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Engineering Data Catalog t cialis g Spe ndlin ir Ha trial A ndus and I OEM RING INEE ENG DATA 7697 Snider Road, Mason, OH 45040-9135 Telephone: 513-573-0600 Visit us at www.cincinnatifan.com for more information. Catalog ENG-409 Supersedes ENG-203 TABLE OF CONTENTS PAGE PAGE I. Terms and Definitions . 2 XI. Typical Entrance Losses . 10 II. Fan Arrangements . 3 XII. Good Duct Installation Guidelines . 10 III. Rotation and Discharge Designations . 3 XIII. Estimating Static Pressure (10 to 2000 CFM) . 11 IV. Wheel Types . 3 XIV. Estimating Static Pressure (1000 to 100,000 CFM) . 12 V. Fan Laws and Formulas . 4 XV. Noise Factors . 13 VI. Temperature and Altitude Conversions . 5 XVI. Belt Drive Losses . 13 VII. Material Conveying . 6-7 XVII. Area and Circumference of Circles . 14 VIII. Ventilation Guidelines (Air Changes) . 8 XVIII. English and Metric Conversions . 15 IX. Exhaust Hood Velocities . 8 XIX. Decimal and Millimeter Equivalents of Fractions . 15 X. Duct Design Practices . 9 XX. Motor Dimensions and Positions . 16 I. TERMS AND DEFINITIONS AHP. – Air Horsepower, is work done by the fan Free Air Delivery – is the condition under which the performance curve, also a drop in the BHP expressed as horsepower. a fan operates when no static pressure or resist - curve. It is caused by the separation of the air ance is present. flow from the surface of the propeller blade or AHP = CFM x TP HP. – Horsepower, is the actual rated output of fan wheel. 6356 the fan motor used. Shut Off – is the point of operation where the fan BHP. – Brake Horsepower, is the horsepower ab - ME. – Mechanical Efficiency, is the ratio of flow rate is zero. sorbed by the fan. horsepower absorbed (BHP) to horsepower de - System – The path through which air is pushed BTU. – British Thermal Unit, is the amount of livered by the fan (AHP). or pulled. This normally includes ducts, coils, fil - heat required to raise one pound of water from ter, plenum changer, etc., through which air ME = AHP 63˚F to 64˚F. BHP flows. A system can be as simple as inducing air CFM. – Cubic Feet Per Minute, is the volume of Plenum Chamber – is an air compartment main - motion into a space or a network of ducts pro - air moved per minute. tained under pressure to serve one or more dis - viding air for multiple locations. Capture Velocity – The air velocity at any point in tributing ducts. TE. – or Total Efficiency, may be expressed as front of a hood or at the hood opening nec-es - RPM. – Revolutions Per Minute, is the number of TE = CFM x TP sary to overcome opposing air currents and cap - times the fan shaft revolves per minute. 6356 x BHP ture the contaminated air by causing it to flow Replacement Air – The term has been used in TS. – Tip-Speed, is the peripheral speed in feet into the hood. the same context as supply air, make-up, and in - per minute of a propeller tip or fan wheel at any Conveying Velocity – The minimum air velocity take air. It introduces fresh outside air into a specified RPM. required to move or transport particles within a structure to replace air exhausted from fans. TP. – Total Pressure, is the sum of the static duct system. Measured in feet per minute. Standard Air – is air which weighs .075 pounds pressure (SP), and velocity pressure (VP) at any Drive Losses – Power lost in overcoming fric - per cubic foot, which is dry air at 70˚F dry bulb given point in a ventilating system. tion from the belt, pulley and bearing friction. with a barometric pressure of 29.92 inches of V. – Velocity, is equal to the flow rate (CFM) di - EDR. – Equivalent Direct Radiation, is the mercury. vided by the cross-sectional area of the air flow. amount of heating surface which will give off 240 SE. – Static Efficiency, is expressed as V = CFM ÷ Area (Sq. Ft.). BTU. per hour. SE = CFM x SP VP. – Velocity Pressure, is equal to the kinetic FPM. – Feet Per Minute, is the velocity of the 6356 x BHP energy per unit volume of the flowing air. It can airstream. be calculated from the formula. Final Temperature – is the temperature of air SP. – Static Pressure, is a measure of the force 2 after passing over heating coils under specified exerted by the fan in moving air through any ven - VP = [FPM ] conditions. tilating system. 4005 Stall – A region of instability on a fan perfor mance curve. Evidence of this region is a dip in Transport Velocity – See Conveying Velocity. 2 II. FAN ARRANGEMENTS AS DEFINED BY AMCA SW - Single Width DW - Double Width SI - Single Inlet DI - Double Inlet ARR. 1 SWSI For belt drive or ARR. 2 SWSI For belt drive or ARR. 3 SWSI For belt drive or ARR. 3 DWDI For belt drive or ARR. 4 SWSI For direct drive. Im - direct connecdtion. Impeller over - direct connection. Impeller over - direct connection. One bearing on direct connection. One bearing on peller overhung on prime mover shaft. hung. Two bearings on base. hung. Bearings in bracket sup - each side and supported by fan each side and supported by fan No bearings on fan. Prime mover base ported by fan housing. housing. housing. mounted or integrally connected. ARR. 7 SWSI For belt drive or ARR. 7 DWDI For belt drive or ARR. 8 SWSI For belt drive or ARR. 9 SWSI For belt drive. Im - ARR. 10 SWSI For belt drive. direct connecdtion.Arrangement 3 direct connection.Arrangement 3 direct connecdtion.Arrangement 1 peller overhung, two bearings, Impeller overhung two bearings, plus base for prime mover. plus base for prime mover. plus extended base for prime with prime mover outside base. with prime mover inside base. mover. III. ROTATION & DISCHARGE DESIGNATIONS IV. WHEEL TYPES Shrouded Radial Blade Clockwise Clockwise Clockwise Clockwise Up Blast Top Angular Up Top Horizontal Top Angular Down CW 360 CW 45 CW 90 CW 135 Backward Clockwise Clockwise Clockwise Clockwise Inclined Down Blast Bottom Angular Down Bottom Horizontal Bottom Angular Up CW 180 CW 225 CW 270 CW 315 Open Radial Blade Counterclockwise Counterclockwise Counterclockwise Counterclockwise Up Blast Top Angular Up Top Horizontal Top Angular Down CCW 360 CCW 45 CCW 90 CCW 135 Open Paddle Wheel Counterclockwise Counter clockwise Counterclockwise Counterclockwise (Not available from Down Blast Bottom Angular Down Bottom Horizontal Bottom Angular Up Cincinnati Fan) CCW 180 CCW 225 CCW 270 CCW 315 Notes: 1. DIRECTION OF ROTATION IS DETERMINED FROM DRIVE SIDE OF FAN. 2. On single inlet fans, drive side is always considered as the side opposite fan inlet. 3. On double inlet fans with drives on both sides, drive side is that with the higher powered drive unit. 4. Direction of discharge is determined in accordance with diagrams. Angle of discharge is Forward Curve referred to the vertical axis of fan and designated in degrees from such standard refer - (Squirrel Cage) ence axis. Angle of discharge may be any intermediate angle as required. 5. For fan inverted for ceiling suspension, or side wall mounting, direction of rotation and discharge is determined when fan is resting on floor. 3 V. FAN LAWS AND FORMULAS 4 VI. TEMPERATURE - ALTITUDE CONVERSIONS Fan performance tables are developed using standard air which is 70˚F., The location of bearings on the fan must be considered when moving 29.92” barometric pressure and .075 lbs. per cubic foot. Density changes high temperature air. Fans with bearings located in the air stream have resulting from temperature or barometric pressure variations (such as temperature limitations. Such fans include: circulators, propeller fans, axial higher altitudes) must be corrected to standard conditions before selecting power roof ventilators, double inlet centrifugal fans and some tubeaxial a fan based on standard performance data. fans. Fans designed for higher temperatures have the bearings located out of the air stream. Most single inlet centrifugal fans and centrifugal power Temperature and/or altitude conversion factors are used in making cor - roof ventilators are designed in this manner. Tubeaxial fans can handle rections to standard conditions. high temperatures when there is a drive bearing tube installed in the air stream to isolate and protect the bearings. Example: Select a belt driven fan to deliver 1500 CFM at 8.6” SP at 200˚F., and 7000’ With the addition of a shaft cooler wheel or heat slinger, a centrifugal fan’s altitude. temperature limits can be extended. The heat slinger absorbs heat from the STEP 1. From the table below, conversion factor is 1.63. fan shaft while circulating air over the inboard bearing to help keep it run - STEP 2. Correct static pressure is: 1.63 x 8.6” SP = 14” SP at standard ning cool. conditions. STEP 3. Check fan catalog for 1500 CFM at 14” SP. We select a belt driven Motors: fan at 3456 RPM and 5.15 BHP. With class A rise, an enclosed motor would be expected to have less than STEP 4. Correct the BHP for the lighter air: 5.15 ÷ 1.63 = 3.16 BHP. A 5 HP 15˚C extra rise. With Class F rise, an enclosed motor would be expected motor will suffice at 200˚F., and 7000’ but not at standard conditions. Spe - to have about a 20˚C extra rise. Therefore, Class A, B, or F insulated mo - cial motor insulation may be required above 3500 feet altitude. Consult tors could be protected to 9900 foot altitude by using next higher class of Factory. insulation (since there is a 20˚C. difference between allowable temperature of these classes of insulation). Safe Operating Speeds: Also, for high efficiency motors with 1.15 or higher service factor, der - When a fan moves air at temperatures substantially above 70˚F, the safe ating to 1.0 service factor allows the motor to be used up to 9900 feet at operating speed of the wheel and shaft could be exceeded.
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