brainerd, Pequot Lakes 1,280 -24 108 81 Grand Island 1,857 -8 127 82 Duluth 14 1 7 -21 110 77 Lincoln 1 188 -7 136 84 Hibbing 1,352 -25 116 78 Norfolk 1,552 -11 129 83 International Falls 1 184 -29 112 78 North Platte 2,785 -10 118 80 Minneapolis-St. Paul 837 -16 124 83 Omaha, Eppley Airfield 981 -7 136 85 Redwood Falls 1,024 -17 135 83 Omaha, Wso 1,332 -8 134 84 Rochester 1,319 -17 128 81 Scottsbluff 3,957 -11 102 76 Saint Cloud 1,024 -20 125 83 Sidney 4,304 -8 97 73 Tofte 791 -10 92 70 Valentine 2,598 -16 110 79 MISSISSIPPI NEVADA Biloxi, Keesler AFB 33 31 151 86 Elko 5,135 -5 84 68 Columbus, AFB 220 20 141 85 Ely 6,263 -6 82 64 Greenwood 154 20 148 86 Las Vegas, Int'I Airport 2,178 27 102 79 Jackson 331 21 142 84 Mercury 3,310 24 102 72 McComb 413 23 141 83 North Las Vegas, Nellis AFB 1 870 28 106 79 Meridian 308 21 139 84 Reno 4,400 8 77 69 Tupelo 361 18 137 83 Tonopah 5,427 7 83 67 MISSOURI Winnemucca 4,314 1 79 68 Cape Girardeau 341 6 141 86 NEW HAMPSHIRE Columbia 899 -1 137 85 Concord 344 -8 118 79 Joplin 981 3 137 85 Lebanon 597 -7 113 79 Kansas City 1,024 -1 137 86 Mount Washington 6,266 -23 90 58 Poplar Bluff 479 8 144 85 Portsmouth, Pease AFB 102 4 123 85 Spickard/Trenton 886 1 139 83 NEW JERSEY Springfield 1,270 3 134 84 Atlantic City 66 8 131 81


DR 01/07/03 16

TABLE 6e - PEAK CLIMATE CONDITIONS FOR MAKEUP AIR DEHUMIDIFICATION DESIGN DB GR/LB DB DB GR/LB DB STATE/CITY ELEV.


WINTER SUMMER NEW JERSEY CONT'D Hickory 1,188 18 133 80 Millvile 82 10 134 81 Jacksonville, New River Mcaf 26 23 145 86 Newark 30 10 127 81 New Bern 20 22 144 86 Teterboro 10 10 134 84 Raleigh/Durham 440 16 134 82 Trenton, McGuire AFB 135 11 132 83 Wilmington 33 23 146 85 NEW MEXICO Winston-Salem 971 18 134 81 Alamogordo, Holloman AFB 4,094 20 106 72 NORTH DAKOTA Albuquerque 53 15 13 98 68 Bismarck 1,660 -21 109 79 Carlsbad 3,294 19 121 76 Devils Lake 1,453 -23 108 78 Clayton 4,970 1 98 72 Forgo 899 -22 122 82 Clovis, Cannon AFB 4,295 10 114 75 Grand Forks, AFB 912 -20 118 81 Farmington 5,502 8 94 69 Minot, AFB 1,667 -21 109 80 Gallup 6,470 -1 94 65 Minot, lnt'I Airport 1,716 -20 106 78 Roswell 3,668 14 111 73 Wlliston 1,906 -24 103 78 Truth Or Consequences 4,859 22 94 71 OHIO Tucumcari 4,065 9 109 73 Akron/Canton 1,237 0 125 80 NEW YORK Cincinnati, Lunken Field 482 5 132 82 Albany 292 -7 118 79 Gleveland 804 1 125 82 Binghamton 1,631 -2 118 77 Columbus, Int'I Airport 817 1 128 82 Buffalo 705 2 118 78 Columbus, RickenbckrAFB 745 3 130 83 Central Islip 98 11 129 79 Dayton, Int'l Airport 1,004 -1 129 82 Elmira/Corning 955 -2 122 81 Dayton, Wright-Paterson AFB 823 1 136 84 Glens Falls 328 -10 127 81 Findlay 810 -2 132 81 Massena 213 -15 118 80 Mansfield 1,296 -1 128 81 New York, JFK Airport 23 11 125 80 Toledo 692 -2 129 82 New York La Guardia A 30 13 129 81 Youngstown 1,184 -1 122 80 Newburgh 492 6 130 82 Zanesville 899 2 130 82 Niagara Falls 591 4 125 81 OKLAHOMA Plattsburgh, AFB 236 -9 115 79 Altus. AFB 1,378 13 132 84 Poughkeepsie 167 2 126 82 Enid, Vance AFB 1,306 5 130 85 Rochester 554 1 123 81 Lawton, Fort Sill/Post Field 1 188 12 135 83 Rome, Griffiss AFB 505 -5 117 80 McAlester 771 10 141 85 Syracuse 407 -3 120 80 Oklahoma City, Tinker AFB 1,293 10 138 87 Watertown 325 -12 118 78 Oklahoma City, W. Rogers A 1,302 9 129 83 White Plains 440 7 128 80 Tulsa 676 9 137 87 NORTH CAROLINA OREGON Asheville 2,169 11 128 79 Astoria 23 25 81 69 Cape Hatteras 10 26 147 83 Eugene 374 21 83 74 Charlotte 768 18 130 82 Hillsboro 203 19 90 79 Cherry Point, Mcas 30 24 146 87 Klamath Falls 4,091 4 85 74 Fayetteville, Fort Bragg 243 22 139 84 Meacham 4,055 -9 67 66 Goldsboro, Johnson AFB 108 22 139 84 Medford 1,329 21 81 75 Greensboro 886 15 132 82 North Bend 13 30 76 65


DR 01/07/03 17

TABLE 6f - PEAK CLIMATE CONDITIONS FOR MAKEUP AIR DEHUMIDIFICATION DESIGN DB GR/LB DB DB GR/LB DB STATE/CITY ELEV.


WINTER SUMMER OREGON CONT'D Nashville 591 10 134 83 Pendleton 1,496 3 74 71 TEXAS Portland 39 22 83 75 Abilene 1,791 16 123 81 Redmond 3,077 1 71 68 Amarillo 3,606 6 112 76 Salem 200 20 81 75 Austin 620 25 137 81 Sexton Summit 3,842 21 76 70 Beaumont/Port Arthur 23 29 152 86 PENNSYLVANIA Beeville, Chase Field NAS 190 28 155 86 Allentown 384 5 123 81 Brownsville 20 36 146 83 Altoona 1,503 5 119 79 College Station/Bryan 322 22 141 82 Bradford 2,142 -6 116 75 Corpus Christi 43 32 148 84 Du Bois 1,818 0 116 76 Dallas/Fort Worth, Int'l A 597 17 132 82 Erie 738 2 122 79 Del Rio, Laughlin AFB 1,083 28 136 82 Harrisburg 308 9 130 82 EI Paso 3,917 21 114 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 948 2 120 79 Junction 1,713 19 130 80 Williamsport 525 2 125 80 Killeen, For Hood 1,014 20 137 81 RHODE ISLAND Kingsville, NAS 49 31 149 85 Providence 62 5 124 80 Laredo 509 32 138 82 SOUTH CAROLINA Lubbock Int'I Airport 3,241 11 120 77 Beaufort, Mcas 39 28 145 85 Lubbock Reese AFB 3,337 11 122 78 Charleston 49 25 145 84 Lufkin 289 23 143 83 Columbia 226 21 134 82 Marfa 4,859 15 110 72 Florence 148 23 142 85 McAlIen 108 34 146 83 Greer/Greenville 971 19 130 81 Midland/Odessa 2,861 17 120 76 Myrtle Beach, AFB 26 25 150 87 San Angelo 1,909 20 123 80 Sumter, Shaw AFB 243 24 136 83 San Antonio, Int'I Airport 794 26 139 81 SOUTH DAKOTA San Antonio, Kelly AFB 689 27 145 83 Chamberlain 1,739 -13 124 84 San Antonio, Randolph AFB 761 27 138 82 Huron 1,289 -17 126 84 Sanderson 2,838 23 123 79 Pierre 3 742 -14 116 81 Victoria 118 29 145 83 Rapid City 3,169 -11 104 76 Waco 509 22 135 83 Sioux Falls 1,427 -16 127 84 Wichita Falls, Sheppard, AFB 1,030 14 129 82 TENNESSEE UTAH Bristol 1,519 9 125 81 Cedar City 5,623 2 93 68 Chattanooga 689 15 134 82 Ogden, HiIl AFB 4,787 6 91 72 Crossville 1,880 7 134 80 Salt Lake City 4,226 6 92 73 Jackson 433 12 140 85 VERMONT Knoxville 981 13 131 82 Burlington 341 -11 115 79 Memphis 285 16 143 87 Montpelier/Barre 1,165 -10 111 78


DR 01/07/03 18

TABLE 6g - PEAK CLIMATE CONDITIONS FOR MAKEUP AIR DEHUMIDIFICATION DESIGN DB GR/LB DB DB GR/LB DB STATE/CITY ELEV.


WINTER SUMMER VIRGINIA Cody 5,095 -14 76 70 Fort Belvoir 69 12 139 86 Gillette 4,035 -16 88 73 Hampton, Langley AFB 10 21 141 85 Lander 5,558 -14 81 69 Lynchburg 938 12 129 81 Rock Springs 6,759 -9 78 62 Newport News 43 18 139 84 Sheridan 3,967 -14 88 71 Norfolk 30 20 135 83 Worland 4,245 -22 94 75 Oceana, NAS 23 22 139 85 Quantico, Mcas 13 16 136 87 Richmond 177 14 737 84 Roanoke 1,175 12 123 80 Sterling 322 9 130 83 Washington, National A 66 15 137 83 WASHINGTON Bellingham 157 15 81 73 Hanford 732 5 73 72 Olympia 200 18 81 73 Quillayute 203 23 76 65 Seattle, lnt'l Airport 449 23 78 71 Spokane, Fairchild AFB 2,461 1 77 68 Stampede Pass 3,967 3 70 63 Tacoma, McChord AFB 322 18 79 71 Walla Walla 1,204 4 82 74 Wenatchee 1,243 3 78 75 Yakima 1,066 4 78 75 WEST VIRGINIA Bluefield 2,858 5 120 75 Charleston 981 6 129 81 Elkins 1,998 -2 121 78 Huntington 837 6 132 82 Martinsburg 558 8 130 81 Morgantown 1,247 4 124 79 Parkersburg 860 4 132 82 WISCONSIN Eau Claire 906 -18 125 82 Green Bay 702 -13 124 82 La Crosse 663 -14 132 83 Madison 866 -11 126 83 Milwaukee 692 -7 127 83 Wausau 1 201 -15 120 79 WYOMING Big Piney 6,969 -22 69 60 Casper 5,289 -13 85 66 Cheyenne, Warren AFB 6,142 -7 90 66


DR 01/07/03 19

SYSTEM SPECIFICATIONS

GENERAL Furnish and install an indoor air dehumidifier. Performance and specifications shall meet or exceed that shown on the equipment schedule.

Units shall be manufactured by Nautica Dehumidifiers, Inc., 200-19 East Second Street, Huntington Station, NY 11746. (www.nauticadehumid.com). Alternate manufacturers must meet or exceed energy efficiency of specified unit and must be evaluated by engineer twelve days prior to bidding.

PRINCIPLE OF OPERATION/DESIGN INFORMATION The unit shall be designed to treat recirculated air by filtering, removing moisture, and reducing the relative humidity level of the discharge air in summer and preheating in winter.

Indoor air dehumidifier shall be Nautica model ________. System efficiency shall be a minimum of 6.0 pounds of condensed water per KwH of compressor power consumption. Dehumidifier air volume shall not exceed 45 cfm per pound of condensed moisture per hour. Standard rating conditions are: Inlet air 80°F / 60% RH.

Dehumidifier shall be capable of removing ____ pounds of moisture per hour with inlet conditions of ____ DB and _____ % RH. Dehumidifier air volume shall be ______ cfm.

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 DHRxx: supply fan, MSP® dehumidifying coil, heater, controls, condensing unit.

Modular indoor 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, controls, and split condensing unit. Unit will require multiple electrical connections. Disconnect switches to be furnished by Division 16 contractor.

UNIT CONSTRUCTION Base shall be fabricated of minimum 14-gauge mill galvanized steel floor-sheet continuously welded to side channels and suitably braced on the underside to carry the loading presented by internal components. Base shall be insulated on both the underside and in the web area of the side channels. Insulation shall then be covered with an 18-gauge mill galvanized cover sheet.

Units for outdoor applications shall have painted exterior. Roof shall be pitched ¼” per foot for drainage. Units for indoor applications shall have unpainted galvanized finish.

Cabinet shall be double wall (Pick one – 1” or 2”), constructed of 20-gauge galvanized steel exterior with 20-gauge galvanized steel interior skin. Insulation shall be sandwiched between interior and exterior surfaces. All interior wall openings and seams that could allow passage of humid air into the insulated space shall be double-sealed to prevent the possibility of internal wall condensation. Access shall be provided for inspection and service access to all components.

Insulation shall be 1" thick, 3-pound density, fiberglass and shall comply with NFPA-90A for flame spread, smoke development and fuel contribution.

DR 01/07/03 20

MSP® DEHUMIDIFYING COIL Unit shall be furnished with a MSP® 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. The heat transfer media shall be constructed of 3000 series aluminum. To ensure complete drainage of condensate and no standing water, heat exchangers shall be positioned so that condensate flows downward through the heat exchanger, at an angle between vertical and 45 degrees. Pressure drop through air-to-air heat exchangers shall be no greater than 0.25” Wc, with 77% sensible efficiency, equal mass flow rates, 70 deg Fahrenheit temperature difference and 50% RH on the condensing pass

Cooling coil shall be ARI-rated direct expansion or chilled water type with 3/8”, ½”, or 5/8” OD copper tubes, aluminum fins. Air shall pass through a minimum of 6 rows of coil. Fin spacing shall not exceed 12 fins per inch. Coil position shall be arranged to ensure that each circuit is exposed to equal loads. DX coils shall have pressure-type brass distributors and solder connections shall be provided. Coil face velocity shall not exceed 500 FPM. DX coils shall be provided with externally equalized thermostatic expansion valve for maximum cooling effectiveness.

Condensate drain pan shall be insulated heliarc welded minimum 18-gauge stainless steel type 304. Pan shall be pitched to ensure no standing water.

Thermostatic expansion valve shall be provided for maximum cooling effectiveness.

FAN Fans shall be licensed to bear the AMCA seal and tested in accordance with AMCA Standard 210. Fans shall be as rated on the equipment schedule. Fans shall have heavy gauge housings and wheels, and shall be both statically and dynamically balanced. Fan assembly shall be isolated from the unit casing with vibration isolators. Outlet of fan shall be separated from the unit casing with a flexible discharge connection. V-belt drive shall be furnished with a service factor of 1.2 times the motor horsepower. Supply fans delivering air volumes of 3000 cfm or above shall be backward inclined centrifugal type.

HEATER (PICK APPROPRIATE PARAGRAPH)

Electric heating coil shall be designed for direct exposure to the airstream. Heater shall be open wound helically coiled nickel/chrome alloy elements set in galvanized steel frames with sealtite insulators and stainless steel terminations. Contactors and protective devices shall be included.

Heater shall be indirect-fired gas type with multiple stages. Heat exchanger and burner shall be stainless steel for 100% outside air duty.

Provide hot water coil for heating supply air. Installing contractor shall provide hot water control valve and piping accessories.

CONDENSING UNIT (PICK APPROPRIATE PARAGRAPH)

Provide air-cooled condensing unit. Unit shall be provided with 5-year compressor parts only warranty. Condensing unit capacity shall be as specified on the schedule. Unit shall be factory charged. Compressor electrical circuit shall be equipped with overload protection, high and low pressure safety controls.

Provide packaged water-cooled condensing unit. Unit shall be provided with 5-year compressor parts only warranty. Condensing unit capacity shall be as specified on the schedule. Unit shall be factory charged. Compressor electrical circuit shall be equipped with overload protection, high and low pressure safety controls.

CONTROL SYSTEM Control system shall be designed to optimize energy consumption and provide precise control of humidity. Control system shall be complete with humidistat and freeze control. Panel shall include unit controller to cycle compressor(s) for dehumidification and to stage heater.

DR 01/07/03 21

AIR COOLED SPLIT DEHUMIDIFIER SELECTION CHART MODEL CAPACITY AIRFLOW POWER CONDENSING UNIT MRE *DRIA-4A LB/H SCFM KW NOMINAL TONS LB/KWH48-240A 180.0 6,720 26.00 20.0 6.9232-180A 130.5 4,480 18.68 15.0 6.9928-150A 106.6 3,920 15.68 12.5 6.8024-120A 92.1 3,360 12.80 10.0 7.2016-090A 65.6 2,240 8.91 7.5 7.3615-072A 52.3 2,100 7.14 6.0 7.3210-060A 40.3 1,400 5.97 5.0 6.7509-048A 33.8 1,260 4.97 4.0 6.8008-042A 30.1 1,120 4.24 3.5 7.1106-036A 25.3 1,000 3.84 3.0 6.5806-030A 22.9 1,000 3.11 2.5 7.38

* Moisture Removal EfficiencyFor use in indoor swimming pools, specify "coated units"

SPECIFY “COATED” UNITS FOR INDOOR POOLS AND OTHER CORROSIVE ENVIRONMENTS.

DR 01/07/03 22

AIR COOLED SPLIT PIPING

MSPTM

COIL

SUC

TIO

N L

INE

LIQ

UID

LIN

E

DR 01/07/03 23

AIR COOLEDPACKAGED DEHUMIDIFIER SELECTION CHART MODEL CAPACITY AIRFLOW POWER MRE *DRIP-4A LB/H SCFM KW LB/KWH48-240** 189.4 6,720 22.84 8.2932-156** 122.8 4,480 14.63 8.3924-121** 95.5 3,360 10.95 8.7216-81** 63.6 2,240 7.39 8.6112-56** 43.6 1,680 6.23 7.0010-49** 38.6 1,400 5.51 7.009-44** 34.8 1,260 4.76 7.318-41** 32.7 1,120 4.64 7.056-30** 23.3 1,000 3.22 7.244-22** 17.3 1,000 2.56 6.75

** Insert Heat rejection configuration (Figures 1-4)* Moisture Removal Efficiency

For use in indoor swimming pools, specify "coated units" SPECIFY “COATED” UNITS FOR INDOOR POOLS AND OTHER CORROSIVE ENVIRONMENTS.

DR 01/07/03 24

HEAT REJECTION OPTIONS FOR PACKAGED UNITS FIGURE 1 - WATER REJECTION (W)

FIGURE 2 - WATER/INDOOR REJECTION

FIGURE 3 - INDOOR REJECTION (A)

FIGURE 4 - OUTDOOR/INDOOR REJECTION

COIL

COMPRESSOR

MSP®

COIL

AIR COOLEDCONDENSER

COIL

COMPRESSOR

MSP®

COIL

COIL

COMPRESSOR

MSP®

COIL

CONDENSER

POOL WATERHEATING CIRCUIT

COIL

COMPRESSOR

MSP®

COIL

WATERLOOP

Documents

Indoor Air Dehumidifier Design Manual