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ENGINEERING COOKBOOK

A Handbook for theMechanical Designer

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A Handbookfor the

Mechanical Designer

Second EditionCopyright 1999

This handy engineeringinformation guide is a token of

Loren Cook Companys appreciationto the many ne mechanicaldesigners

in our industry.

Springeld, MO

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Fan BasicsFan Types . . . . . . . . . . . . . . . . . . . . . .. . . . . . . . . . . . . . . . . 1Fan Selection Criteria . . . . .. . . . . . . . . . . . . . . . . . . . . . . . . 1Fan Laws. . . .. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .. 2Fan Performance Tables and Curves . . . . . . . . . . . . . . .. . . 2Fan Testing - Laboratory, Field . . . . . . . . . . . . . .. . . . . . . . . 2Air Density Factors for Altitude and Temperature. . . . . . . . . 3Use of Air Density Factors - An Example . . . .. . . . . . . . . . . 3Classications for Spark ResistantConstruction . . . . . . . .4-5

Impeller Designs - Centrifugal. . . . . . . . . . . . . . . . .. . . . . .5-6Impeller Designs - Axial . . . . . . . . . . . . . .. . . . . . . . . . . . . . 7Terminology for Centrifugal FanComponents. . . . . . . . . . . . 8Drive Arrangements forCentrifugal Fans . . . . . . . . . . . . .9-10Rotation &Discharge Designations for Centrifugal Fans 11-12Motor Positionsfor Belt or Chain Drive Centrifugal Fans . . 13Fan InstallationGuidelines . . . . . . . . . . . . . . . . . . . . . . . . . 14FanTroubleshooting Guide . . . . . . . . . . . . . . . . . . . . . . .. . 15

Motor and Drive BasicsDenitions and Formulas . . . . . . . . . .. . . . . . . . . . . . . . . . 16Types of Alternating CurrentMotors . . . . . . . . . . . . . . . .17-18Motor InsulationClasses. . . . . . . . . . . . . . . . . . . . . . . . . . .18Motor Service Factors . . . . . . . . . . . . . . . . . . . . . .. . . . . . . 19

Locked Rotor KVA/HP. . . . . . . . . . . . . . . . . . . . . . .. . . . . . 19Motor Efciency and EPAct . . . . . . . . . . . . . .. . . . . . . . . . . 20Full Load Current . . . . . . . . . . . . .. . . . . . . . . . . . . . . . .21-22General Effect of Voltage andFrequency . . . . . . . . . . . . . . 23Allowable Ampacities of NotMore Than Three

Insulated Conductors . . . . . . . . . . . . . . . . . . . . . .. . .24-25Belt Drives. . . . . . . . . . . . . . . . . . . . . . .. . . . . . . . . . . . . . . 26Estimated Belt Drive Loss . . . . .. . . . . . . . . . . . . . . . . . . . . 27Bearing Life . . . . .. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .28

System Design GuidelinesGeneral Ventilation . . . . . . . . . .. . . . . . . . . . . . . . . . . . . . . 29Process Ventilation . .. . . . . . . . . . . . . . . . . . . . . . . . . . . . . 29KitchenVentilation. . . . . . . . . . . . . . . . . . . . . . . . . . . .. . . . 30

Sound . . . . . . . . . . . . . . . . . . . . . . . . . . . . .. . . . . . . . . . . . 31Rules of Thumb . . . . . . . . . . . . .. . . . . . . . . . . . . . . . . .31-32Noise Criteria . . . . . .. . . . . . . . . . . . . . . . . . . . . . . . . . . . . 32

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System Design Guidelines (cont.)Sound Power and Sound PowerLevel. . . . . . . . . . . . . . . . . 32Sound Pressure and SoundPressure Level . . . . . . . . . . . . 33Room Sones dBA Correlation. . . . . . . . . . . . . . . . . . . . . 33Noise Criteria Curves.. . . . . . . . . . . . . . . . . . . . . . . . . . . . . 34DesignCriteria for Room Loudness. . . . . . . . . . . . . . . . .35-36Vibration. . . . . . . . . . . . . . . . . . . . . . . . . . .. . . . . . . . . . . . . 37Vibration Severity . . . . . . . . . .. . . . . . . . . . . . . . . . . . . .38-39

General Ventilation Design

Air Quality Method . . . . . . . . . . . . . . . . . . . . . . .. . . . . . . . . 40Air Change Method . . . . . . . . . . . . . . .. . . . . . . . . . . . . . . . 40Suggested Air Changes . . . . . .. . . . . . . . . . . . . . . . . . . . . . 41Ventilation Rates forAcceptable Indoor Air Quality . . . . . . . 42Heat Gain FromOccupants of Conditioned Spaces . . . . . . 43Heat Gain FromTypical Electric Motors. . . . . . . . . . . . . . . . 44Rate ofHeat Gain Commercial Cooking Appliances in

Air-Conditioned Areas. . . . . . . . . . . . . . . . . . . . . .. . . . . . 45Rate of Heat Gain From Miscellaneous Appliances . . .. . . 46Filter Comparison . . . . . . . . . . . . . . . . . . . . .. . . . . . . . . . . 46Relative Size Chart of Common AirContaminants . . . . . . . 47Optimum Relative Humidity Ranges forHealth . . . . . . . . . . 48

Duct Design

Backdraft or Relief Dampers . . . . . . . . . . . . . . . . . .. . . . . . 49Screen Pressure Drop . . . . . . . . . . . . . . . .. . . . . . . . . . . . . 50Duct Resistance. . . . . . . . . . . .. . . . . . . . . . . . . . . . . . . . . . 51RectangularEquivalent of Round Ducts . . . . . . . . . . . . . . . 52TypicalDesign Velocities for HVAC Components. . . . . . . . . 53Velocityand Velocity Pressure Relationships . . . . . . . . . . . 54U.S.Sheet Metal Gauges . . . . . . . . . . . . . . . . . . . . . . . .. . 55Recommended Metal Gauges for Ducts . . . . . . . . . . . . .. . 56Wind Driven Rain Louvers. . . . . . . . . . . . . . . . . . .. . . . . . . 56

Heating & RefrigerationMoisture and Air Relationships . . .. . . . . . . . . . . . . . . . . . . 57Properties of SaturatedSteam . . . . . . . . . . . . . . . . . . . . . . 58Cooling LoadCheck Figures . . . . . . . . . . . . . . . . . . . . . .59-60

Heat Loss Estimates . . . . . . . . . . . . . . . . . . . . . .. . . . . .61-62Fuel Comparisons . . . . . . . . . . . . . . . . .. . . . . . . . . . . . . . . 62Fuel Gas Characteristics . . . . .. . . . . . . . . . . . . . . . . . . . . . 62

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Heating & Refrigeration (cont.)Estimated Seasonal Efcienciesof Heating Systems . . . . 63Annual Fuel Use . . . . . . . . . . .. . . . . . . . . . . . . . . . . . . 63-64Pump Construction Types. . . . . . . . . . . . . . . . . . . . . . . . . 64Pump ImpellerTypes . . . . . . . . . . . . . . . . . . . . . . . . . . . . .64Pump Bodies . . . . . . . . . . . . . . . . . . . . . . . . . . .. . . . . . . . 65Pump Mounting Methods . . . . . . . . . . . . . .. . . . . . . . . . . 65Afnity Laws for Pumps . . . . . . . . . . .. . . . . . . . . . . . . . . . 66Pumping System TroubleshootingGuide . . . . . . . . . . . 67-68

Pump Terms, Abbreviations, and Conversion Factors . . . .69Common Pump Formulas . . . . . . . . . . . . . . . . . . . . . .. . . 70Water Flow and Piping . . . . . . . . . . . . . . . . . . .. . . . . . 70-71Friction Loss for Water Flow . . . . . . . . . . .. . . . . . . . . . 71-72Equivalent Length of Pipe for Valves andFittings . . . . . . . 73Standard Pipe Dimensions . . . . . . . . .. . . . . . . . . . . . . . . 74Copper Tube Dimensions . . . . . .. . . . . . . . . . . . . . . . . . . 74Typical Heat TransferCoefcients . . . . . . . . . . . . . . . . . . . 75Fouling Factors. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .76Cooling Tower Ratings. . . . . . . . . . . . . . . . . . . . . .. . . . . . 77Evaporate Condenser Ratings . . . . . . . . . . . . .. . . . . . . . 78Compressor Capacity vs. Refrigerant Temperatureat

100F Condensing . . . . . . . . . . . . . . . . . . . . . . . .. . . . . 78

Refrigerant Line Capacities for 134a. . . . . . . . . . . . . .. . . 79Refrigerant Line Capacities for R-22 . . . . . . . . . . .. . . . . . 79Refrigerant Line Capacities for R-502 . . . . . . . .. . . . . . . . 80Refrigerant Line Capacities for R-717 . . . . . .. . . . . . . . . . 80

Formulas & Conversion FactorsMiscellaneous Formulas . . . .. . . . . . . . . . . . . . . . . . . . 81-84Area and Circumferenceof Circles . . . . . . . . . . . . . . . . 84-87Circle Formula . .. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .87Common Fractions of an Inch . . . . . . . . . . . . . . . . . . .. 87-88Conversion Factors . . . . . . . . . . . . . . . . . . . . .. . . . . . . 88-94Psychometric Chart . . . . . . . . . . . . . . .. . . . . . . . . . . . . . . 95

Index . . . . . . . . . . . . . . . . . . . . . . . . . . . . .. . . . . . . . . . . . 96-103

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Fan TypesAxial Fan - An axial fan discharges air parallel to theaxis of the

impeller rotation. As a general rule, axial fans are preferredforhigh volume, low pressure, and non-ducted systems.Axial FanTypes Propeller, Tube Axial and Vane Axial.

Centrifugal Fan - Centrifugal fans discharge air perpendiculartothe axis of the impeller rotation. As a general rule,centrifugalfans are preferred for higher pressure ductedsystems.Centrifugal Fan Types Backward Inclined, Airfoil, ForwardCurved, and Radial Tip.

Fan Selection CriteriaBefore selecting a fan, the followinginformation is needed.

Air volume required - CFM System resistance - SP Air density(Altitude and Temperature)

Type of service Environment type Materials/vapors to beexhausted Operation temperature

Space limitations Fan type Drive type (Direct or Belt) Noisecriteria Number of fans Discharge Rotation Motor position Expectedfan life in years

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Fan LawsThe simplied form of the most commonly used fan laws

include. CFM varies directly with RPM

CFM1 /CFM2 = RPM 1 /RPM 2 S P varies with the square of theRPM

SP 1 /SP 2 = (RPM 1 /RPM 2)2

HP varies with the cube of the RPM HP 1 /HP 2 = (RPM 1 /RPM2)

3

Fan Performance Tables and CurvesPerformance tables provide asimple method of fan selection.

However, it is critical to evaluate fan performance curves inthefan selection process as the margin for error is very slim whenselecting a fan near the limits of tabular data . The perfor-mancecurve also is a valuable tool when evaluating fan perfor-mance inthe eld.

Fan performance tables and curves are based on standardairdensity of 0.075 lb/ft 3. When altitude and temperature differsig-nicantly from standard conditions (sea level and 70 F)perfor-mance modication factors must be taken into account toensureproper performance.

For further information refer to Use of Air Density Factors - AnExample , page 3.

Fan Testing - Laboratory, FieldFans are tested and performancecertied under ideal labora-

tory conditions. When fan performance is measured in eldcon-ditions, the difference between the ideal laboratory conditionandthe actual eld installation must be considered.Considerationmust also be given to fan inlet and dischargeconnections as theywill dramatically affect fan performance in theeld. If possible,readings must be taken in straight runs ofductwork in order toensure validity. If this cannot beaccomplished, motor amperageand fan RPM should be used along withperformance curves toestimate fan performance.

For further information refer to Fan Installation Guidelines,page 14.

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Fan applications may involve the handling of potentiallyexplo-sive or ammable particles, fumes or vapors. Suchapplicationsrequire careful consideration of all system componentsto insurethe safe handling of such gas streams. This AMCAStandarddeals only with the fan unit installed in that system. TheStandardcontains guidelines which are to be used by both themanufac-turer and user as a means of establishing general methodsofconstruction. The exact method of construction and choiceofalloys is the responsibility of the manufacturer; however, thecus-tomer must accept both the type and design with fullrecognitionof the potential hazard and the degree of protectionrequired.Construction Type

A. All parts of the fan in contact with the air or gas beinghan-dled shall be made of nonferrous material. Steps must alsobetaken to assure that the impeller, bearings, and shaftareadequately attached and/or restrained to prevent a lateraloraxial shift in these components.

B. The fan shall have a nonferrous impeller and nonferrousringabout the opening through which the shaft passes. Fer-rous hubs,shafts, and hardware are allowed provided con-struction is suchthat a shift of impeller or shaft will notpermit two ferrous partsof the fan to rub or strike. Stepsmust also be taken to assure theimpeller, bearings, and

shaft are adequately attached and/or restrained to preventalateral or axial shift in these components.C. The fan shall be soconstructed that a shift of the impeller or

shaft will not permit two ferrous parts of the fan to ruborstrike.

Notes1. No bearings, drive components or electrical devicesshall

be placed in the air or gas stream unless they are con-structedor enclosed in such a manner that failure of thatcomponent cannotignite the surrounding gas stream.

2. The user shall electrically ground all fan parts.3. For thisStandard, nonferrous material shall be a material

with less than 5% iron or any other material with demon-stratedability to be spark resistant.

Fan Basics

Classifications for Spark Resistant Construction

Adapted from AMCA Standard 99-401-86

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Classications for Spark Resistant Construction(cont.)

4.The use of aluminum or aluminum alloys in the presence of

steel which has been allowed to rust requires specialconsid-eration. Research by the U.S. Bureau of Mines and othershasshown that aluminum impellers rubbing on rusty steelmay cause highintensity sparking.

The use of the above Standard in no way implies a guaranteeofsafety for any level of spark resistance. Spark resistantconstruc-tion also does not protect against ignition of explosivegasescaused by catastrophic failure or from any airstream materialthatmay be present in a system.Standard Applications

Centrifugal Fans Axial and Propeller Fans Power RoofVentilators

This standard applies to ferrous and nonferrous metals.Thepotential questions which may be associated with fans constructedof FRP, PVC, or any other plastic compound were not addressed.

Impeller Designs - CentrifugalAirfoil - Has the highest efciencyof all of the centrifugal impeller

designs with 9 to 16 blades of airfoil contourcurved away fromthe direction of rotation.Air leaves the impeller at a velocityless thanits tip speed. Relatively deep blades providefor efcientexpansion with the blade pas-sages. For the given duty, the airfoilimpellerdesign will provide for the highest speed of

the centrifugal fan designs.Applications - Primary applicationsinclude general heating sys-tems, and ventilating and airconditioning systems. Used in largersizes for clean air industrialapplications providing signicantpower savings.

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Impeller Designs - Centrifugal (cont.)Backward Inclined,Backward Curved - Efciency is slightly

less than that of the airfoil design. Backwardinclined orbackward curved blades are singlethickness with 9 to 16 bladescurved orinclined away from the direction of rotation.Air leavesthe impeller at a velocity less thanits tip speed. Relatively deepblades provideefcient expansion with the blade passages.

Applications - Primary applications include general heatingsys-

tems, and ventilating and air conditioning systems. Also usedinsome industrial applications where the airfoil blade is notaccept-able because of a corrosive and/or erosiveenvironment.Radial - Simplest of all centrifugal impellers andleast efcient.

Has high mechanical strength and the impel-ler is easilyrepaired. For a given point of rat-ing, this impeller requiresmedium speed.Classication includes radial blades and mod-ied radialblades), usually with 6 to 10blades.Applications - Used primarilyfor material

handling applications in industrial plants. Impeller can be ofrug-ged construction and is simple to repair in the eld. Impellerissometimes coated with special material. This design also isusedfor high pressure industrial requirements and is notcommonlyfound in HVAC applications.Forward Curved - Efciency isless than airfoil and backward

curved bladed impellers. Usually fabricated atlow cost and oflightweight construction. Has24 to 64 shallow blades with both theheeland tip curved forward. Air leaves the impellerat velocitiesgreater than the impeller tip

speed. Tip speed and primary energy trans-ferred to the air isthe result of high impellervelocities. For the given duty, thewheel is the

smallest of all of the centrifugal types and operates mostef-ciently at lowest speed.Applications - Primary applicationsinclude low pressure heat-ing, ventilating, and air conditioningapplications such as domes-tic furnaces, central station units, andpackaged air conditioningequipment from room type to roof topunits.

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Impeller Designs - AxialPropeller - Efciency is low and usuallylimited to low pressure

applications. Impeller construction costs arealso usually low.General construction fea-tures include two or more blades ofsinglethickness attached to a relatively small hub.Energy transferis primarily in form of velocitypressure.Applications - Primaryapplications include

low pressure, high volume air moving applications such as aircir-

culation within a space or ventilation through a wallwithoutattached duct work. Used for replacement airapplications.

Tube Axial - Slightly more efcient than propeller impellerdesignand is capable of developing a more usefulstatic pressurerange. Generally, the numberof blades range from 4 to 8 with thehub nor-mally less than 50 percent of fan tip diameter.Blades canbe of airfoil or single thicknesscross section.Applications -Primary applications include

low and medium pressure ducted heating, ventilating, andairconditioning applications where air distribution on thedown-stream side is not critical. Also used in some industrialapplica-tions such as drying ovens, paint spray booths, andfume

exhaust systems.Vane Axial - Solid design of the blades permitsmedium to high

pressure capability at good efciencies. Themost efcient fans ofthis type have airfoilblades. Blades are xed or adjustablepitchtypes and the hub is usually greater than 50percent of the fantip diameter.Applications - Primary applications includegeneralheating, ventilating, and air condition-

ing systems in low, medium, and high pressureapplications.Advantage where straight through ow and compactinstallationare required. Air distribution on downstream side isgood. Alsoused in some industrial applications such as dryingovens, paintspray booths, and fume exhaust systems. Relatively morecom-

pact than comparable centrifugal type fans for the sameduty.

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Terminology for Centrifugal Fan ComponentsHousing

Side Panel

Impeller

Cutoff

Blast AreaDischarge

OutletArea

Cutoff

Scroll

FrameImpellerShroud

Inlet CollarBearingSupport

Inlet

Blade

Back Plate

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Shaft

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Drive Arrangements for Centrifugal FansSW - Single Width, SI -Single InletDW - Double Width, DI - Double Inlet

Arr. 1 SWSI - For belt driveor direct drive connection.Impellerover-hung. Twobearings on base.

Arr. 2 SWSI - For belt driveor direct drive connection.Impellerover-hung. Bearingsin bracket supported by fanhousing.

Arr. 3 SWSI - For belt driveor direct drive connection.Onebearing on each sidesupported by fan housing.

Arr. 3 DWDI - For belt driveor direct connection. Onebearing oneach side andsupported by fan housing.

Fan Basics

Adapted from AMCA Standard 99-2404-78

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Drive Arrangements for Centrifugal Fans (cont.)SW - SingleWidth, SI - Single InletDW - Double Width, DI - Double Inlet

Arr. 8 SWSI - For belt driveor direct connection.Arrangement 1plusextended base for primemover.

Arr. 7 DWDI - For belt driveor direct connection.Arrangement 3plus base forprime mover.

Arr. 10 SWSI - For beltdrive. Impeller overhung,

two bearings, with primemover inside base.

Arr. 9 SWSI - For belt drive.Impeller overhung, two

bearings, with prime moveroutside base.

Fan Basics

Arr. 4 SWSI - For directdrive. Impeller over-hung onprime movershaft. No bear-ings on fan. Prime moverbase mounted orintegrallydirectly connected.

Arr. 7 SWSI - For belt driveor direct connection.Arrangement 3plus base forprime mover.

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Rotation & Discharge Designations forCentrifugal Fans*

Clockwise

Top Horizontal

CounterclockwiseTop Angular Down

Clockwise CounterclockwiseTop Angular Up

Clockwise Counterclockwise

* Rotation is always as viewed from drive side.

Down Blast

Clockwise Counterclockwise

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12* Rotation is always as viewed from drive side.

Rotation & Discharge Designations forCentrifugal Fans*(cont.)

Clockwise CounterclockwiseBottom Horizontal

Clockwise Counterclockwise

Bottom Angular Down

Clockwise CounterclockwiseBottom Angular Up

Clockwise Counterclockwise

Up Blast

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Motor Positions for Belt Drive Centrifugal Fans

To determine the location of the motor, face the drive side ofthefan and pick the proper motor position designated by thelettersW, X, Y or Z as shown in the drawing below.

Adapted from AMCA Standard 99-2404-78

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Correct Installations

Incorrect Installations

Turbulence Turbulence

Limit slope to7 diverging

Cross-sectionalarea not greaterthan 112-1/2% of

inlet area

Limit slope to15 converging

Cross-sectionalarea not greaterthan 92-1/2% of

inlet area

x

Minimum of 2-1/2inlet diameters

(3 recommended)

Correct Installations

Limit slope to15 converging

Cross-sectional areanot greater than 105%

of outlet area

Limit slope to7 diverging

Cross-sectional areanot greater than 95%

of outlet area

x

Minimum of 2-1/2outlet diameters

(3 recommended)

Incorrect Installations

TurbulenceTurbulence

Fan Installation GuidelinesCentrifugal Fan Conditions

Typical Inlet Conditions

Typical Outlet Conditions

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Fan Troubleshooting GuideLow Capacity or Pressure

Incorrect direction of rotation Make sure the fan rotates insamedirection as the arrows on the motor or belt driveassembly.

Poor fan inlet conditions There should be a straight, clearductat the inlet.

Improper wheel alignment.

Excessive Vibration and Noise

Damaged or unbalanced wheel. Belts too loose; worn or oilybelts. Speed too high. Incorrect direction of rotation. Make surethe fan rotates in

same direction as the arrows on the motor or beltdriveassembly.

Bearings need lubrication or replacement.

Fan surge.Overheated Motor

Motor improperly wired. Incorrect direction of rotation. Makesure the fan rotates in

same direction as the arrows on the motor or beltdriveassembly.

Cooling air diverted or blocked. Improper inlet clearance.Incorrect fan RPM. Incorrect voltage.

Overheated Bearings Improper bearing lubrication. Excessive belttension.

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% slip =(synchronous speed - actual speed)

synchronous speed X 100

Denitions and FormulasAlternating Current : electric currentthat alternates or reversesat a dened frequency, typically 60cycles per second (Hertz) inthe U.S. and 50 Hz in Canada and othernations.Breakdown Torque : the maximum torque a motor willdevelopwith rated voltage and frequency applied without an abruptdropin speed.Efficiency : a rating of how much input power anelectric motorconverts to actual work at the rotating shaftexpressed in per-cent.

% efficiency = (power out / power in) x 100 Horsepower : a rateof doing work expressed in foot-pounds perminute.

HP = (RPM x torque) / 5252 lb-ft.Locked Rotor Torque : theminimum torque that a motor willdevelop at rest for all angularpositions of the rotor with rated volt-age and frequencyapplied.Rated Load Torque : the torque necessary to produceratedhorsepower at rated-load speed.Single Phase AC : typicalhousehold type electric powerconsisting of a single alternatingcurrent at 110-115 volts.Slip : the difference between synchronousspeed and actualmotor speed. Usually expressed in percent slip.

Synchronous speed : the speed of the rotating magnetic eld inanelectric motor.

Synchronous Speed = (60 x 2f) / p Where: f = frequency of thepower supply

p = number of poles in the motor

Three Phase AC : typical industrial electric power consisting of3alternating currents of equal frequency differing in phase of120degrees from each other. Available in voltages ranging from200to 575 volts for typical industrial applications.Torque : ameasure of rotational force dened in foot-poundsorNewton-meters.

Torque = (HP x 5252 lb-ft.) / RPM

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Types of Alternating Current MotorsSingle Phase AC Motors

This type of motor is used in fan applications requiringlessthan one horsepower. There are four types of motors suitablefordriving fans as shown in the chart below. All are singlespeedmotors that can be made to operate at two or more speedswithinternal or external modications.

Single Phase AC Motors (60hz)

Three-phase AC Motors

The most common motor for fan applications is the three-phasesquirrel cage induction motor. The squirrel-cage motor isa constantspeed motor of simple construction that produces rel-atively highstarting torque. The operation of a three-phasemotor is simple: thethree phase current produces a rotatingmagnetic eld in the stator.This rotating magnetic eld causes amagnetic eld to be set up in therotor. The attraction and repul-sion of these two magnetic eldscauses the rotor to turn.

Squirrel cage induction motors are wound for thefollowingspeeds:

Motor Type HPRange Efciency SlipPoles/RPM Use

Shaded Pole 1/6 to1/4 hplow

(30%)high

(14%)4/15506/1050

small direct drivefans (low starttorque)

Perm-splitCap.

Up to1/3 hp

medium(50%)

medium(10%)

4/16256/1075

small direct drivefans (low starttorque)

Split-phaseUp to1/2 hp

medium-high (65%)

low(4%)

2/34504/17256/11408/850

small belt drive

fans (good starttorque)

Capacitor-start

1/2 to34 hp

medium-high (65%)

low(4%)

2/34504/17256/11408/850

small belt drivefans (good starttorque)

Number ofPoles

60 HzSynchronous Speed

50 HzSynchronous Speed

2 3600 30004 1800 15006 1200 10008 900 750

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Types of Alternating Current MotorsActual motor speed issomewhat less than synchronous speed

due to slip. A motor with a slip of 5% or less is called anormalslip motor. A normal slip motor may be referred to as aconstantspeed motor because the speed changes very little withloadvariations. In specifying the speed of the motor on thenameplatemost motor manufacturers will use the actual speed of themotorwhich will be less than the synchronous speed due to slip.

NEMA has established several different torque designs tocovervarious three-phase motor applications as shown in the chart.

Motor Insulation ClassesElectric motor insulation classes arerated by their resistance

to thermal degradation. The four basic insulation systemsnor-mally encountered are Class A, B, F, and H. Class A has atem-perature rating of 105C (221F) and each step from A to B, BtoF, and F to H involves a 25 C (77 F) jump. The insulation classinany motor must be able to withstand at least the maximum

ambient temperature plus the temperature rise that occurs asaresult of continuous full load operation.

NEMADesign

StartingCurrent

LockedRotor

BreakdownTorque % Slip

B Medium MediumTorque HighMax.5%

C Medium HighTorque MediumMax.5%

D MediumExtra-High

Torque Low5%

or moreNEMADesign Applications

BNormal starting torque for fans, blowers, rotarypumps,compressors, conveyors, machine tools.Constant load speed.

CHigh inertia starts - large centrifugal blowers, ywheels, andcrusher drums. Loaded starts such aspiston pumps, compressors, andconveyers. Con-stant load speed.

DVery high inertia and loaded starts. Also consider-ablevariation in load speed. Punch presses,shears and forming machinetools. Cranes, hoists,elevators, and oil well pumping jacks.

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Motor Service FactorsSome motors can be specied with servicefactors other than

1.0. This means the motor can handle loads above theratedhorsepower. A motor with a 1.15 service factor can handle a15%overload, so a 10 horsepower motor can handle 11.5 HP ofload. Ingeneral for good motor reliability, service factor shouldnot beused for basic load calculations. By not loading the motorinto theservice factor under normal use the motor can betterwithstandadverse conditions that may occur such as higher thannormal ambienttemperatures or voltage uctuations as well asthe occasionaloverload.Locked Rotor KVA/HP

Locked rotor kva per horsepower is a rating commonly speci-ed onmotor nameplates. The rating is shown as a code letteron thenameplate which represents various kva/hp ratings.

The nameplate code rating is a good indication of thestartingcurrent the motor will draw. A code letter at the beginningof thealphabet indicates a low starting current and a letter at theend ofthe alphabet indicates a high starting current. Startingcurrentcan be calculated using the following formula:

Starting current = (1000 x hp x kva/hp) / (1.73 x Volts)

Code Letter kva/hp Code Letter kva/hp

A 0 - 3.15 L 9.0 - 10.0B 3.15 - 3.55 M 10.0 - 11.2C 3.55 - 4.0 N11.2 - 12.5D 4.0 - 4.5 P 12.5 - 14.0E 4.5 - 5.0 R 14.0 - 16.0F 5.0- 5.6 S 16.0 - 18.0G 5.6 - 6.3 T 18.0 - 20.0H 6.3 - 7.1 U 20.0 -22.4J 7.1 - 8.0 V 22.4 and upK 8.0 - 9.0

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Motor Efciency and EPActAs previously dened, motor efciency is ameasure of how

much input power a motor converts to torque and horsepower attheshaft. Efciency is important to the operating cost of a motorand tooverall energy use in our economy. It is estimated thatover 60% ofthe electric power generated in the United States isused to powerelectric motors. On October 24, 1992, the U.S.Congress signed intolaw the Energy Policy Act (EPAct) thatestablished mandated efciencystandards for general purpose,three-phase AC industrial motors from1 to 200 horsepower.

EPAct became effective on October 24, 1997.

Department of Energy General Purpose Motors

Required Full-Load Nominal EfciencyUnder EPACT-92

MotorHP

Nominal Full-Load EfciencyOpen Motors Enclosed Motors

6 Pole 4 Pole 2 Pole 6 Pole 4 Pole 2 Pole1 80.0 82.5 80.0 82.575.5

1.5 84.0 84.0 82.5 85.5 84.0 82.52 85.5 84.0 84.0 86.5 84.084.03 86.5 86.5 84.0 87.5 87.5 85.5

5 87.5 87.5 85.5 87.5 87.5 87.57.5 88.5 88.5 87.5 89.5 89.588.510 90.2 89.5 88.5 89.5 89.5 89.515 90.2 91.0 89.5 90.2 91.090.220 91.0 91.0 90.2 90.2 91.0 90.225 91.7 91.7 91.0 91.7 92.491.030 92.4 92.4 91.0 91.7 92.4 91.040 93.0 93.0 91.7 93.0 93.091.750 93.0 93.0 92.4 93.0 93.0 92.460 93.6 93.6 93.0 93.6 93.693.075 93.6 94.1 93.0 93.6 94.1 93.0

100 94.1 94.1 93.0 94.1 94.5 93.6125 94.1 94.5 93.6 94.1 94.594.5

150 94.5 95.0 93.6 95.0 95.0 94.5200 94.5 95.0 94.5 95.0 95.095.0

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Full Load CurrentSingle Phase Motors

Based on Table 430-148 of the National Electric Code, 1993.Formotors running at usual speeds and motors with normal torquecharacteristics.

HP 115V 200V 230V1/6 4.4 2.5 2.21/4 5.8 3.3 2.91/3 7.2 4.13.61/2 9.8 5.6 4.93/4 13.8 7.9 6.91 16 9.2 8

1-1/2 20 11.5 102 24 13.8 123 34 19.6 175 56 32.2 28

7-1/2 80 46 4010 100 57.5 50

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Full Load CurrentThree Phase Motors

A-C Induction Type-Squirrel Cage and Wound Rotor Motors*

Branch-circuit conductors supplying a single motor shall have anampacity not less than 125 percent of the motor full-load currentrating.Based on Table 430-150 of the National Electrical Code ,

1993. For motors running at speeds usual for belted motors andwith normal torque characteristics.* For conductor sizing only

HP 115V 200V 230V 460V 575V 2300V 4000V1/2 4 2.3 2 1 0.83/4 5.63.2 2.8 1.4 1.11 7.2 4.15 3.6 1.8 1.4

1-1/2 10.4 6 5.2 2.6 2.12 13.6 7.8 6.8 3.4 2.73 11 9.6 4.8 3.9517.5 15.2 7.6 6.1

7-1/2 25 22 11 910 32 28 14 1115 48 42 21 1720 62 54 27 2225 7868 34 2730 92 80 40 32

40 120 104 52 4150 150 130 65 5260 177 154 77 62 15.4 8.875 221192 96 77 19.2 11

100 285 248 124 99 24.8 14.3125 358 312 156 125 31.2 18150 415360 180 144 36 20.7

200 550 480 240 192 48 27.6Over 200 hpApprox. Amps/hp 2.75 2.41.2 0.96 .24 .14

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General Effect of Voltage and FrequencyVariations on InductionMotor Characteristics

CharacteristicVoltage

110% 90%Starting Torque Up 21% Down 19%Maximum Torque Up 21%Down 19%Percent Slip Down 15-20% Up 20-30%Efciency - Full Load Down0-3% Down 0-2%3/4 Load 0 - Down Slightly Little Change1/2 Load Down0-5% Up 0-1%Power Factor - Full Load Down 5-15% Up 1-7%3/4 LoadDown 5-15% Up 2-7%1/2 Load Down 10-20% Up 3-10%Full Load CurrentDown Slightly to Up 5% Up 5-10%Starting Current Up 10% Down 10%FullLoad - Temperature Rise Up 10% Down 10-15%Maximum Overload CapacityUp 21% Down 19%

Magnetic Noise Up Slightly Down Slightly

CharacteristicFrequency

105% 95%Starting Torque Down 10% Up 11%Maximum Torque Down 10%Up 11%Percent Slip Up 10-15% Down 5-10%

Efciency - Full Load Up Slightly Down Slightly3/4 Load UpSlightly Down Slightly1/2 Load Up Slightly Down SlightlyPowerFactor - Full Load Up Slightly Down Slightly3/4 Load Up SlightlyDown Slightly1/2 Load Up Slightly Down SlightlyFull Load CurrentDown Slightly Up SlightlyStarting Current Down 5% Up 5%Full Load -Temperature Rise Down Slightly Up SlightlyMaximum Overload CapacityDown Slightly Up SlightlyMagnetic Noise Down Slightly UpSlightly

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Allowable Ampacities of Not More Than ThreeInsulatedConductors

Rated 0-2000 Volts, 60 to 90C (140 to 194F), in Racewayor Cableor Earth (directly buried). Based on ambient air temper-ature of30C (86F).

AWGkcmil

Temperature Rating of Copper Conductor60C (140F)

TypesTW, UF

75C (167F)Types

FEPW, RH, RHW,THHW, THW, THWN,

XHHW, USE, ZW

90C (194F)Types

TA,TBS, SA, SIS, FEP, FEPB,MI, RHH, RHW-2, THHN,

THHW, THW-2, USE-2, XHH,XHHW, XHHW-2, ZW-2

18 1416 1814 20 20 2512 25 25 3010 30 35 408 40 50 556 55 65 75470 85 953 85 100 1102 95 115 1301 110 130 150

1/0 125 150 1702/0 145 175 1953/0 165 200 225

4/0 195 230 260250 215 255 290300 240 285 320350 260 310 350400280 335 380500 320 380 430600 355 420 475

700 385 460 520750 400 475 535800 410 490 555900 435 520 585

1000 455 545 6151250 495 590 6651500 520 625 7051750 545 6507352000 560 665 750

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Allowable Ampacities of Not More Than ThreeInsulatedConductors

Unless otherwise specically permitted elsewhere in this Code,the overcurrent pro-tection for conductor types marked with anobelisk () shall not exceed 15 amperes forNo. 14, 20 amperes forNo. 12, and 30 amperes for No. 10 copper, or 15 amperes forNo. 12and 25 amperes for No. 10 aluminum and copper-clad aluminum afterany cor-rection factors for ambient temperature and number ofconductors have been applied.Adapted from NFPA 70-1993, NationalElectrical Code, Copyright 1992.

AWGkcmil

Temperature Rating ofAluminum or Copper-Clad Conductor60C(140F)

TypesTW, UF

75C (167F)Types

RH, RHW, THHW,THW, THWN, XHHW,

USE

90C (194F)Types

TA,TBS, SA, SIS, THHN,THHW,THW-2, THWN-2, RHH,

RHW-S, USE-2, XHH, XHHW,XHHW-2, ZW-2

12 20 20 25

10 25 30 358 30 40 456 40 50 604 55 65 753 65 75 852 75 90 100185 100 115

1/0 100 120 1352/0 115 135 1503/0 130 155 1754/0 150 180 205250170 205 230300 190 230 255350 210 250 280400 225 270 305500 260 310350600 285 340 385700 310 375 420750 320 385 435800 330 395 450900355 425 480

1000 375 445 5001250 405 485 5451500 435 520 5851750 455 5456152000 470 560 630

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Belt DrivesMost fan drive systems are based on the standard "V"drive

belt which is relatively efficient and readily available. Theuse ofa belt drive allows fan RPM to be easily selected throughacombination of AC motor RPM and drive pulley ratios.

In general select a sheave combination that will result inthecorrect drive ratio with the smallest sheave pitchdiameters.Depending upon belt cross section, there may besomeminimum pitch diameter considerations. Multiple belts andsheavegrooves may be required to meet horsepower

requirements.

V-belt Length FormulaOnce a sheave combination is selected wecan calculate

approximate belt length. Calculate the approximate V-beltlengthusing the following formula:

L = Pitch Length of BeltC = Center Distance of SheavesD = PitchDiameter of Large Sheaved = Pitch Diameter of Small Sheave

Belt Drive Guidelines1. Drives should always be installed withprovision for center

distance adjustment.2. If possible centers should not exceed 3times the sum of

the sheave diameters nor be less than the diameter of thelargesheave.

3. If possible the arc of contact of the belt on thesmallersheave should not be less than 120.

4. Be sure that shafts are parallel and sheaves are inproperalignment. Check after first eight hours of operation.

5. Do not drive sheaves on or off shafts. Be sure shaftandkeyway are smooth and that bore and key are of correctsize.

6. Belts should never be forced or rolled over sheaves.Morebelts are broken from this cause than from actual failureinservice.

7. In general, ideal belt tension is the lowest tension atwhich

the belt will not slip under peak load conditions. Checkbelttension frequently during the first 24-48 hours ofoperation.

Motor RPM desired fan RPM

Drive Ratio =

L = 2C+1.57 (D+d)+ 4C

(D-d) 2

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Range of drive losses for standard belts

Estimated Belt Drive Loss

Higher belt speeds tend to have higher losses than lowerbeltspeeds at the same horsepower.

Drive losses are based on the conventional V-belt which hasbeenthe work horse of the drive industry for several decades.

Example: Motor power output is determined to be 13.3 hp. Thebelts are the standard type and just warm to the touch

immediately after shutdown. From the chart above, the drive loss= 5.1% Drive loss = 0.051 x 13.3 = 0.7 hp Fan power input = 13.3 -0.7 hp = 12.6 hp

100

8060

4030

2015

1086

43

1

1.52

0 . 3

0 . 4

0 . 6

0 . 8 1 2 3 4 6 8 1 0 2 0 3 0 4 0 6 0 8 0

1 0 0

2 0 0

3 0 0

4 0 0

6 0 0

,

Motor Power Output, hp

Adapted from AMCA Publication 203-90.

Range of drive losses for standard belts

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Bearing LifeBearing life is determined in accordance withmethods pre-

scribed in ISO 281/1-1989 or the Anti Friction BearingManufac-

turers Association (AFBMA) Standards 9 and 11, modied tofollowthe ISO standard. The life of a rolling element bearing isdened asthe number of operating hours at a given load andspeed the bearingis capable of enduring before the rst signs offailure start tooccur. Since seemingly identical bearings underidentical operatingconditions will fail at different times, life isspecied in bothhours and the statistical probability that a cer-

tain percentage of bearings can be expected to fail withinthattime period.

Example:A manufacturer species that the bearings supplied in apartic-

ular fan have a minimum life of L-10 in excess of 40,000 hoursatmaximum cataloged operating speed. We can interpretthisspecication to mean that a minimum of 90% of the bearingsinthis application can be expected to have a life of at least40,000hours or longer. To say it another way, we should expect lessthan 10% of the bearings in this application to fail within 40,000hours.

L-50 is the term given to Average Life and is simply equal to5times the Minimum Life. For example, the bearing speciedabove hasa life of L-50 in excess of 200,000 hours. At least 50% of thebearings in this application would be expected to have a life of200,000 hours or longer.

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General Ventilation Locate intake and exhaust fans to make useof prevailing

winds. Locate fans and intake ventilators for maximumsweeping

effect over the working area. If lters are used on gravityintake, size intake ventilator to

keep intake losses below 1/8 SP. Avoid fans blowing oppositeeach other, When necessary,

separate by at least 6 fan diameters. Use Class B insulatedmotors where ambient temperaturesare expected to be high forair-over motor conditions.

If air moving over motors contains hazardous chemicalsorparticles, use explosion-proof motors mounted in or out oftheairstream, depending on job requirements.

For hazardous atmosphere applications use fans of non-sparkingconstruction.*

Process Ventilation Collect fumes and heat as near the source ofgeneration as

possible. Make all runs of ducts as short and direct aspossible.

Keep duct velocity as low as practical considering captureforfumes or particles being collected.

When turns are required in the duct system use long radiuselbowsto keep the resistance to a minimum (preferably 2ductdiameters).

After calculating duct resistance, select the fan having

reserve capacity beyond the static pressure determined. Use samerationale regarding intake ventilators and motors

as in General Ventilation guidelines above. Install the exhaustfan at a location to eliminate any recircula-

tion into other parts of the plant. When hoods are used, theyshould be sufcient to collect all

contaminating fumes or particles created by the process.*Referto AMCA Standard 99; See page 4.

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Kitchen VentilationHoods and Ducts

Duct velocity should be between 1500 and 4000 fpm Hoodvelocities (not less than 50 fpm over face area between

hood and cooking surface) Wall Type - 80 CFM/ft2 Island Type -125 CFM/ft2

Extend hood beyond cook surface 0.4 x distance betweenhood andcooking surface

Filters Select lter velocity between 100 - 400 fpm Determinenumber of lters required from a manufacturers

data (usually 2 cfm exhaust for each sq. in. of lter areamaxi-mum)

Install at 45 - 60 to horizontal, never horizontal Shield ltersfrom direct radiant heat

Filter mounting height: No exposed cooking ame1-1/2 minimum tolter Charcoal and similar res4 minimum to lter

Provide removable grease drip pan Establish a schedule forcleaning drip pan and lters and fol-

low it diligently

Fans

Use upblast discharge fan Select design CFM based on hood designand duct velocity Select SP based on design CFM and resistance oflters and

duct system Adjust fan specication for expected exhaust airtemperature

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SoundSound Power (W) - the amount of power a source convertstosound in watts.Sound Power Level (LW) - a logarithmic comparisonof soundpower output by a source to a reference sound source,W0(10

-12 watt).LW = 10 log 10 (W/W 0 ) dB

Sound Pressure (P) - pressure associated with sound outputfrom asource. Sound pressure is what the human ear reacts to.SoundPressure Level (Lp) - a logarithmic comparison of soundpressureoutput by a source to a reference sound source,P 0 (2 x 10

-5 Pa).Lp = 20 log 10 (P/P 0 ) dB

Even though sound power level and sound pressure level arebothexpressed in dB, THERE IS NO OUTRIGHT CONVERSION BETWEEN SOUNDPOWER LEVEL AND SOUND PRESSURE LEVEL . A constant sound poweroutput will result in signicantlydifferent sound pressures andsound pressure levels when thesource is placed in differentenvironments.

Rules of ThumbWhen specifying sound criteria for HVAC equipment,refer to

sound power level, not sound pressure level.When comparing soundpower levels, remember the lowest

and highest octave bands are only accurate to about +/-4dB.Lower frequencies are the most difficult to attenuate.

2 x sound pressure (single source) = +3 dB(sound pressurelevel)2 x distance from sound source = -6dB (sound pressurelevel)+10 dB(sound pressure level)= 2 x original loudnessperception

When trying to calculate the additive effect of twosoundsources, use the approximation (logarithms cannot beaddeddirectly) on the next page.

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Rules of Thumb (cont.)

Noise CriteriaGraph sound pressure level for each octave band onNC curve.

Highest curve intercepted is NC level of sound source. SeeNoiseCriteria Curves ., page 34.

Sound Power and Sound Power Level

Difference between

sound pressure levels

dB to add to highest

sound pressure level0 3.01 2.52 2.13 1.84 1.55 1.26 1.07 0.880.69 0.5

10+ 0

Sound Power (Watts)SoundPower

Level dBSource

25 to 40,000,000 195 Shuttle Booster rocket

100,000 170 Jet engine with afterburner10,000 160 Jet aircraftat takeoff

1,000 150 Turboprop at takeoff100 140 Prop aircraft attakeoff

10 130 Loud rock band1 120 Small aircraft engine

0.1 110 Blaring radio

0.01 100 Car at highway speed0.001 90

Axial ventilating fan (2500m3h) Voice shouting

0.0001 80 Garbage disposal unit0.00001 70 Voiceconversationallevel

0.000001 60 Electronic equipment coolingfan0.0000001 50 Ofce airdiffuser0.00000001 40 Small electric clock0.000000001 30 Voice -very soft whisper

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Sound Pressure and Sound Pressure Level

Room Sones dBA Correlation

From ASHRAE 1972 Handbook of Fundamentals

Sound Pressure(Pascals)

Sound

PressureLevel dB Typical Environment

200.0 140 30m from military aircraft at take-off

63.0 130 Pneumatic chipping and riveting(operators position)20.0120 Passenger Jet takeoff at 100 ft.

6.3 110 Automatic punch press(operators position)2.0 100Automatic lathe shop0.63 90 Construction sitepneumatic drilling0.280 Computer printout room0.063 70 Loud radio (in average domesticroom)0.02 60 Restaurant0.0063 50 Conversational speech at 1m0.00240 Whispered conversation at 2m

0.00063 300.0002 20 Background in TV recording studios0.00002 0Normal threshold of hearing

150

1009080706050

40

30

20

10950 60 70 80 90 100

dBA = 33.2 Log (sones) + 28, Accuracy

2dBA

Sound Level dBA

L o u

d n

e s s

, S o n e s

10

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Octave Band Mid-Frequency - Hz

O c

t a v e

B a n

d S o u n

d P r e s s u r e

L e v e

l d B

90

80

70

60

50

40

30

20

1063

70

65

60

55

50

45

40

35

30

25

20

15125 250 500 1000 2000 4000 8000

NoiseCriteriaNC Curves

Approximatethreshold ofhearing forcontinuousnoise

Noise Criteria Curves

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Design Criteria for Room Loudness

Note: Values showns above are room loudness in sones and are notfansone ratings. For additional detail see AMCA publication 302 -Applicationof Sone Rating.

Room Type Sones Room Type Sones

Auditoriums Indoor sports activities Concert and opera halls 1.0to 3 Gymnasiums 4 to 12Stage theaters 1.5 to 5 Coliseums 3 to9Movie theaters 2.0 to 6 Swimming pools 7 to 21Semi-outdooramphi-

theaters 2.0 to 6 Bowling alleys 4 to 12

Lecture halls 2.0 to 6 Gambling casinos 4 to 12Multi-purpose 1.5to 5 Manufacturing areas Courtrooms 3.0 to 9 Heavy machinery 25 to60Auditorium lobbies 4.0 to 12 Foundries 20 to 60TV audiencestudios 2.0 to 6 Light machinery 12 to 36

Churches and schools Assembly lines 12 to 36Sanctuaries 1.7 to 5Machine shops 15 to 50

Schools & classrooms 2.5 to 8 Plating shops 20 to50Recreation halls 4.0 to 12 Punch press shops 50 to 60Kitchens 6.0to 18 Tool maintenance 7 to 21Libraries 2.0 to 6 Foremans ofce 5 to15Laboratories 4.0 to 12 General storage 10 to 30Corridors andhalls 5.0 to 15 Ofces

Hospitals and clinics Executive 2 to 6Private rooms 1.7 to 5Supervisor 3 to 9Wards 2.5 to 8 General open ofces 4 to12Laboratories 4.0 to 12 Tabulation/computation 6 to 18Operatingrooms 2.5 to 8 Drafting 4 to 12Lobbies & waiting rooms 4.0 to12 Professional ofces 3 to 9Halls and corridors 4.0 to 12Conference rooms 1.7 to 5

Board of Directors 1 to 3Halls and corridors 5 to 15

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Design Criteria for Room Loudness (cont.)

Note: Values showns above are room loudness in sones and are notfansone ratings. For additional detail see AMCA publication 302 -Applicationof Sone Rating.

Room Type Sones Room Type Sones

Hotels Public buildings Lobbies 4.0 to 12 Museums 3 to 9Banquetrooms 8.0 to 24 Planetariums 2 to 6Ball rooms 3.0 to 9 Post ofces 4to 12Individual rooms/suites 2.0 to 6 Courthouses 4 to 12Kitchensand laundries 7.0 to 12 Public libraries 2 to 6Halls and corridors4.0 to 12 Banks 4 to 12Garages 6.0 to 18 Lobbies and corridors 4 to12

Residences Retail stores Two & three family units 3 to 9Supermarkets 7 to 21

Apartment houses 3 to 9 Department stores(main oor) 6 to 18

Private homes (urban) 3 to 9 Department stores(upper oor) 4 to12

Private homes(rural & suburban) 1.3 to 4 Small retail stores6 to 18

Restaurants Clothing stores 4 to 12Restaurants 4 to 12Transportation (rail, bus, plane)Cafeterias 6 to 8 Waiting rooms 5to 15co*cktail lounges 5 to 15 Ticket sales ofce 4 to 12

Social clubs 3 to 9 Control rooms & towers 6 to 12Nightclubs 4 to 12 Lounges 5 to 15Banquet room 8 to 24 Retail shops 6 to18

Miscellaneous Reception rooms 3 to 9Washrooms and toilets 5 to15Studios for sound

reproduction1 to 3

Other studios 4 to 12

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VibrationSystem Natural Frequency

The natural frequency of a system is the frequency at whichthesystem prefers to vibrate. It can be calculated by the follow-ingequation:

fn = 188 (1/d)1/2 (cycles per minute)

The static deection corresponding to this natural frequencycanbe calculated by the following equation:

d = (188/fn

)2 (inches)

By adding vibration isolation, the transmission of vibrationcanbe minimized. A common rule of thumb for selection ofvibrationisolation is as follows:

Critical installations are upper oor or roof mountedequipment.Non-critical installations are grade level or basem*ntoor.

Always use total weight of equipment when selectingisolation.Always consider weight distribution of equipment inselection.

EquipmentRPM

Static Deection of IsolationCritical

InstallationNon-criticalInstallation

1200+ 1.0 in 0.5 in600+ 1.0 in 1.0 in400+ 2.0 in 1.0 in300+ 3.0in 2.0 in

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Vibration SeverityUse the Vibration Severity Chart to determineacceptability of vibration

levels measured.

Vibration Frequency - CPM

10.008.006.00

4.003.00

2.00

1.000.800.60

0.400.30

0.20

0.100.080.060.040.030.02

0.010.0080.006

0.0040.003

0.002

0.001

1 0 0

2 0 0

3 0 0

4 0 0

5 0 0

1 0 0 0

1 2 0 0

1 8 0 0

2 0 0 0

3 0 0 0

3 6 0 0

4 0 0 0

5 0 0 0

1 0 0 0 0

2 0 0 0 0

3 0 0 0 0

4 0 0 0 0

5 0 0 0 0

1 0 0 0 0 0

1 2

0 0

1 8

0 0

3 6

0 0

Vibration Velocity - In/sec.-Peak

Values shown are forfiltered readings takenon the machinestructureor bearing cap

V E R Y S M O O T H

R O U G H

V E R Y R O U G H

S L I G H T L Y R O U G H S M O

O T H E X T R E M E L Y S M O O T H

V E R Y G O O D

G O O D

F A I R

. 0 0 4 9 I N / S E C

. 0 0 9 8 I N / S E C

. 0 1 9 6 I N / S E C

. 0 3 9 2 I N / S E C

. 0 7 8 5 I N / S E C

. 1 5 7 I N / S E C

. 3 1 4 I N / S E C

. 6 2 8 I N / S E C

Vibration Frequency - CPM

Vibration Displacement-Mils-Peak-to-Peak

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Vibration Severity (cont.)When using the Machinery VibrationSeverity Chart, the

following factors must be taken into consideration:1. When usingdisplacement measurements only filtered

displacement readings (for a specific frequency) shouldbeapplied to the chart. Unfiltered or overall velocity readingscanbe applied since the lines which divide the severityregions are, infact, constant velocity lines.

2. The chart applies only to measurements taken on thebearingsor structure of the machine. The chart does notapply tomeasurements of shaft vibration.

3. The chart applies primarily to machines which arerigidlymounted or bolted to a fairly rigid foundation.Machinesmounted on resilient vibration isolators such as coilspringsor rubber pads will generally have higher amplitudesofvibration than those rigidly mounted. A general rule is toallowtwice as much vibration for a machine mounted on

isolators. However, this rule should not be applied tohighfrequencies of vibration such as those characteristic ofgearsand defective rolling-element bearings, as theamplitudes measuredat these frequencies are lessdependent on the method of machinemounting.

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Air Quality MethodDesigning for acceptable indoor air qualityrequires that we

address: Outdoor air quality Design of the ventilation systemsSources of contaminants Proper air ltration System operation andmaintenance

Determine the number of people occupying the respectivebuildingspaces. Find the CFM/person requirements in Ventila-tion Rates forAcceptable Indoor Air Quality, page 42. Calculatethe requiredoutdoor air volume as follows:

People = Occupancy/1000 x Floor Area (ft 2 ) CFM = People xOutdoor Air Requirement (CFM/person)

Outdoor air quantities can be reduced to lower levels ifproperparticulate and gaseous air ltration equipment isutilized.

Air Change MethodFind total volume of space to be ventilated.Determine the

required number of air changes per hour.

CFM = Bldg. Volume (ft 3 ) / Air Change Frequency

Consult local codes for air change requirements or, in absenceofcode, refer to Suggested Air Changes, page 41.

Heat Removal MethodWhen the temperature of a space is higherthan the ambient

outdoor temperature, general ventilation may be utilized topro-vide free cooling. Knowing the desired indoor and thedesignoutdoor dry bulb temperatures, and the amount of heatremovalrequired (BTU/Hr):

CFM = Heat Removal (BTU/Hr) / (1.10 x Temp diff)

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41

Suggested Air Changes

Type of Space

Air Change

Frequency(minutes)

Assembly Halls 3-10Auditoriums 4-15Bakeries 1-3Boiler Rooms2-4Bowling Alleys 2-8Dry Cleaners 1-5Engine Rooms 1-1.5Factories(General) 1-5Forges 1-2Foundries 1-4Garages 2-10

Generating Rooms 2-5Glass Plants 1-2Gymnasiums 2-10Heat TreatRooms 0.5-1Kitchens 1-3Laundries 2-5Locker Rooms 2-5Machine Shops3-5Mills (Paper) 2-3Mills (Textile) 5-15Packing Houses2-15Recreation Rooms 2-8Residences 2-5

Restaurants 5-10Retail Stores 3-10Shops (General) 3-10Theaters3-8Toilets 2-5Transformer Rooms 1-5Turbine Rooms 2-6Warehouses2-10

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Ventilation Rates for Acceptable Indoor Air Quality

Adapted from ASHRAE Standard 62-1989 Ventilation for AcceptableIndoor Air Qual- ity.

SpaceOutdoor Air

Required(CFM/person)

Occupancy

(People/1000 ft 2)Auditoriums 15 150Ballrooms/Discos 25 100Bars30 100Beauty Shops 25 25Classrooms 15 50

Conference Rooms 20 50Correctional Facility Cells 20 20DormitorySleeping Rooms 15 20Dry Cleaners 30 30Gambling Casinos 30 120GameRooms 25 70Hardware Stores 15 8Hospital Operating Rooms 3020Hospital Patient Rooms 25 10Laboratories 20 30Libraries 1520Medical Procedure Rooms 15 20Ofce Spaces 20 7

Pharmacies 15 20Photo Studios 15 10Physical Therapy 1520Restaurant Dining Areas 20 70Retail Facilities 15 20SmokingLounges 60 70Sporting Spectator Areas 15 150Supermarkets 158Theaters 15 150

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Heat Gain From Occupants of Conditioned Spaces 1

Notes: 1 Tabulated values are based on 78F for dry-bulbtempera-

ture.2 Adjusted total heat value for sedentary work,restaurant,

includes 60 Btuh for food per individual (30 Btu sensible and30Btu latent).

3

For bowling gure one person per alley actually bowling, andallothers as sitting (400 Btuh) or standing (55 Btuh).* Use sensiblevalues only when calculating ventilation to

remove heat.Adapted from Chapter 26 ASHRAE FundamentalsHandbook, 1989.

Typical Application Sensible Heat

(BTU/HR)*

Latent Heat

(BTU/HR)Theater-Matinee 200 130Theater-Evening 215 135Ofces,Hotels, Apartments 215 185Retail and Department Stores 220 230DrugStore 220 280Bank 220 280Restaurant 2 240 310Factory 240 510DanceHall 270 580Factory 330 670Bowling Alley3 510 940Factory 510940

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Heat Gain From Typical Electric Motors

Adapted from Chapter 26 ASHRAE Fundamentals Handbook, 1989.

MotorName-

plate orRatedHorse-power

MotorType

Nominalrpm

Full LoadMotorEf-

ciency inPercent

Motor In,DrivenEquip-ment inSpaceBtuh

Motor

Out,DrivenEquip-ment inSpaceBtuh

Motor

2ndDrivenEquip-

ment Outof Space

Btuh0.25 Split Ph. 1750 54 1,180 640 5400.33 Split Ph. 1750 561,500 840 660

0.50 Split Ph. 1750 60 2,120 1,270 8500.75 3-Ph. 1750 72 2,6501,900 740

1 3-Ph. 1750 75 3,390 2,550 8501 3-Ph. 1750 77 4,960 3,8201,1402 3-Ph. 1750 79 6,440 5,090 1,3503 3-Ph. 1750 81 9,430 7,6401,7905 3-Ph. 1750 82 15,500 12,700 2,790

7,5 3-Ph. 1750 84 22,700 19,100 3,64010 3-Ph. 1750 85 29,90024,500 4,49015 3-Ph. 1750 86 44,400 38,200 6,21020 3-Ph. 1750 8758,500 50,900 7,61025 3-Ph. 1750 88 72,300 63,600 8,68030 3-Ph.1750 89 85,700 76,300 9,44040 3-Ph. 1750 89 114,000 102,00012,60050 3-Ph. 1750 89 143,000 127,000 15,70060 3-Ph. 1750 89172,000 153,000 18,90075 3-Ph. 1750 90 212,000 191,000 21,200

100 3-Ph. 1750 90 283,000 255,000 28,300125 3-Ph. 1750 90353,000 318,000 35,300150 3-Ph. 1750 91 420,000 382,000 37,8002003-Ph. 1750 91 569,000 509,000 50,300250 3-Ph. 1750 91 699,000636,000 62,900

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Rate of Heat Gain From Commercial CookingAppliances inAir-Conditioned AreaApplianceGas-Burning,Floor Mounted Type

Manufacturers Input Rating

Watts Btuh Heat gainWith Hood

Broiler, unit 70,000 7,000Deep fat fryer 100,000 6,500Oven,deck,

per sq. ft of hearth area 4,000 400

Oven, roasting 80,000 8,000Range, heavy duty -

Top section 64,000 6,400

Range, heavy duty - Oven 40,000 4,000Range, jr., heavy duty-

Top section 45,000 4,500

Range, jr., heavy duty - Oven 35,000 3,500Range, restuaranttype

per 2-burner section24,000 2,400

per oven 30,000 3,000per broiler-griddle 35,000 3,500

Electric, Floor Mounted TypeGriddle 16,800 57,300 2,060Broiler,no oven 12,000 40,900 6,500

with oven 18,000 61,400 9,800

Broiler, single deck 16,000 54,600 10,800Fryer 22,000 75,000730Oven, baking,

per sq. ft of hearth 500 1,700 270

Oven, roasting,per sq. ft of hearth 900 3,070 490

Range, heavy duty -Top section 15,000 51,200 19,100

Range, heavy duty - Oven 6,700 22,900 1,700Range, medium duty-

Top section 8,000 27,300 4,300

Range, medium duty - Oven 3,600 12,300 1,900Range, light duty -Top section 6,600 22,500 3,600Range, light duty - Oven 3,000 10,2001,600

Adapted from Chapter 26 ASHRAE Fundamentals Handbook, 1989

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46

Rate of Heat Gain From Miscellaneous Appliances

Adapted from Chapter 26 ASHRAE Fundamentals Handbook, 1989.

*Use sensible heat gain for ventilation calculation .FilterComparison

Electrical

Appliances

ManufacturersRating

Recommended Rate ofHeat Gain, Btuh

Watts Btuh *Sensible Latent TotalHair dryer 1,580 5,400 2,300400 2,700Hair dryer 705 2,400 1,870 330 2,200Neon sign, 30 30

per linear ft of tube 60 60Sterilizer, instrument 1,100 3,750650 1,200 1,850Gas-Burning AppliancesLab burners

Bunsen 3,000 1,680 420 2,100

Fishtail 5,000 2,800 700 3,500Meeker 6,000 3,360 840 4,200

Gas Light, per burner 2,000 1,800 200 2,000Cigar lighter 2,500900 100 1,000

Filter TypeASHRAE

ArrestanceEfciency

ASHRAEAtmo-

sphericDust SpotEfciency

InitialPressure

Drop(IN.WG)

FinalPressure

Drop(IN.WG)

Permanent 60-80% 8-12% 0.07 .5Fiberglass Pad 70-85% 15-20% 0.17.5Polyester Pad 82-90% 15-20% 0.20 .52 Throw Away 70-85% 15-20%0.17 .52 Pleated Media 88-92% 25-30% 0.25 .5-.860% Cartridge 97%60-65% 0.3 1.080% Cartridge 98% 80-85% 0.4 1.090% Cartridge 99%90-95% 0.5 1.0HEPA 100% 99.97% 1.0 2.0

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0 . 0 0 0 1

0 . 0 0 1

0 . 0 1

0 . 1

1

1 0

1 0 0

1 0 0 0

1 0 0 0 0

R a i n

T o b a c c o

S m o k e

M i s t s

D i a m e

t e r o

f

H u m a n

H a i r H

e a v y

I n d u s t . D

u s t

O i l S m o k e

F o g

Y e a s

t - C e l

l s

V i s i b l e B y

H u m a n

E y e

G a s

M o l e c u l e s

V i r u s

B a c

t e r i a

P o l l e n

P l a n t

S p o r e s

M o l

d s

X - r a y s

E l e c t r o n i c - M

i c r o s c o p e

U n s e t

t l i n g - A t m o s p h e r

i c - I m p u r i t

i e s

F u m e s

L u n g - D a m a g i n g - P a r

t i c l e s

U l t r a -

V i o l e t

V i s i b l e

I n f r a - R e d

F l y -

A s h

M i c r o s c o p e

D u s

t s

S e t

t l i n g - A

t m o s . - I

m p u r .

R e l a t

i v e S

i z e

C h a r t o f

C o m m o n

A i r C o n

t a m i n a n

t s

M ic ro n

0 .3

T h i s D i m e n s

i o n

R e p r e s e n t s

t h e D i a m e t e r o f a

H u m a n

H a i r ,

1 0 0 M i c r o n s

1 M i c r o n =

1 m

i c r o m e t e r =

1 m

i l l i o n t

h o f a

m e t e r

T h i s

r e p r e s e n

t s a

1 0 m

i c r o n

d i a m .

p a r t i c l e

, t h e

s m a l l e s t s i z e

v i s i b l e w

i t h t h e

h u m a n e y e .

T h i s r e p r e s e n

t s a

0 . 3

m i c r o n

d i a m e t e r

p a r t i c l e

. T h i s

i s t h e m o s t

r e s p i r a

b l e ,

l u n g

d a m a g i n g

p a r t i c l e s i z e .

0 . 0 0 0 1

0 . 0 0 1

0 . 0 1

0 . 1

1

1 0

1 0 0

1 0 0 0

1 0 0 0 0

Relative Size Chart of Common Air Contaminants

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48

Optimum Relative Humidity Ranges for Health

Bacteria

Viruses

Fungi

Mites

Respiratory

Infections

1

Allergic Rhinitis

and Asthma

Chemical

Interactions

Ozone

Production

Optimal

Zone

Decrease in Bar Width

IndicatesDecrease in Effect

10

20

30

40

50

60

70

80

90

Per Cent Relative Humidity

1INSUFFICIENT DATA

ABOVE50% R.H.

Optimum relative humidity ranges for health as found byE.M.Sterling in "Criteria for Human Exposure to Humidity in

Occupied Buildings."ASHRAEW

inter Meeting, 1985.

Optim

um Relative Hum

idity Ranges forHealth

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1 0 0

2 0 0

3 0 0

4 0 0

5 0 0

1 0 0 0

2 0 0 0

3 0 0 0

4 0 0 0

5 0 0 0

1.5

1.0

0.5

0.40.3

0.2

0.1

0.050.04

0.03

0.02

0.01

CFMSq. Ft. Damper AreaV (Velocity) =

DAMPER FACE VELOCITY -fpm

P R E S S U R E

L O S S -

I n c

h e s w . g .

Damper Pressure Drop

Adapted from HVAC Systems Duct Design, Third Edition, 1990,SheetMetal & Air Conditioning Contractors National Association .

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0.20.4

0.3

0.2

0.1

0.050.04

0.03

0.02

0.01

0.0050.0040.003

0.002

0.001

Insect Screen

1 0 0

2 0 0

3 0 0

4 0 0

5 0 0

3 0 0 0

4 0 0 0

5 0 0 0

1 0 0 0

2 0 0 0

1/2 in.Mesh Bird Screen

P R E S S U R E L O S S

i n c h e s w . g .

FACE AREA VELOCITYfpm

0.6

Screen Pressure Drop

Adapted from HVAC Systems Duct Design, Third Edition, 1990,SheetMetal & Air Conditioning Contractors National Association .

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Rectangular Equivalent of Round Ducts

S i d e o

f D u c t

( a )

Side of Duct (b)

500

400

300

200

1009080706050

40

30

20

10987

65

4

3

2

1 2 3 4 5 6 8 10 20 30 40 50 6080100

2

3

4

5 6

7

8 9

1 0

1 2

1 4

1 6

1 8

2 0 2 2

2 4 2 6

2 8

3 0 3 2

3 4

3 6 3 8

4 0

4 5

5 0

5 5

6 0 6 5

7 0 7 5

8 0

9 0

1 0 0

d=1.2655

(ab) 3(a + b)

D i a m e t e r ( d )

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Typical Design Velocities for HVAC Components*

* Adapted from ASHRAE Pocket Guide, 1993

Intake Louvers Velocity (FPM)

7000 cfm and greater 400Exhaust Louvers

5000 cfm and greater 500Panel Filters

Viscous Impingement 200 to 800 Dry-Type, Pleated Media:

Low Efciency 350 Medium Efciency 500 High Efciency 500 HEPA250

Renewable Media Filters Moving-Curtain Viscous Impingement 500Moving-Curtain Dry-Media 200

Electronic Air Cleaners Ionizing-Plate-Type 300 to 500Charged-Media Non-ionizing 250 Charged-Media Ionizing 150 to350

Steam and Hot Water Coils500 to 600200 min.

1500 maxElectric Coils

Open Wire Refer to Mfg. Data Finned Tubular Refer to Mfg.Data

Dehumidifying Coils 500 to 600Spray-Type Air Washers 300 to600Cell-Type Air Washers Refer to Mfg. Data

High-Velocity, Spray-Type Air Washers 1200 to 1800

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Velocity and Velocity Pressure Relationships

For calculation of velocity pressures at velocities other thanthoselisted above: P v = (V/4005)

2

For calculation of velocities when velocity pressures areknown:

Velocity(fpm)

Velocity Pressure(in wg)

Velocity(fpm)

Velocity Pressure(in wg)

300 0.0056 3500 0.7637400 0.0097 3600 0.8079500 0.0155 37000.8534600 0.0224 3800 0.9002700 0.0305 3900 0.9482800 0.0399 40000.9975900 0.0504 4100 1.0480

1000 0.0623 4200 1.09971100 0.0754 4300 1.15271200 0.0897 44001.20691300 0.1053 4500 1.26241400 0.1221 4600 1.31911500 0.14024700 1.37711600 0.1596 4800 1.4364

1700 0.1801 4900 1.49681800 0.2019 5000 1.55861900 0.2250 51001.62152000 0.2493 5200 1.68572100 0.2749 5300 1.75122200 0.30175400 1.81792300 0.3297 5500 1.88592400 0.3591 5600 1.955125000.3896 5700 2.02562600 0.4214 5800 2.09722700 0.4544 59002.17012800 0.4887 6000 2.24432900 0.5243 6100 2.31983000 0.56106200 2.39653100 0.5991 6300 2.47443200 0.6384 6400 2.553633000.6789 6500 2.63403400 0.7206 6600 2.7157

(Vp )V=4005

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U.S. Sheet Metal Gauges

*Aluminum is specied and purchased by material thickness ratherthan gauge.

Gauge No.

Steel

(Manuf. Std. Ga.)

Galvanized

(Manuf. Std. Ga.)Thick. in. Lb./ft. 2 Thick.in. Lb./ft. 2

26 .0179 .750 .0217 .90624 .0239 1.00 .0276 1.15622 .0299 1.25.0336 1.40620 .0359 1.50 .0396 1.656

18 .0478 2.00 .0516 2.15616 .0598 2.50 .0635 2.65614 .0747 3.125.0785 3.28112 .1046 4.375 .1084 4.53110 .1345 5.625 .1382 5.7818.1644 6.875 .1681 7.0317 .1793 7.50

Gauge No.Mill Std. Thick

Aluminum*Stainless Steel

(U.S. Standard Gauge)

Thick. in. Lb./ft. 2 Thick.in. Lb./ft. 2

26 .020 .282 .0188 .787524 .025 .353 .0250 1.05022 .032 .452.0312 1.31320 .040 .564 .0375 1.57518 .050 .706 .050 2.10016 .064.889 .062 2.62514 .080 1.13 .078 3.28112 .100 1.41 .109 4.594

10 .125 1.76 .141 5.9068 .160 2.26 .172 7.2187 .190 2.68 .1887.752

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Recommended Metal Gauges for Duct

Wind Driven Rain Louvers

A new category of product has emerged recently calledawind-driven rain louver. These are architectural louversdesignedto reject moisture that are tested and evaluated undersimulatedwind driven rain conditions. Since these are relativelynew prod-ucts, several different test standards have emerged toevaluatethe performance of these products under severe wind andrainweather conditions. In addition, manufacturers havedevelopedtheir own standards to help evaluate the rain resistanceof theirproducts. Specifying engineers should become familiar withthedifferences in various rain and pressure drop test standardstocorrectly evaluate each manufacturers claims. Four teststan-dards are detailed below:

Table from AMCA Supplement to ASHRAE Journal, September1998.*AMCA Louver Engineering Committee at this writing iscurrently updatingAMCA 500-L to allow testing of varying sizes,wind speed, and rainfallintensity and is developing a CertiedRatings Program for this productcategory.

Rectangular Duct Round DuctGreatest

DimensionU.S.ga.

B&Sga. Diameter

Galv. SteelU.S. ga.

AluminumB&S ga.

to 30 in. 24 22 to 8 in. 24 2231-60 22 20 9-24 22 2061-90 20 1825-48 20 1891-up 18 16 49-72 18 16

Dade Co.Test

Power PlantTest

AMCA 500Test*

HEVACTest

Wind Velocitym/s (mph)

16-50(35 - 110)

22(50) 0

13.5(30)

Rain Fall Ratemm/h (in./h)

220(8.8)

38-280(1.5 to 10.9)

100(4)

75(3)

Wet Wall WaterFlow RateL/s (gpm)

0 0 0.08(1.25) 0

Airow Through

Louverm/s (fpm) 0

6.35 (1,250)

Free AreaVelocity

6.35 (1,250)

Free AreaVelocity

3.6 (700)

Free CoreArea Velocity

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Moisture and Air RelationshipsASHRAE has adopted pounds ofmoisture per pound of dry air

as standard nomenclature. Relations of other units areexpressedbelow at various dewpoint temperatures.

a 7000 grains = 1 lb b Compared to 70F saturated

Normally the sensible heat factor determines the cfm requiredtoaccept a load. In some industrial applications the latentheatfactor may control the air circulation rate.

Adapted from Numbers, by Bill Hollady & Cy Otterholm1985.

Equiv.Dew Pt., F

Lb H 20/lbdry air

Parts permillion

Grains/lbdry air a

PercentMoisture % b

-100 0.000001 1 0.0007 -90 0.000002 2 0.0016 -80 0.000005 50.0035 -70 0.00001 10 0.073 0.06-60 0.00002 21 0.148 0.13-500.00004 42 0.291 0.26-40 0.00008 79 0.555 0.5-30 0.00015 146 1.020.9-20 0.00026 263 1.84 1.7-10 0.00046 461 3.22 2.9

0 0.0008 787 5.51 5.0

10 0.0013 1,315 9.20 8.320 0.0022 2,152 15.1 13.630 0.0032 3,15424.2 21.840 0.0052 5,213 36.5 33.050 0.0077 7,658 53.6 48.4600.0111 11,080 77.6 70.270 0.0158 15,820 110.7 100.0

80 0.0223 22,330 156.3 90 0.0312 31,180 218.3 100 0.0432 43,190302.3

Thus cfm = Latent heat 1 Btu/h(W1 - W2) x 4840

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Properties of Saturated Steam

Based on 1967 ASME Steam Tables

Temperature

F

Pressure

PSIA

Specic Volume Specic EnthalpySat. Vapor

Ft 3/lbmSat. Liquid

Btu/lbmSat. Vapor

Btu/lbm32 0.08859 3304.7 -0.0179 1075.540 0.12163 2445.8 8.0271079.060 0.25611 1207.6 28.060 1087.780 0.50683 633.3 48.0371096.4

100 0.94924 350.4 67.999 1105.1120 1.6927 203.26 87.97 1113.61402.8892 123.00 107.95 1122.0160 4.7414 77.29 127.96 1130.2180 7.511050.22 148.00 1138.2200 11.526 33.639 168.09 1146.0212 14.696 26.799180.17 1150.5220 17.186 23.148 188.23 1153.4240 24.968 16.321208.45 1160.6

260 35.427 11.762 228.76 1167.4280 49.200 8.644 249.17 1173.830067.005 6.4658 269.7 1179.7320 89.643 4.9138 290.4 1185.2340 117.9923.7878 311.3 1190.1360 153.010 2.9573 332.3 1194.4380 195.7292.3353 353.6 1198.0400 247.259 1.8630 375.1 1201.0420 308.7801.4997 396.9 1203.1440 381.54 1.21687 419.0 1204.4460 466.870.99424 441.5 1204.8480 566.15 0.81717 464.5 1204.1500 680.860.67492 487.9 1202.2520 812.53 0.55957 512.0 1199.0540 962.790.46513 536.8 1194.3560 1133.38 0.38714 562.4 1187.7580 1326.170.32216 589.1 1179.0600 1543.2 0.26747 617.1 1167.7620 1786.90.22081 646.9 1153.2640 2059.9 0.18021 679.1 1133.7660 2365.70.14431 714.9 1107.0680 2708.6 0.11117 758.5 1068.5

700 3094.3 0.07519 822.4 995.2705.47 3208.2 0.05078 906.0906.0

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Cooling Load Check Figures

Heating & Refrigeration

C l a s s

i c a

t i o n

O c c u p a n c y

S q .

F t / P e r s o n

L i g h

t s

W a t

t s / S q .

F t .

R e f r i g e r a

t i o n

S q .

F t / T o n

A i r Q u a n

t i t i e s

C F M / S q .

F t .

E a s

t - S o u

t h - W e s

t

N o r

t h

I n t e r n a

l

L o

H i

L o

H i

L o

H i

L o

H i

L o

H i

L o

H i

A p a r t m e n

t , H i g h R i s e

3 2 5

1 0 0

1 . 0

4 . 0

4 5 0

3 5 0

0 . 8

1 . 7

0 . 5

1 . 3

A u d i t o r

i u m s ,

C h u r c

h e s ,

T h e a t e r s

1 5

6

1 . 0

3 . 0

4 0 0

9 0

1 . 0

3 . 0

E d u c a t

i o n a

l F a c

i l i t i e s

S c h o o

l s , C

o l l e g e s ,

U n i v e r s

i t i e s

3 0

2 0

2 . 0

6 . 0

2 4 0

1 5 0

1 . 0

2 . 2

0 . 9

2 . 0

0 . 8

1 . 9

F a c t o r i e s -

A s s e m

b l y

A r e a s

5 0

2 5

3 . 0

6 . 0

2 4