Attachment J-1G - WCC PPD-512-001 - HVAC DCM A00002.pdf

WCC Technical Specification Section 512 Addendum i

Title:

ATTACHMENT J-1G: HEATING, VENTILATION AND AIR

CONDITIONING (HVAC) DESIGN CRITERIA MANUAL

(DCM)

09 July 2021

WATERWAY COMMERCE CUTTER (WCC)

Amendment 00002

DISTRIBUTION STATEMENT A: Approved for public release; distribution is unlimited.

512 Addendum ii

REFERENCES

[1] Waterway Commerce Cutter Performance Specifications (PS)

[2] NAVSEA Design Practices Manual (DPM), T9500-AA-PRO-130, Chapter 510

[3] NAVSEA 0938-LP-018-0010, Heating, Ventilation and Air Conditioning Design Criteria Manual for

Surface Ships of the United States Navy, 29 March 1991

[4] Society of Naval and Marine Engineers (SNAME) Technical & Research (T&R) Bulletin 4-16, Recommended Practices for Merchant Ship HVAC Design Calculations, 2015

[5] Society of Naval and Marine Engineers (SNAME) Technical & Research (T&R) Bulletin 4-7, Thermal

Insulation Report

[6] American Society of Heating, Refrigerating and Air Conditioning Engineers (ASHRAE) Handbook –

Fundamentals (2009)

[7] Industrial Ventilation - A Manual of Recommended Practice by the Committee on Industrial Ventilation, P.O Box 16153, Lansing, Michigan, 48901.

512 Addendum iii

TABLE OF CONTENTS

REFERENCES .............................................................................................................................................................. ii

TABLE OF CONTENTS .............................................................................................................................................iii

1 INTRODUCTION

2 BASIC DATA

2.1 Weather Air and Seawater Design Temperatures

2.2 Transmission

2.2.1 Cooling season

2.2.2 Heating season

2.2.3 Compartment temperatures

2.2.4 Solar radiation

2.3 Heat Transfer Coefficients

2.3.1 General

2.3.2 Applicability

2.4 Lighting

2.4.1 Cooling season

2.4.2 Heating season

2.4.3 Quantities

2.5 Personnel

2.5.1 Cooling season

2.5.2 Heating season

2.6 Equipment

2.6.1 Cooling season

2.6.2 Heating season

2.7 Replenishment Air

3 VENTILATION DESIGN (GENERAL)

3.1 Pre-Cooling

3.2 Limiting Design Temperature

3.4 Infiltration Load

3.3 Rate of Change

3.4 Pre-heat

3.5 Special Requirements

4 AIR CONDITIONING DESIGN

4 6 .1 Heat loads

4.2 Selection – Cooling Coils

4.3 Selection – Air Handling Assembly

4.4 Selection – Fan-Coil Unit

4.5 Temperature Rise (∆T) Due to Fan Heat

4.6 Mix Temperature (DB) – Return and Weather Air

4.7 Bypass Air

4.8 Constant Summer Reheat

4.9 Space Air Quantities

512 Addendum iv

5 DESIGN CRITERIA SHEET EXPLANATION

5.1 Insulation

5.2 Space Treatment

5.3 Design Temperature

5.4 Design Relative Humidity

5.5 Assumed Temperature

5.6 Rate of Change

5.7 Applicable Spaces

5.8 Special Requirements

5.9 General Notes

Design Criteria Sheet No.2 Design Criteria Sheet No.3 Design Criteria Sheet No.4 Design Criteria Sheet No.4I Design Criteria Sheet No.5 Design Criteria Sheet No.6 Design Criteria Sheet No.6B Design Criteria Sheet No.7A Design Criteria Sheet No.7B Design Criteria Sheet No.8 Design Criteria Sheet No.12A Design Criteria Sheet No.12E Design Criteria Sheet No.12K Design Criteria Sheet No.13I Design Criteria Sheet No.13 Design Criteria Sheet No.15

Index of Spaces

PPD 512-01 Page 1 of 37

1 INTRODUCTION

This Design Criteria Manual (DCM) was developed from references [1] through [7] and contains criteria and summaries of acceptable methods for the development of the Heating, Ventilation, and Air Conditioning (HVAC) systems for the WCC.

2 BASIC DATA

2.1 Weather Air and Seawater Design Temperatures

Cooling Season Heating Season

Air 100°F Dry Bulb / 83°F Wet Bulb -10°F Dry bulb

Seawater 90°F 32°F

Table 2-1: Weather Air and Seawater Design Temperature Requirements

2.2 Transmission

2.2.1 Cooling season

Heating effect of adjacent spaces shall be calculated. Cooling effect of adjacent spaces shall not be considered unless the lower temperatures are maintained by air-conditioning or refrigeration equipment or otherwise specified in the space design criteria sheets. Except for heat balance checks and as noted herein, cooling effect of weather boundaries shall not be considered.

2.2.2 Heating season

The heat loss through all boundaries shall be included. Heat gain through boundaries shall be deducted if the higher temperature is mechanically maintained by the heating system.

2.2.3 Compartment temperatures

Design temperatures for air-conditioned and ventilated spaces are given in the design criteria sheets. Temperatures for spaces, which do not have a design temperature, shall be estimated if these spaces are adjacent to compartments having a design temperature and requiring a heat transmission calculation. These estimates, if not given in the various “Design Criteria” as assumed temperatures, are usually made by a heat balance calculation or by inspection. They shall be based on the applicable combination of solar effect, weather or sea boundaries, insulation, and adjacent space temperatures and compartment function.

2.2.4 Solar radiation

The effect of solar radiation on weather metal boundaries shall be in accordance with reference [4] and assumed to produce surface temperatures during cooling season as follows: 145°F for deck and 125°F for vertical boundaries.

The effect of solar radiation on weather glass boundaries shall be in accordance with reference [4] and assumed to produce surface temperatures during cooling season as follows: 160 BTUH/ft2 for glass.

The heat transfer resulting from these temperatures shall be considered for that weather boundary showing the greatest heat gain. Solar effect for other weather boundaries shall be neglected but transmission load shall be figured on

PPD 512-01 Page 2 of 37 weather air temperature. Solar effect shall not be considered during heating season.

2.3 Heat Transfer Coefficients

2.3.1 General

Heat is a form of energy that is transferred across a boundary because of temperature difference by means of convection, conduction and radiation. These three effects shall be evaluated and combined into a single overall coefficient of transmittance U. Reference [5] provides data for selecting U values for different arrangements of insulated and uninsulated bulkheads and decks. Fibrous glass-board U-values may be used for polyamide insulation.

Care should be taken to ensure the number of insulation types are kept to a minimum to drive commonality across the vessel. Insulation selections shall be appropriate for the boundaries based on the expected temperature differentials, and shall not exceed the allowable transmission coefficient “U”values specified in Table 2.2.

Temperature Differential (°F) Maximum “U” Value (BTUH/ft2/°F)

0°F - 15°F 1.75 16°F - 30°F 0.37 31°F - 50°F 0.26 51°F - 75°F 0.16 76°F - 90°F 0.10

91°F+ 0.08

Table 2.2 – Maximum Heat Transfer Coefficients (U)

Calculations for U shall be divided into two groups: surface-to-air and air-to-air.

Surface-to-air coefficients evaluate the effect of heat transfer from surface temperatures on one side of a boundary to the air temperatures on the other side.

Air-to-air coefficients apply to all other conditions. These values shall be further subdivided into classifications of inside air to inside air and weather air to inside air.

Reference [5] provides selected values, which are an average of values for the entire range, used in heating and cooling load calculations.

2.3.2 Applicability

Insulation requirements shall be in accordance with WCC Specification 635. For values not covered in reference [5], ASHRAE Publication “Handbook of Fundamentals” shall be used. For fire and acoustic insulation, use equivalent thickness of thermal insulation.

2.4 Lighting

2.4.1 Cooling season

Heat gain from lighting units shall be in accordance with reference [4] and shall be used in computation of heat loads for all compartments, except ventilated compartments calculated on a rate of change basis.

2.4.2 Heating season

Heat gain from lighting units shall be deducted from space heating requirements for all heated compartments except

PPD 512-01 Page 3 of 37

Pilot House, Messrooms, and staterooms.

2.4.3 Quantities

The actual wattage of lighting in a space shall be used if known. The total wattage in spaces using fluorescent lighting units shall include the ballast loss in addition to wattage of tubes. Present twin-tube 20 W fluorescent fixtures have a ballast loss of 2 x 4.5 = 9 W, making the total loss for the fixture 49 W. If actual wattage is not known, heat gains from lighting units are based on lighting requirements as noted in WCC Specification 330 Conversions from foot-candles to BTUH/ft2 of deck area (under) are provided in Table 2-2.

Foot-candles 3 7 14 21 28 42

Fluorescent - 2.8 5.0 7.0 8.9 15.0

LED light bulbs- BTUH/sq. ft

- 1.12 2.0 2.8 3.6 6.0

LED light tubes- BTUH/sq. ft

- 1.4 2.5 3.5 4.5 7.5

Table 2-3: Conversions from foot-candles to BTUH/sq. ft.

Note 1. BTUH/sq,ft, loads are based on actual maintained lighting levels.

Note 2. LED light bulbs use roughly half the wattage of fluorescent lighting, about 6 watts of power versus 14 watts of power for a compact flourescent lamp (CFL).

Except – Use loads for staterooms as follows:

SPACE Incandescent Florescent

Stateroom (Single) 680 BTUH 2.4 BTUH/sq. ft. Area + 150 BTUH

Stateroom (Dept Head) 1200 BTUH 4.3 BTUH/sq. ft. Area + 150 BTUH

Stateroom (Double) 1020 BTUH 2.4 BTUH/sq. ft. Area + 230 BTUH

Stateroom (Triple) 1360 BTUH 2.4 BTUH/sq. ft. Area + 310 BTUH

Table 2-4: Assumed Lighting Loads

2.5 Personnel

2.5.1 Cooling season

Both sensible and latent heat from personnel at maximum design occupancy shall be be in accordance with Table 2- 5 and used in computation of heat loads of air-conditioned spaces. For messing facilities, add 30 BTUH sensible and latent per person eating as an allowance for heat dissipation from food.

Occupancy for staterooms shall be based on the number of sleeping accommodations. For all other compartments, use maximum seating arrangements when calculating personnel loads.

PPD 512-01 Page 4 of 37

Heat gain from personnel shall not be considered in ventilated spaces.

Table 2-4 provides heat dissipation from personnel, per person, for various compartment types. The heat gain data has been extracted from Figure 3-9 in Reference [2], and has been measured for a dry bulb temperature of 78°F.

Space Sensible Heat, BTUH Latent Heat, BTUH Offices, Staterooms, Cabins, and Electronic Spaces

265 335

Worksing Spaces, Messrooms and General Workshops

315 485

Table 2-5: Heat Dissipation from Personnel

2.5.2 Heating season

Sensible and latent heat gains from personnel in air conditioned compartments shall not be considered in compartment heating season calculations.

2.6 Equipment

2.6.1 Cooling season

Heat gain from all known heat producing equipment shall be based on actual equipment data from the OEM. If this information is not available reference [6] shall be utilized to estimate heat gain from equipment with an estimate for miscellaneous items within a compartment, including passages, making allowance for operating load factors of such equipment. The load factor shall consider simultaneous use of combinations of equipment and whether equipment is used intermittently or continuously.

2.6.2 Heating season

The heating effect of equipment shall be considered only in compartments as specified in Design Criteria Sheets.

Otherwise, equipment shall be considered secured.

2.7 Replenishment Air

Replenishment air for air-conditioning systems shall be based on the following rates, for the total design occupancy of the compartments served by the system:

Class Z systems - 5 CFM per man

Class W systems - 10 CFM per man

These rates shall be increased only to meet the 75 CFM minimum branch requirements or to balance exhaust requirements of spaces such as galleys, laundries, and sanitary spaces. Air-conditioning systems serving spaces normally unmanned shall receive 75 CFM (minimum) of replenishment air. Sensible and latent heat content of replenishment air over compartment design temperature shall be included in cooling loads for all systems. Difference in sensible heat content between replenishment air and compartment design ambient shall be included in heating loads for all systems.

The minimum normal mode quantity for fan coil unit replenishment air terminals is 35 CFM.

PPD 512-01 Page 5 of 37

3 VENTILATION DESIGN (GENERAL)

3.1 Pre-Cooling

Ventilation supply systems for the Engine Rooms, Auxiliary Machinery Room, Lockers, Storerooms, and replenishment air to air conditioning systems shall utilize cooling coils for pre-cooling supply weather air only if cooling load calculations determine that space design temperature cannot be maintained with untreated ventilation air.

3.2 Limiting Design Temperature

If a limiting design temperature is specified for a compartment, calculate cooling season supply air quantity by the following formula:

𝑄𝑄 =

𝐻𝐻𝑠𝑠

𝐾𝐾 × ∆𝑇𝑇

Where:

Q = Air quantity – CFM

HS= Sensible heat gain to compartment – BTUH ∆T=Difference between compartment and weather air design temperatures in degrees Fahrenheit dry bulb K = 1.044 when calculating supply air during cooling season K = 1.24 when calculating supply air during heating season without preheat K = 1.14 when calculating supply air during heating season with preheat at 40°F K = 1.12 when calculating supply air during heating season with preheat at 50°F

3.4 Infiltration Load

Infiltration shall be applied for spaces which are not pressurized and have direct access to the weather where it is common practice to have doors open when navigating near land. All other outside doors are considered as closed.

The sensible heat component of infiltration is included in the cooling and heating loads. The latent heat component is only included in the A/C cooling loads. The latent heat gain is not considered for heating, except when humidification is required by the specifications.

3.3.1 Infiltration Heat Gain (Loss)

Infiltration heat gains or losses are calculated using the following equations:

Total

Heat q=60×Q×(ho − hr) v

Sensible Heat

Cooling Season: qs =1.04xQx∆T

Heating Season: qs =1.24xQx∆T

Latent Heat Cooling Season: ql = q - qs

PPD 512-01 Page 6 of 37 q = total heat [Btu/hr] qs = sensible heat [Btu/hr] ql =latent heat [Btu/hr] ho = enthalpy of outdoor air [Btu/lb/°F] hr = enthalpy of room air [Btu/lb/°F] Q = airflow quantity [CFM] 60 = conversion factor ΔT = change in temperature [°F]

ΔT is the difference between design outdoor dry bulb temperature and design room dry bulb temperature, and the constants 1.04 and 1.24 are the HVAC conversion factors from Section 3.2.

For spaces that are not pressurized, the infiltration rate of change shall be 60 minutes for cooling calculations and 10 minutes for heating calculations. The dimensions used in calculating the room volume are the finished deck heights and horizontal dimensions inside joiner linings and bulkheads.

If the space is pressurized, the infiltration rate of change shall be 120 minutes for cooling calculations and 20 minutes for heating calculations.

3.3 Rate of Change

If a rate of change is specified for a ventilated space, air quantity shall be calculated by the following formula:

𝑸𝑸 = 𝑽𝑽

𝑹𝑹�

Where:

Q=Air quantity - CFM

V=Gross volume of space – ft3

R=Specified rate of change – minutes

3.4 Pre-heat

Ventilation supply air to all spaces requiring pre-heat shall be heated to a temperature of 40°F dB minimum, 50°F dB maximum, unless a specific pre-heat temperature is required by the design criteria sheets. Additionally, preheat needs shall be assessed based on operating modes of equipment, such as number of engines running or diesel engines taking combustion air from the compartment, to ensure that compartment design temperature requirements can be met.

3.5 Special Requirements

Special requirements applicable to individual spaces shall be as specified in the Design Criteria Sheets. For additional information on controls and fan selection, see WCC Specification 512.

4 AIR CONDITIONING DESIGN

4.1 Heat loads

The compartment heat loads, sensible heat factors and replenishment air quantity are determined from the cooling load calculations.

4.2 Selection – Cooling Coils

Cooling coils shall be selected as follows:

PPD 512-01 Page 7 of 37

1) Chilled water entering temperature is 45°F.

2) Air quantity in CFM shall be in accordance with the velocity limitations of WCC Specification 512 and manufacturer data for the required load and coil entering air conditions (DB, WB).

3) Cooling coils selection shall be in accordance with the manufacturer cooling coil performance data.

4) Chilled water rate shall be determined from cooling coil selection criteria.

4.3 Selection – Air Handling Assembly

Air-handling assemblies are to be selected in accordance with the manufacturer’s ratings, instructions, and recommendations. If such manufacturer's information is not available, then selection shall be made as follows:

2) Air quantity in CFM and size of fan-coil assemblies shall be determined from manufacturer data for the required coil load (BTUH) and coil entering air conditions (DB, WB).

3) Chilled water rate shall be determined from air handling assembly selection criteria.

4) Adequacy of selections shall be confirmed by the unit manufacturer's ratings, instructions and recommendations when they become available.

4.4 Selection – Fan-Coil Unit

Fan coil units shall be selected in accordance with the manufacturer's ratings, instructions and recommendations. In addition to such manufacturer's information, the following information shall be used:

2) Chill water rate shall be determined from fan coil unit selection criteria.

4.5 Temperature Rise (∆T) Due to Fan Heat

The ∆T (DB) for these loads is calculated from the formula:

∆𝑇𝑇 =

𝑞𝑞𝑆𝑆

1.08 × 𝑄𝑄𝐴𝐴

∆T = Dry Bulb temperature rise - °F qS = Sensible heat - BTUH, from Equations 3-8 and 4-1, in Reference [4] QA = Air quantity - CFM

4.6 Mix Temperature (DB) – Return and Weather Air

The mix temperature (DB) of air returning to the cooling coil(s) and weather air at design conditions is calculated by the following formula:

PPD 512-01 Page 8 of 37

𝑇𝑇𝑀𝑀 =

(𝑇𝑇𝑊𝑊 × 𝑄𝑄𝑊𝑊) + (𝑇𝑇𝑅𝑅 × 𝑄𝑄𝑅𝑅)

𝑄𝑄𝑊𝑊 + 𝑄𝑄𝑅𝑅

TM = Mixture Temperature (DB) - °F TW = Weather Air Temperature (DB) - °F TR = Return Air Temperature (DB) - °F QW = Weather Air Quantity - CFM QR = Return Air Quantity - CFM

The same formula applies to any air mixture by the substitution of the applicable temperatures and air quantities.

4.7 Bypass Air

The total air quantity of an air conditioning system can be increased by bypassing a quantity of return air around the cooling coil. The total air quantity of the system is equal to the required air quantity for the system plus the fan bypass air quantity. The necessity of using bypass air is to add air to a system to suit fan selection and/or to satisfy compartment return air requirements.

For pre-cooled ventilation systems, a cooling coil may be installed downstream of the fan to pre-cool a portion of the ventilation air. The remaining portion of the ventilation air shall be by-passed around the coil and then mixed with the pre-cooled air. Pre-cooling ventilation air lowers the temperature of the supply air to ventilated compartments.

Lowering the temperature of the ventilation air will increase temperature differential between the ventilation air and the ventilated space design temperature. The temperature differential will result in a lesser amount of ventilation air.

4.8 Constant Summer Reheat

If an individual compartment room slope results in a room condition above the maximum room relative humidity, constant summer reheat shall be added so that the resultant relative humidity in the space is below the maximum relative humidity in accordance with reference [4].

4.9 Space Air Quantities

Individual space air quantities are determined by apportioning total system air quantity among the spaces as follows:

𝑠𝑠𝑠𝑠𝑠𝑠𝑠𝑠𝑠𝑠 𝑠𝑠𝑎𝑎𝑎𝑎 𝑞𝑞𝑞𝑞𝑠𝑠𝑞𝑞𝑞𝑞𝑎𝑎𝑞𝑞𝑞𝑞 = 𝑄𝑄𝑇𝑇 �

𝐻𝐻𝑆𝑆𝑅𝑅

𝐻𝐻𝑆𝑆𝑅𝑅𝑇𝑇� �

Where:

QT = Total system air quantity - CFM HSR = Space sensible load – BTUH HSRT = Sum of space sensible loads – BTUH Individual space air quantities are calculated after the cooling coil and the air conditioning fan are sized.

5 DESIGN CRITERIA SHEET EXPLANATION

These sheets contain data and requirements to be followed in the design of air-conditioning, ventilation and heating

PPD 512-01 Page 9 of 37 systems serving spaces to which these sheets are applicable. Where multiple functions are combined in a single space, the design of that space shall be such that the design criteria for all the component functions are met or bettered. The symbol “---” is used on the design criteria's sheets where there are no criteria specified. The following is an explanation of the design criteria items enumerated on the Design Criteria Sheets (item numbers correspond to those on the Design Criteria Sheets).

5.1 Insulation

For thermal insulation requirements, see Table 5-1. These categories define the thickness and extent of insulation required for compartment boundaries based on the design and assumed temperatures of adjacent compartments. Other insulation treatments may be considered provided the U-value is less than that of the treatment required in Table 5-1.

The values of Table 5-1 define the SNAME 4-7 insulation type required.

Table 5-1: Thermal Insulation Requirements For WCC Compartments

5.2 Space Treatment

a. Supply

b. Exhaust/Return

c. System Classification

d. Closure Classification

Space treatment required (A/C or ventilation) is indicated by the application of certain system requirements (a, b, c,

d) under the applicable type of system. The following designations listed under the applicable system(s) indicate the

COLUMN 0

TEMPERATURES AND

DETAIL REQUIREMENTS

CATEGORY

0 0 0 0 0 0 0 0 0 0 0 52 52 52 52 0 22 0 0 0

52 0 0 0 0 0 0 0 0 0

0 0 0 22 22 0 22 22 22 22

52 0 0 0 0 0 0 0 0 0 0 0 0 0 52 22 22 22

52 22 0 0 0 0 0 0 0 0 0 0 0 0 0 22 52 22 22 22

52 22 0 0 0 0 0 0 0 0 0 0 0 22 112 52 22 22

*INSULATION SHALL BE INSTALLED ON THE PLANE SURFACE SIDE IN WAY OF BULKHEADS, AND ON THE UNDERSIDE

OF DECKS

106° - 119° B

B

22*

4 95° AND BELOW NON A/C D

5 A/C SPACES F 22*

1 120° AND ABOVE A

3 96° - 105° C

A C D F

B A

L L

A S

T T

A N

K S

WEATHER SEA

H O

R

IZ

O N

T A

L

(B

R E

M E

T A

L

V E

R T

IC

B

O V

E L

.S .W

.L

V E

R T

IC

E

L O

W L

.S .W

.L

9 10

L

IN

E

TYPE OF COMPARTMENT

V O

ID

S

A T

S H

E

O V

E L

.S .W

.L

BOUNDARIES

THERMAL INSULATION REQUIREMENTS - REFER TO SNAME TR BULLETIN 4-7 INSULATION TYPES

ROOM SIDE BOUNDARIES ADJOINING SIDE BOUNDARIES

1 3 4 5 6 7 8

PPD 512-01 Page 10 of 37 type of supply and exhaust (or return for air-conditioning systems) to be provided these space(s):

M = Mechanical (fan) N = Natural NM = Natural or Mechanical (preferred type listed first) M/N = Combination of Mechanical and Natural

System and closure classifications shall be as follows:

Classification Operation W Fan operating or closure open under all conditions of ship operation (secured and closed respectively on to prevent the spread of damage).

Z Fan normally operating and closure normally open but secured and closed respectively during General Quarters.

Table 5-2: Damage Control Classification

5.3 Design Temperature

Design temperature, if noted, indicates the maximum cooling season temperature and minimum heating season temperature allowable under design weather temperatures, unless otherwise noted. The symbol “P” under heating season column indicates that only preheated air is required. Whether these temperatures are to be maintained by air-conditioning or ventilation systems is indicated in item 2. In ventilation systems, the Design Temperature is equal to the temperature of the air entering the compartment plus the allowable Temperature Rise. All temperatures are given in degrees Fahrenheit.

5.4 Design Relative Humidity

Design relative humidity indicates maximum allowable percentage of relative humidity, unless specific tolerances are otherwise noted. Relative humidity reduction shall be accomplished in the applicable space(s) by the air-conditioning or heating system.

5.5 Assumed Temperature

Assumed temperatures are listed for those spaces ventilated on an-other than temperature rise basis. The assumed temperature listed is to be used in calculating transmission loads to or from adjacent spaces. If spaces with assumed temperatures are; (a) subjected to significant weather loading, (b) adjacent to high temperature spaces, or (c) have unusually high equipment loads, a heat balance shall be accomplished to more accurately determine ambient conditions prior to calculating a transmission load.

5.6 Rate of Change

Rate of change, if noted, indicates a requirement for ventilation at a rate sufficient to ensure one complete air change in the amount of time (in minutes) indicated.

5.7 Applicable Spaces

Sheet-criteria are applicable to the listed spaces.

5.8 Special Requirements

Special requirements applicable to the spaces identified. The special requirements shall be applicable to all spaces listed in item 8, unless otherwise noted.

PPD 512-01 Page 11 of 37

5.9 General Notes

The following notes shall apply to all space criteria sheets. They shall be considered for the use and interpretation of the criteria contained in this manual:

(1) The quantity of supply air shall equal the quantity of exhaust air, unless stated otherwise.

(2) The design of all hoods (e.g. exhaust, back draft), unless stated otherwise, shall be in accordance with the latest edition of Reference [7].

(3) Exhaust air to be discharged directly to the weather refers only to the physical location of the exhaust system’s discharge point. Unless otherwise noted, it does not require an independent exhaust system, nor does it imply an absence of exhaust service to other spaces downstream of the space.

Exhaust to areas such as uptakes and voids are prohibited except where specifically permitted.

(4) Air filter requirements shall be as stated in WCC Specification 512.

(5) Required insulation type and U-values shall be based on the temperature differemce across each individual boundary in accordance with Table 2-2

(6) Ventilation air quantities shall be based on the allowable temperature rise over supply air temperature , or the minimum rate of change, or the quantity of air required for other specified criteria, whichever results in the greater air quantity.

(7) Compartment heat gains because of lighting requirements shall be as stated in Section 2 of this

DCM.

(8) The number and location of HVAC system terminals serving a space shall be as required to adequately satisfy all space environmental factors. Environmental factors shall include personal comfort; personnel heat stress considerations; removal of heat and noxious, toxic, or explosive fumes and vapors at the source; air distribution to suit space heat producing equipment locations;

space geometry; prevention of stagnant or humid areas; and uniformity of temperature gradients.

PPD 512-01 Page 12 of 37

Design Criteria Sheet No.2

1 Insulation Category A

2 Space Treatment A/C Ventilation

a. Supply - M

b. Exhaust / Return - M

c. System Classification - W

d. Closure Classification - W

Cooling Season Heating Season

3. Design Temperature 120°F 40°F

4. Design Relative Humidity - -

5. Assumed Temperature - -

6. Rate of Change (see 8b) -

7. Applicable Spaces

Auxiliary Machinery Room Engine Room

Emergency Generator Room (if provided interior to the cutter)

8. Special Requirements

(a) An analysis shall be made of ventilation air requirements for the machinery spaces based upon the equipment operating schedule as determined in a heat balance analysis. Only those pieces of machinery being utilized under each ship operation condition shall be included in the determination of ventilation air required for that condition. The ship condition requiring the largest quantity of ventilation air shall be used.

(b) The rate of change for the Engine Room shall be a minimum of 1 minute. The rate of change for the Auxiliary Machinery Room shall be a minimum of 2 minutes. Auxiliary Machinery Rooms without diesel engines may have their rate of change lowered to 4 minutes. The rate of change for the Emergency Generator Room shall be 10 minutes.

(c) The supply and exhaust systems shall have multi-speed fans.

(d) Unit heaters shall be provided to maintain 40°F in the Auxiliary Machinery Room and 50°F in the Engine Room and Emergency Generator Room with all equipment and ventilation secured. If Emergency Generator is provided with provisions to allow for starting in the service environments defined in WCC Specification 070 the unit heater may be omitted for the Emergency Generator Room only.

PPD 512-01 Page 13 of 37

(e) A supply terminal shall be located within six (6) to nine (9) inches of the intake opening of each air compressor. The terminal shall be of the open-end duct type or expanding cone type and shall be located to discharge air directly into the air compressor intake opening. Terminal air quantity shall be equal to 150 % of the air compressor intake air requirement and the terminal face velocity shall be approximately equal to the air compressor intake opening face velocity.

(f) All other supply terminals shall be located to serve main walking and maintenance areas, work benches, and heat producing equipment. The ventilation supply system air quantity (less the terminal air quantities required by air compressors) shall be distributed equally among the required supply terminals. Terminals shall be installed so that there are at least three diameters of straight duct upstream of the terminal and the terminal shall be located to direct air at a 45 degree angle downward toward the torso of the operator wherever practicable.

(g) For spaces containing Z-drive equipment:

1) Heat load for equipment shall be calculated as follows:

Motor 10% of rated HP Standby Motor 9% of rated HP (if motor is idling during normal operation) Pump 15% of rated HP

Note: Overall use factor for all equipment is 60%.

2) When calculating heating season requirements, consider all machinery secured.

(h) Supply air to the Emergency Generator shall be preheated.

(i) The quantity of exhaust ventilation required for each machinery space shall be 105% of the supply air quantity.

(j) Locate exhaust terminals in the extreme overhead directly over principle heat sources.

(k) Exhaust fans serving Engine and Auxiliary Machinery rooms may discharge into uptake spaces.

Machinery rooms with fixed firefighting systems installed that do not discharge to uptake spaces shall be provided with independent supply and exhaust systems.

(l) Spaces containing air conditioning plants shall be provided with exhaust terminals terminating 9 inches above the deck and near the air conditioning plants. The terminal air quantity shall be equal to a 15 minute rate of change for the deck level volume where the plants are located.

PPD 512-01 Page 14 of 37

Design Criteria Sheet No.3

1 Insulation Category C

2 Space Treatment A/C Ventilation

a. Supply - M

b. Exhaust / Return - M

c. System Classification - W

d. Closure Classification - W

Cooling Season Heating Season

3. Design Temperature 110°F P

4. Design Relative Humidity - -

5. Assumed Temperature - 40°F

6. Rate of Change 6 -

7. Applicable Spaces

Auxiliary Machinery Space (containing sewage equipment)

8. Special Requirements

(a) A minimum negative pressure differential, with respect to adjacent spaces, of 0.25 inches W.G. shall be maintained when access doors are closed.

(b) Compartment exhaust terminals shall be located in the vicinity of the Vacuum Sewage Collection System pumps.

(c) Two-thirds of the compartment exhaust shall be exhausted from terminals nine (9) inches above the deck, in the vicinity of the pumps. One-third of the compartment air quantity shall be exhausted from the overhead.

(d) Supply terminals shall be installed in the overhead.

(e) Spaces shall be equipped with an air flow alarm, Circuit HF (High Frequency) in accordance with WCC Specification 436.

PPD 512-01 Page 15 of 37

Design Criteria Sheet No.4

1. Insulation Category F

2. Space Treatment A/C Ventilation

a. Supply M -

b. Exhaust / Return M -

c. System Classification W -

d. Closure Classification W -

Cooling Season Heating Season

3. Design Temperature 78°F 65°F

4. Design Relative Humidity 55% -

5. Assumed Temperature - -

6. Rate of Change (see 8a and 8b) -

7. Applicable Spaces

ATON Workshop Engineers Workshop

8. Special Requirements

(a) Spaces that utilize solvents or other volatile liquids that would require mechanical exhaust ventilation to effectively remove offensive or dangerous fumes, shall be ventilated on the basis of a six (6) minute rate of change or a ten (10) degree rise above weather air (whichever results in the larger quantity of air). These spaces may be air conditioned if mechanical exhaust can be provided that precludes recirculation of fumes and does not significantly increase air conditioning load.

(b) Spaces where welding is conducted shall be ventilated on the basis of a four (4) minute rate of change or enough air to satisfy hood requirements. The assumed temperature shall be 105°F. Exhaust fume collectors shall be installed over welding slabs in accordance with Figure 5-1.

(c) Applicable to ATON Workshop only:

1. Replenishment supply air to the fan coil unit shall be mechanical.

2. Supply air for the hood shall be natural from an adjacent ventilated compartment and shall not be included as replenishment air for the fan coil unit. Assumed air temperature for the natural supply air is 120°F.

3. Supply air for the hood shall be directed to the hood area so as not to impact the other areas in the workshop.

4. The air required for exhaust hood shall not be reduced during the heating season.

5. The exhaust fan serving the hood shall be sized to include the required hood exhaust requirements. A by-pass shall be installed around the exhaust fan sized for the hood air requirement.

PPD 512-01 Page 16 of 37

6. A motorized shut-off damper shall be installed in the fan’s by-pass and shall be normally open and closed during welding only.

7. A motorized shut-off damper shall be installed in the welding hood’s natural supply from the adjacent ventilated compartment and shall be normally closed, and opened during welding only.

8. During welding, hood exhaust shall be a combination of natural supply from the adjacent ventilated compartment and the replenishment air to the fan coil unit.

9. When welding is secured, hood exhaust shall be replenishment supply air only.

PPD 512-01 Page 17 of 37

Figure 5-1: Exhaust Terminal and Typical Duct Arrangement for Welding Slab

PPD 512-01 Page 18 of 37

Design Criteria Sheet No.4I

1 Insulation Category F

2 Space Treatment A/C Ventilation

a. Supply NM -

b. Exhaust / Return M -

c. System Classification Z -

d. Closure Classification Z -

Cooling Season Heating Season

3. Design Temperature 90°F 65

4. Design Relative Humidity See 8(a) -

5. Assumed Temperature - -

6. Rate of Change 4 -

7. Applicable Spaces

Laundry

(a) Design relative humidity may exceed 55%.

(b) Space cooling shall be accomplished with a precooling coil in the supply system.

(c) For spaces containing more than one drier:

An exhaust terminal shall be located overhead in the vicinity of the dryers. A lint trap in accordance with DCM Figure 5-2 shall be installed in the dryer exhaust system. The air quantity for the ship’s exhaust terminal shall be not less than 150% of the tumbler-drier fan capacity. No filter or trap is to be installed in the ship’s exhaust system.

(d) A minimum, 0.25 negative pressure shall be maintained within the Laundry with the access doors closed.

(e) The Laundry shall be served by an independent supply system and an independent exhaust system.

(f) Mechanical exhaust shall be equal to a minimum of 115-% of supply.

PPD 512-01 Page 19 of 37

Figure 5-2: Lint Trap Installation

PPD 512-01 Page 20 of 37

Design Criteria Sheet No.5

2 Space Treatment A/C Ventilation

a. Supply M -

b. Exhaust / Return M -

c. System Classification W -

d. Closure Classification W -

Cooling Season Heating Season

3. Design Temperature 78°F 65°F

4. Design Relative Humidity 55% -

5. Assumed Temperature - -

6. Rate of Change - -

7. Applicable Spaces

Electronics Equipment Room Pilot House

8. Special Requirements

(a) In electronic control and equipment spaces, recirculation system return terminals where practicable shall be located near hot equipment that do not have internal ventilation blowers and where practicable within 6 inches of the discharge outlet of equipment provided with blowers that meet both the following conditions:

1) Rated heat dissipation is 500W or greater.

2) Air flow through the equipment has a temperature rise of 10°F or greater.

(b) Terminals shall be arranged so as to prevent water or spray from entering the equipment and shall not be directly connected to the equipment internal ventilation system.

(c) The Pilot House shall be served by an independent system.

(d) Add 15% to equipment heat dissipation to allow for future equipment additions. In calculating the heating season requirements use one-third of the cooling season equipment heat dissipation as a heat gain. Do not include the 15% future load allowances.

(e) Load and usage factors for electronic equipment in the Pilot House and Electronics Equipment Room shall be 0.8.

PPD 512-01 Page 21 of 37

(f) An infiltration load shall be applied to the Pilothouse. The infiltration rate of change shall be 60 minutes for cooling season calculations and 10 minutes for heating season calculations in accordance with SNAME 4-16; equations 3-15 (cooling season) and 3-15a (heating season).

PPD 512-01 Page 22 of 37

Design Criteria Sheet No.6

2 Space Treatment A/C Ventilation

a. Supply M -

b. Exhaust / Return NM -

c. System Classification Z -

d. Closure Classification Z -

Cooling Season Heating Season

3. Design Temperature 78°F 65°F

4. Design Relative Humidity 55% -

5. Assumed Temperature - -

6. Rate of Change - -

7. Applicable Spaces

Commanding Officer Stateroom Engineering Officer Stateroom Engineering Petty Officer Stateroom Executive Petty Officer Stateroom Crew Stateroom

8. Special Requirements

(a) No terminal shall be located over a berth or berth unit.

(b) Terminals shall not discharge towards a berth.

(c) Replenishment air shall be based upon full complement in sleeping areas.

(d) If negative heat loads are obtained because of deductions for lights and personnel, provide reheaters for 65°F delivery of replenishment air.

PPD 512-01 Page 23 of 37

Design Criteria Sheet No.6B

2 Space Treatment A/C Ventilation

a. Supply M -

b. Exhaust / Return NM -

c. System Classification Z -

d. Closure Classification Z -

Cooling Season Heating Season

3. Design Temperature 78°F 65°F

4. Design Relative Humidity - -

5. Assumed Temperature - -

6. Rate of Change - -

7. Applicable Spaces

Office Engineering Log Office Ship’s Office

(a) Use maximum seating arrangements when calculating personnel load.

(b) Natural return, if used, shall be via surrounding passages.

PPD 512-01 Page 24 of 37

Design Criteria Sheet No.7A

2 Space Treatment A/C Ventilation

a. Supply - N

b. Exhaust / Return - M

c. System Classification - Z

d. Closure Classification - Z

Cooling Season Heating Season

3. Design Temperature - 75°F (see 8b)

4. Design Relative Humidity - -

5. Assumed Temperature 100°F -

6. Rate of Change (see 8c) -

7. Applicable Spaces

Toilet Toilet / Shower Deck Toilet

8. Special Requirements

(a) Heating shall be provided by convection or space heaters.

(b) Spaces associated with staterooms are heated to 75°F. All other spaces are heated to 70°F. The heating season temperature for Toilet/Shower spaces that directly adjoin a living space may be reduced from 75°F (Design) to 65°F (Assumed) if it can be maintained without requiring space heaters when the heating season temperature of the adjoining stateroom, from which access to the Toilet/Shower space is obtained, is increased from 65°F (Design) to 70°F (Design).

(c) If natural supply is taken from adjacent ventilated areas or from non-cooled passages, the quantity of exhaust air shall be based on a six (6) minute rate of change. If natural supply is taken from surrounding spaces that are air-conditioned, exhaust shall be based on a four (4) minute rate of change.

(d) Ventilation shall be arranged to circulate the air thoroughly. Where the size and arrangement of the space is such that a natural supply opening high in a bulkhead will bypass air to the exhaust terminal, a baffle shall be provided to divert the air downward or the opening shall be located in the lower part of the bulkhead. Exhaust terminals shall be located to avoid bypassing air through an open access door.

PPD 512-01 Page 25 of 37

Design Criteria Sheet No.7B

2 Space Treatment A/C Ventilation

a. Supply M -

b. Exhaust / Return M -

c. System Classification Z -

d. Closure Classification Z -

Cooling Season Heating Season

3. Design Temperature 78°F 65°F

4. Design Relative Humidity - -

5. Assumed Temperature - -

6. Rate of Change - -

7. Applicable Spaces

Mudroom

PPD 512-01 Page 26 of 37

Design Criteria Sheet No.8

2 Space Treatment A/C Ventilation

a. Supply M/N -

b. Exhaust / Return M -

c. System Classification Z -

d. Closure Classification Z -

Cooling Season Heating Season

3. Design Temperature 78°F 65°F

4. Design Relative Humidity - -

5. Assumed Temperature - -

6. Rate of Change - -

7. Applicable Spaces

Galley/Scullery/Mess (combined)

8. Special Requirements

(a) Exhaust terminals shall be provided over dishwashers and coffee urns. Ranges shall be provided with a UL 710 Type 1 (Underwriters Labatories) - exhaust hood and with UL 1046 listed grease filters.

(b) Humidity control shall be provided by installation of a humidistat to activate the heater(s) when the room humidity exceeds 55%.

(c) The Galley/Scullery space shall be served by dedicated supply and exhaust systems. Mechanical supply air shall be a maximum of 90 % of the total air leaving the space (through exhaust or return).

(d) The replenishment air shall be 10% of the mechanical supply unless increased to accommodate exhaust requirements.

The air exhausted to the weather shall be a minimum of 20% of the total air leaving the space.

Return air shall therefore be a maximum of 80%.

(d) Heat dissipation of scullery equipment and their operating load factors shall be obtained for air conditioning load calculations.

(e) Add 30 BTU sensible heat and 30 BTU latent heat per hour per man to the heat load as an allowance for heat dissipation from food.

PPD 512-01 Page 27 of 37

Design Criteria Sheet No.12A

1 Insulation Category lnsulation categories shall be in accordance with Table 5-1 herein for spaces at the steady state temperatures determined through heat balance calculations.

2 Space Treatment A/C Ventilation

a. Supply (see 8c) NM

b. Exhaust / Return (see 8c) M

c. System Classification Z Z

d. Closure Classification Z Z

Cooling Season Heating Season

3. Design Temperature (see 8b) P

4. Design Relative Humidity - -

5. Assumed Temperature 100°F 50°F

6. Rate of Change 10 (see 8d) -

7. Applicable Spaces

Fan Room Unassigned

8. Special Requirements

(a) These spaces are not usually ventilated as the prevailing temperature in each space is adequate for its intended use. However, ventilation or air conditioning of these spaces shall be required in accordance with the requirements listed below.

(b) Fan Rooms shall be conditioned to 90°F during the cooling season and 40°F during the heating season if there are cooling coils; piping, or traps; and/or chilled water piping in the space. Natural supply from an air conditioned space shall be used. Mechanical supply from a recirculation system may be used if natural supply is not practical.

(c) Unassigned spaces in air conditioned areas shall be conditioned to 78°F in the cooling season and heated to 65°F in the heating season.

(d) Unassigned spaces in non air conditioned areas shall receive supply and exhaust air in the cooling season based on a 10 minute minimum rate of change or 10°F allowable temperature rise, whichever is greater.

PPD 512-01 Page 28 of 37

Design Criteria Sheet No.12E

2 Space Treatment A/C Ventilation

a. Supply NM -

b. Exhaust / Return NM -

c. System Classification Z -

d. Closure Classification Z -

Cooling Season Heating Season

3. Design Temperature - -

4. Design Relative Humidity 55% -

5. Assumed Temperature - -

6. Rate of Change - -

7. Applicable Spaces

Passage Vestibule

Stairwells

(a) These spaces are not usually ventilated as the prevailing temperature in each space is adequate for its intended use. However, ventilation or air conditioning of these spaces shall be required in accordance with the requirements listed below.

(b) Passageways in air conditioned areas may be used in natural returns. In those cases, if the passage has a load which would result in a temperature rise of ten (10) degrees or more, for the return air, a terminal shall be placed in the passage sized for its load. If during the heating season, the passage has a load which results in a temperature drop of ten (10) degrees or more, the passage shall be heated by convection heaters if there is no terminal provided for cooling. Other passageways require no treatment.

(c) Stairwells in air conditioned areas shall be pressurized to retard the spread of smoke.

PPD 512-01 Page 29 of 37

Design Criteria Sheet No.12K

1 Insulation Category lnsulation categories shall be in accordance with Table 5-1 herein for spaces at the steady state temperatures determined through heat balance calculations.

2 Space Treatment A/C Ventilation

a. Supply - NM

b. Exhaust / Return - M

c. System Classification - Z

d. Closure Classification - Z

Cooling Season Heating Season

3. Design Temperature 100°F 65°F

4. Design Relative Humidity - -

5. Assumed Temperature - -

6. Rate of Change 6 -

7. Applicable Spaces

Repair Locker

(a) Natural supply (75 CFM), if used, shall be taken from surrounding spaces.

(b) Supply air quantities are to be based on the allowable temperature over weather air temperature or the minimum rate of change, whichever is greater.

PPD 512-01 Page 30 of 37

Design Criteria Sheet No.13I

2 Space Treatment A/C Ventilation

a. Supply M -

b. Exhaust / Return NM -

c. System Classification Z -

d. Closure Classification Z -

Cooling Season Heating Season

3. Design Temperature 78°F 65°F

4. Design Relative Humidity 55% -

5. Assumed Temperature - -

6. Rate of Change - -

7. Applicable Spaces

Dry Provisions Storeroom

8. Special Requirements

(a) Provide terminals with ½ inch wire mesh screen.

(b) Natural exhaust, if used, shall be to the surrounding spaces or to the weather.

(c) The Dry Provisions Storeroom shall be air conditioned with a horizontally mounted fan coil unit.

Replenishment air for this space is not required.

PPD 512-01 Page 31 of 37

Design Criteria Sheet No.13

2 Space Treatment A/C Ventilation

a. Supply - M/N

b. Exhaust / Return - M

c. System Classification - Z

d. Closure Classification - Z

Cooling Season Heating Season

3. Design Temperature 110°F 65°F

4. Design Relative Humidity - -

5. Assumed Temperature - -

6. Rate of Change (see 8b and 8c) -

7. Applicable Spaces

ATON Stowage

8. Special Requirements

(a) Supply air quantities shall be based on a temperature rise over weather air temperature or the minimum rate of change, whichever is greater.

(b) Spaces that do not contain welding or burning equipment shall be provided with a mechanical exhaust sufficient to produce a ten-minute rate of change.

PPD 512-01 Page 32 of 37

Design Criteria Sheet No.15

2 Space Treatment A/C Ventilation

a. Supply - M

b. Exhaust / Return - M

c. System Classification - Z

d. Closure Classification - Z

Cooling Season Heating Season

3. Design Temperature - P

4. Design Relative Humidity - -

5. Assumed Temperature 110°F 40°F

6. Rate of Change 4 -

7. Applicable Spaces

Hazardous Material Stowage Locker (includes paint and flammable liquids)

8. Special Requirements

(a) Exhaust terminals shall be provided nine inches above the deck and in the overhead.

(b) Supply terminals shall have eight mesh 0.035 inch diameter aluminum or stainless steel wire screen.

(c) If a compartment exhaust quantity exceeds 10% of system quantity, a non-sparking centrifugal fan (located outside the compartment served) shall be used for the system.

(d)

(e) A minimum negative pressure of 0.25 inches of water pressure shall be maintained through balancing when access doors are closed.

(f) Spaces shall be equipped with an air flow alarm, Circuit HF in accordance with WCC Specification 436.

PPD 512-01 Page 33 of 37

Index of Spaces

SPACE DESIGN CRITERIA SHEET

ATON Workshop 4 ATON Stowage 13 Auxiliary Machinery Room 2 Auxiliary Machinery Room (containing sewage equipment) 3 Commanding Officer Stateroom 6 Crew Stateroom 6 Deck Toilet 7A Dry Provisions Storeroom 13I Electronics Equipment Room 5 Emergency Generator Room 2 Engine Room 2 Engineers Workshop 4 Engineering Officer Stateroom 6 Engineering Petty Officer Stateroom 6 Executive Petty Officer Stateroom 6 Fan Room 12A Galley/Scullery Mess 8 Hazardous Materials Storage Locker 15 Laundry 4I Mud Room 7B Office 6B Passages 12E Pilot House 5 Repair Locker 12K Toilet 7A Toilet /Shower 7A Unassigned 12A Vestibule 12E

2.7 Replenishment Air

Index of Spaces