16.1 HVAC Master Cheat Sheet Document Revised

Please feel free to edit this document and share your document with everyone else on the Google Drive link below. Good luck on the exam! -Justin Kauwale, PE, President of Engineering Pro Guides Link: https://drive.google.com/drive/folders/1qGrnnJh3ux9pDCXWJOtm9wpApbt1rVB3 Section 1.0 – Most Common Units This table shows a list of the popular unit conversions applicable for HVAC & Refrigeration 1 1 1 1 1 1 1 Btu/h Btu/h Btu/h EER SEER feet lb = = = = = = = 8.33 x10-5 2.93 x10-4 0.293 0.083 0.083 03048 0.4536 tons kW W kW/ton kW/ton meter kg 1 1 1 1 1 1 1 ton kW W kW/ton kW/ton meter kg = = = = = = = 12,000 3,412 3.412 12 12 3.2808 2.205 Btu/h Btu/h Btu/h EER SEER feet lb 1 1 1 1 1 1 1 1 1 1 1 1 1 1 1 ft2 gal ft3 fpm gpm cfm in. wg ft. hd psi psi psi lb/ft3 Btu Btu/h HP = = = = = = = = = = = = = = = 0.093 3.79 0.1337 5.08x10-3 0.063 0.472 249.09 2.99 6.89 x10-3 27.68 2.31 16.018 0.293 3.93x10-4 0.7457 m2 liters gal m/s l/s l/s Pa Pa MPa in. wg ft. hd kg/m3 watthour HP kW 1 1 1 1 1 1 1 1 1 1 1 1 1 1 1 m2 liters ft3 m/s l/s l/s Pa Pa MPa in. wg ft. hd kg/m3 watthour HP kW = = = = = = = = = = = = = = = 10.7639 0.227 7.481 195.85 15.85 2.119 4.01 x10-3 3.34 x10-4 145.04 0.036 0.43 0.062 3.412 2,545 1.34 ft2 gal gal fpm gpm cfm in. wg ft. hd psi psi psi lb/ft3 Btu Btu/h HP 𝑙𝑏𝑚 𝑘𝑔 = 16.02 𝑚 𝑓𝑡 𝑘𝑔 𝑙𝑏𝑚 1 = 0.0624 𝑚 𝑓𝑡 𝑙𝑏𝑚 𝑔 1 = 27.7 𝑖𝑛 𝑐𝑚 1 𝑖𝑛 = 25.4 𝑚𝑚 1 𝑖𝑛 = 2.54 𝑐𝑚 1 𝑓𝑡 = 0.3048 𝑚 1𝑓𝑡 = 0.093 𝑚 1 𝑖𝑛 = 6.452 𝑐𝑚 1𝑓𝑡 = 0.0283 𝑚 1 𝑖𝑛 = 16.39 𝑐𝑚 1 𝐵𝑇𝑈 = 1054 𝐽 1 𝑙𝑏𝑓 − 𝑓𝑡 = 1.356 𝐽 1 Density (𝜌) Length (𝑙) Area (𝐴) Volume (𝑉) Energy (𝑄) 1 𝐵𝑇𝑈 = 778 𝑙𝑏𝑓 − 𝑓𝑡 1 http://www.engproguides.com 𝑘𝑔 𝑙𝑏𝑚 = 0.0624 𝑚 𝑓𝑡 𝑔 𝑙𝑏𝑚 1 = 62.4 𝑐𝑚 𝑓𝑡 𝑔 𝑙𝑏𝑚 1 = 0.0361 𝑐𝑚 𝑖𝑛 1 𝑚𝑚 = 0.0394 𝑖𝑛 1 𝑐𝑚 = 0.394 𝑖𝑛 1 𝑚 = 3.28 𝑓𝑡 1 𝑚 = 10.76 𝑓𝑡 1 𝑐𝑚 = 0.1550 𝑖𝑛 1 𝑚 = 35.32𝑓𝑡 1 𝑐𝑚 = 0.0610 𝑖𝑛 1 𝐽 = 9.48 𝑥 10 𝐵𝑇𝑈 1 𝐽 = 0.738 𝑙𝑏𝑓 − 𝑓𝑡 𝑘𝑔 − 𝑚 1𝐽 = 1 =1𝑁−𝑚 𝑠 1 Power (𝑃, 𝑞) Temperature (𝑇) Pressure (𝑃) 1 𝐵𝑇𝑈𝐻 = 0.293 𝑊 𝐵𝑇𝑈 1 𝐵𝑇𝑈𝐻 = 1 𝐻𝑅 12,000 𝐵𝑇𝑈𝐻 = 1 𝑇𝑜𝑛 9 𝑇(℉) = (𝑇(°𝐾) − 273) + 32 5 9 𝑇(℉) = 𝑇(°𝐶) + 32 5 1 𝑖𝑛 𝑤𝑔 = 0.0360912 𝑝𝑠𝑖 2 http://www.engproguides.com 1 𝑊 = 3.414 𝐵𝑇𝑈𝐻 𝐽 1𝑊 =1 𝑆 5 𝑇(°𝐶) = (𝑇(°𝐹) − 32) 9 𝑇(°𝐾) = 𝑇(°𝐶) + 273 1 𝑝𝑠𝑖 = 27.7076 𝑖𝑛 𝑤𝑔 Section 2.0 – Basic Engineering Practice Conversion Formula Present Value to Future Value 𝐹𝑉 = 𝑃𝑉 𝑥 (1 + 𝑖) 𝑃𝑉 = Future Value to Present Value Present Value to Annual Value Annual Value to Present Value Multiply PV by (F/P, i, n) 𝐹𝑉 (1 + 𝑖) Multiply FV by (P/F, i, n) 𝑖 ∗ (1 + 𝑖) 𝐴 = 𝑃𝑉 ∗ ( ) (1 + 𝑖) − 1 Multiply PV by (A/P, i, n) 1 − (1 + 𝑖) 𝑃𝑉 = 𝐴 ∗ ( 𝑖 Multiply AV by (P/A, i, n) Future Value to Annual Value Annual Value to Future Value Factor Value ) 𝑖 𝐴 = 𝐹𝑉( ) (1 + 𝑖) − 1 Multiply FV by (A/F, i, n) (1 + 𝑖) − 1 ) 𝑖 Multiply A by (F/A, i, n) 𝐹𝑉 = 𝐴 ∗ ( Ohm’s Law 𝐼= 𝐼 = 𝑐𝑢𝑟𝑟𝑒𝑛𝑡 [𝑎𝑚𝑝𝑠] 𝑉 = 𝑣𝑜𝑙𝑡𝑎𝑔𝑒 [𝑣𝑜𝑙𝑡𝑠] 𝑅 = 𝑟𝑒𝑠𝑖𝑠𝑡𝑎𝑛𝑡𝑐𝑒 [𝑎𝑚𝑝𝑠] 𝑉 𝑅 =𝑅 +𝑅 +𝑅 +𝑅 Resistors in series 𝑅 Resistors in parallel 1 1 1 1 1 = + + + 𝑅 𝑅 𝑅 𝑅 𝑅 , 𝑃 =𝐼∗𝑉 𝑉 𝑃= 𝑅 𝑃 =𝐼 ∗𝑅 Power Equations 𝑃 Pump Water Horsepower Equations 𝑃 , , [ ,[ ∗ (𝑆𝐺) ℎ ∗𝑄 ; 3956 ∗ (𝑆𝐺) 𝑝 ∗𝑄 ; ] = 1,714 ] = 𝑆𝐺 = 1.0 𝑓𝑜𝑟 𝑤𝑎𝑡𝑒𝑟 𝑎𝑡 39 𝐹 𝑘𝑔 𝑙𝑏𝑚 = 1,000 ; 62.4 𝑝 𝑓𝑡 𝑚 3 http://www.engproguides.com 𝑄 = 𝑣𝑜𝑙𝑢𝑚𝑒𝑡𝑟𝑖𝑐 𝑓𝑙𝑜𝑤 𝑟𝑎𝑡𝑒 [𝑔𝑝𝑚] ℎ = 𝑝𝑟𝑒𝑠𝑠𝑢𝑟𝑒 [𝑓𝑒𝑒𝑡 𝑜𝑓 ℎ𝑒𝑎𝑑] 𝑃 = 𝑝𝑜𝑤𝑒𝑟 [ℎ𝑜𝑟𝑒𝑠𝑒𝑝𝑜𝑤𝑒𝑟] 𝑆𝐺 = 𝑠𝑝𝑒𝑐𝑖𝑓𝑖𝑐 𝑔𝑟𝑎𝑣𝑖𝑡𝑦 𝑝 = 𝑝𝑟𝑒𝑠𝑠𝑢𝑟𝑒 [𝑝𝑠𝑖] Fan Mechanical Horsepower Equation Pump or Fan Brake Horsepower Equation 𝑃 = ∗ 𝑇𝑃 6356 𝑄 𝑃 Motor Horsepower Equation Electrical Power Supplied to Motor , / 𝑃 𝑃 [ ; ] = [ = 𝑄 = 𝑣𝑜𝑙𝑢𝑚𝑒𝑡𝑟𝑖𝑐 𝑓𝑙𝑜𝑤 𝑟𝑎𝑡𝑒 𝑜𝑓 𝑎𝑖𝑟 [𝑐𝑢𝑏𝑖𝑐 𝑓𝑒𝑒𝑡 𝑝𝑒𝑟 𝑚𝑖𝑛𝑢𝑡𝑒] 𝑇𝑃 = 𝑡𝑜𝑡𝑎𝑙 𝑝𝑟𝑒𝑠𝑠𝑢𝑟𝑒 [𝑖𝑛𝑐ℎ𝑒𝑠 𝑤𝑎𝑡𝑒𝑟 𝑔𝑎𝑢𝑔𝑒] 𝑃 , [ ] = 𝑓𝑎𝑛 𝑚𝑒𝑐ℎ𝑎𝑛𝑖𝑐𝑎𝑙 ℎ𝑜𝑟𝑠𝑒𝑝𝑜𝑤𝑒𝑟 ] 𝑃 [ 𝜀 𝑃 / [ ]] 𝜀 [ ] = ]] 𝑃 ; ; [ ] 𝑃𝐹 Real Power Single Phase → P = IV ∗ PF Three Phase → P = √3 ∗ IV ∗ PF PF = power factor; units → kW, W, MW Apparent Power Single Phase → S = IV Three Phase → S = √3 ∗ IV PF = power factor; units → KVA, VA, MVA Apparent Power P = IV PF = power factor; units → KVA, VA, MVA 4 http://www.engproguides.com Section 3.0 – Thermodynamics Term Equation [𝑝𝑠𝑖] = 𝑃 [𝑝𝑠𝑖] + 14.7 𝑝𝑠𝑖 𝑃 Pressure Absolute temperature Temperature °𝑅 = ℉ + 460 Water 𝐵𝑜𝑖𝑙𝑡𝑠 𝑎𝑡 212 °𝐹 𝑎𝑛𝑑 1 𝑎𝑡𝑚 𝐵𝑇𝑈 0.18505 𝑙𝑏𝑚 ) ℎ = 𝑢 + 𝑝𝑣 ∗ ( 1 𝑝𝑠𝑖 ∗ 𝑓𝑡 Enthalpy Description Water has a specific heat of 1.0 Heat Capacity 𝑐 𝑝 =𝑝 ∗ Isentropic transition from Pressure State 1 to Pressure State 2 𝑐 , 𝐵𝑡𝑢 𝑙𝑏𝑚 ℉ 𝑐, 𝐵𝑡𝑢 = 0.240 𝑙𝑏𝑚 °𝑅 𝐵𝑡𝑢 = 0.171 𝑙𝑏𝑚 °𝑅 ℉ 𝜐 𝜐 𝑇 𝑇 𝜐 𝑇 =𝑇 ∗ 𝜐 K = 1.4 for air 𝑄 = 𝑚 ∗ (ℎ − ℎ ) 𝑄 = 𝑚 ∗ 𝑐 ∗ (𝑇 − 𝑇 ) 𝑝 =𝑝 ∗ 𝑃 𝑃 𝜐 𝑇 =𝑇 ∗ 𝜐 𝑇 𝑣 =𝑣 ∗ 𝑇 Transition 𝑇 =𝑇 ∗ Isobaric transition with heat gain or heat rejection Other transitions Relation between the Enthalpy of Saturated Vapor and Liquid Enthalpy of Mixed Vapor-Liquid Relationship of Entropy of Vaporization, Entropy of Saturated Vapor and Liquid Water Entropy of Wet Steam K = 1.4 for air 𝑄 = 𝑚 ∗ (ℎ − ℎ ) 𝑄 = 𝑚 ∗ 𝑐 ∗ (𝑇 − 𝑇 ) Description Adiabatic Isothermal Isochoric ℎ =ℎ +ℎ No change in energy No change in temperature No change in volume ℎ = 𝑒𝑛𝑡ℎ𝑎𝑙𝑝𝑦 𝑜𝑓 𝑠𝑎𝑡𝑢𝑟𝑎𝑡𝑒𝑑 𝑣𝑎𝑝𝑜𝑟; ℎ = 𝑒𝑛𝑡ℎ𝑎𝑙𝑝𝑦 𝑜𝑓 𝑠𝑎𝑡𝑢𝑟𝑎𝑡𝑒𝑑 𝑙𝑖𝑞𝑢𝑖𝑑 ℎ = 𝑒𝑛𝑡ℎ𝑎𝑙𝑝𝑦 𝑜𝑓 𝑣𝑎𝑝𝑜𝑟𝑖𝑧𝑎𝑡𝑖𝑜𝑛 =ℎ +𝑥∗ℎ ℎ 𝑠 =𝑠 +𝑠 𝑠 = 𝑒𝑛𝑡𝑟𝑜𝑝𝑦 𝑜𝑓 𝑠𝑎𝑡𝑢𝑟𝑎𝑡𝑒𝑑 𝑣𝑎𝑝𝑜𝑟 𝑠 = 𝑒𝑛𝑡𝑟𝑜𝑝𝑦 𝑜𝑓 𝑠𝑎𝑡𝑢𝑟𝑎𝑡𝑒𝑑 𝑙𝑖𝑞𝑢𝑖𝑑 𝑠 = 𝑒𝑛𝑡𝑟𝑜𝑝𝑦 𝑜𝑓 𝑣𝑎𝑝𝑜𝑟𝑖𝑧𝑎𝑡𝑖𝑜𝑛 𝑠 =𝑠 +𝑥∗𝑠 5 http://www.engproguides.com 𝑥 = 𝑣𝑎𝑝𝑜𝑟 𝑞𝑢𝑎𝑙𝑖𝑡𝑦 (Mixed Region) as a Function of Steam Quality 𝑠 = 𝑒𝑛𝑡𝑟𝑜𝑝𝑦 𝑜𝑓 𝑤𝑒𝑡 𝑠𝑡𝑒𝑎𝑚 (𝑚𝑖𝑥 𝑜𝑓 𝑙𝑖𝑞𝑢𝑖𝑑 & 𝑣𝑎𝑝𝑜𝑟) 𝑥 = 𝑠𝑡𝑒𝑎𝑚 𝑞𝑢𝑎𝑙𝑖𝑡𝑦, 𝑑𝑟𝑛𝑦𝑒𝑠𝑠 𝑓𝑟𝑎𝑐𝑡𝑖𝑜𝑛, % 𝑣𝑎𝑝𝑜𝑟 𝑄 =𝑚∗ℎ 𝑙𝑏𝑚 𝑚 = 𝑚𝑎𝑠𝑠 𝑓𝑙𝑜𝑤 𝑟𝑎𝑡𝑒 [ ] ℎ𝑟 𝐵𝑡𝑢 𝑄 = 𝑒𝑛𝑒𝑟𝑔𝑦 [ ] ℎ𝑟 Heat Available from Condensing Steam Throttling: Irreversible Adiabatic [Constant Enthalpy] or Isenthalpic Tank Heating/Cooling: Isometric [Constant Volume] ℎ =ℎ 𝑣 =𝑣 𝑓𝑡 𝑣 = 𝑠𝑝𝑒𝑐𝑖𝑓𝑖𝑐 𝑣𝑜𝑙𝑢𝑚𝑒 [ ] 𝑙𝑏 Turbine Expansion: Isentropic [Constant Entropy] or Reversible Adiabatic 𝑠 =𝑠 Compressor: Isentropic [Constant Entropy] or Reversible Adiabatic 𝑠 =𝑠 =𝑃 𝑃 𝑃 = 𝑝𝑟𝑒𝑠𝑠𝑢𝑟𝑒 [𝑝𝑠𝑖𝑎] Boiler Heating: Isobaric [Constant Pressure] Simplified Steam Heating Coil: Steam to Water Heat Transfer 𝑚 ∗ℎ = 500 ∗ 𝐺𝑃𝑀 ∗ ∆𝑇 Simplified Steam Heating Coil: Steam to Air Heat Transfer 𝑚 ∗ℎ = 1.08 ∗ 𝐶𝐹𝑀 ∗ ∆𝑇 6 http://www.engproguides.com 𝑊𝑜𝑟𝑘 Turbines, Pumps and Compressors Energy Balances 𝑚 𝑄 Boilers, Condensers and Evaporators Energy Balances =𝑚 , ∗ ℎ Nozzles, Diffusers Energy Balances Heat Exchangers Energy Balances Mixing Energy Balances ∗𝑐 , 𝑚 𝑚 ∗ 𝑇 ∗𝑐 , −ℎ ∗ℎ = 𝑊𝑜𝑟𝑘 =𝑚 ∗ℎ +𝑚 ∗ℎ =𝑚 =ℎ + = 𝑚 ∗𝑐 , 𝑣 ∗ℎ 𝑣 ℎ + , −𝑇 ∗ℎ + 𝑚 ∗𝑐 , ∗𝑇 =𝑚 ∗𝑐 , + 𝑚 ∗ℎ =𝑚 ∗ℎ ∗𝑇 𝑚 −ℎ +𝑚 / 𝑄 ∗ ℎ 2 , 2 ∗ 𝑇 , −𝑇 ∗𝑇 𝐴 ∗ 𝐶 𝐻 + 𝐵 ∗ (𝑂 + 3.76𝑁 ) → 𝐻𝑒𝑎𝑡 + 𝐶 ∗ 𝐶𝑂 + 𝐷 ∗ 𝐻 𝑂 𝑤ℎ𝑒𝑟𝑒 𝐴, 𝐵, 𝐶 & 𝐷 𝑎𝑟𝑒 𝑛𝑢𝑚𝑒𝑟𝑖𝑐𝑎𝑙 𝑣𝑎𝑙𝑢𝑒𝑠 𝑡ℎ𝑎𝑡 𝑑𝑒𝑠𝑐𝑟𝑖𝑏𝑒 𝑡ℎ𝑒 𝑟𝑎𝑡𝑖𝑜 𝑜𝑓 𝑒𝑎𝑐ℎ 𝑐𝑜𝑚𝑝𝑜𝑢𝑛𝑑 𝑖𝑛 𝑡ℎ𝑒 𝑒𝑞𝑢𝑎𝑡𝑖𝑜𝑛 Combustion 𝐴𝑖𝑟 = (𝑂 + 3.76𝑁 ) % 𝐸𝑥𝑐𝑒𝑠𝑠 𝐴𝑖𝑟 = 𝐴𝑐𝑡𝑢𝑎𝑙 𝐴𝑖𝑟 − 100% 𝑇ℎ𝑒𝑜𝑟𝑒𝑡𝑖𝑐𝑎𝑙 𝐴𝑖𝑟 𝐶𝑂𝑃 = 𝐶𝑂𝑃 = Coefficient of Performance (COP) 𝑊 𝑊 𝐸𝐸𝑅 3.412 (𝑏𝑜𝑡ℎ 𝑣𝑎𝑙𝑢𝑒𝑠 𝑚𝑢𝑠𝑡 𝑏𝑒 𝑠𝑎𝑚𝑒 𝑢𝑛𝑖𝑡𝑠) 𝐶𝑂𝑃 = 𝐵𝑡𝑢 ( ) ℎ𝑟 𝑄 𝑊 7 http://www.engproguides.com 𝐵𝑡𝑢 ( ) ℎ𝑟 , Evaporator Net Refrigeration Effect [𝐵𝑡𝑢ℎ] 𝑄 𝐵𝑡𝑢 𝑙𝑏 ∗ (𝑅𝑒𝑓𝑟𝑖𝑔 𝐹𝑙𝑜𝑤 𝑅𝑎𝑡𝑒) 𝑙𝑏 𝑚𝑖𝑛 = (𝐻 − 𝐻 ) ∗ (60) 𝑚𝑖𝑛 ℎ𝑟 𝐵𝑡𝑢 ;𝐻 𝑙𝑏 𝐻 = 𝑙𝑒𝑎𝑣𝑖𝑛𝑔 𝑒𝑣𝑎𝑝𝑜𝑟𝑎𝑡𝑜𝑟 𝑒𝑛𝑡ℎ𝑎𝑙𝑝𝑦 𝐵𝑡𝑢 = 𝑒𝑛𝑡𝑒𝑟𝑖𝑛𝑔 𝑒𝑣𝑎𝑝𝑜𝑟𝑎𝑡𝑜𝑟 𝑒𝑛𝑡ℎ𝑎𝑙𝑝𝑦 [ ] 𝑙𝑏 Compressor Work [𝐵𝑡𝑢ℎ] 𝑊 𝐵𝑡𝑢 𝑙𝑏 ∗ (𝑅𝑒𝑓𝑟𝑖𝑔 𝐹𝑙𝑜𝑤 𝑅𝑎𝑡𝑒) 𝑙𝑏 𝑚𝑖𝑛 = (𝐻 − 𝐻 ) ∗ (60) 𝑚𝑖𝑛 ℎ𝑟 𝐻 = 𝑙𝑒𝑎𝑣𝑖𝑛𝑔 𝑐𝑜𝑚𝑝𝑟𝑒𝑠𝑠𝑜𝑟 𝑒𝑛𝑡ℎ𝑎𝑙𝑝𝑦 Refrigeration Cycle 𝐵𝑡𝑢 ;𝐻 𝑙𝑏 𝐵𝑡𝑢 = 𝑒𝑛𝑡𝑒𝑟𝑖𝑛𝑔 𝑐𝑜𝑛𝑑𝑛𝑒𝑠𝑒𝑟 𝑒𝑛𝑡ℎ𝑎𝑙𝑝𝑦 [ ] 𝑙𝑏 Net Condenser Effect [𝐵𝑡𝑢ℎ] 𝑄 𝐵𝑡𝑢 𝑙𝑏 ∗ (𝑅𝑒𝑓𝑟𝑖𝑔 𝐹𝑙𝑜𝑤 𝑅𝑎𝑡𝑒) 𝑙𝑏 𝑚𝑖𝑛 = (𝐻 − 𝐻 ) ∗ (60) 𝑚𝑖𝑛 ℎ𝑟 𝐻 = 𝑒𝑛𝑡𝑒𝑟𝑖𝑛𝑔 𝑐𝑜𝑛𝑑𝑒𝑛𝑠𝑒𝑟 𝑒𝑛𝑡ℎ𝑎𝑙𝑝𝑦 𝐵𝑡𝑢 ;𝐻 𝑙𝑏 𝐵𝑡𝑢 = 𝑙𝑒𝑎𝑣𝑖𝑛𝑔 𝑐𝑜𝑛𝑑𝑛𝑒𝑠𝑒𝑟 𝑒𝑛𝑡ℎ𝑎𝑙𝑝𝑦 [ ] 𝑙𝑏 Net Condenser Effect [𝐵𝑡𝑢ℎ] 𝑄 = 𝑊 [𝐵𝑡𝑢ℎ] + 𝑄 [𝐵𝑡𝑢ℎ] = 𝑚 ∗ (ℎ − ℎ ) 𝑃 −𝑃 =𝑚∗ 𝑃𝑢𝑚𝑝 → 𝑊𝑜𝑟𝑘 𝜌 𝑙𝑏𝑠 𝑙𝑏𝑠 𝐵𝑡𝑢 ; 𝑚 = [ ]; 𝑊𝑜𝑟𝑘 = 𝑤ℎ𝑒𝑟𝑒 𝑃 𝑎𝑛𝑑 𝑃 = [𝑝𝑠𝑖], 𝜌 = 𝑓𝑡 ℎ𝑟 ℎ𝑟 𝐵𝑜𝑖𝑙𝑒𝑟 → 𝑄 = 𝑚 ∗ (ℎ − ℎ ) 𝑃𝑢𝑚𝑝 → 𝑊𝑜𝑟𝑘 Rankine Cycle 𝐶𝑜𝑛𝑑𝑒𝑛𝑠𝑒𝑟 → 𝑄 = 𝑚 ∗ (ℎ − ℎ ) 𝑇𝑢𝑟𝑏𝑖𝑛𝑒 → 𝑊 = 𝑚 ∗ (ℎ − ℎ ) 𝐸𝑓𝑓𝑖𝑐𝑖𝑒𝑛𝑐𝑦 = 𝑊𝑜𝑟𝑘 8 http://www.engproguides.com − 𝑊𝑜𝑟𝑘 𝑄 Section 4.0 – Psychrometrics Dry Bulb Temperature Wet Bulb Temperature Dew Point Humidity Ratio Relative Humidity Sensible Heat Latent Heat Enthalpy Dry bulb temperature indicates the amount of energy independent of the amount of water in the air. Measured with a thermometer. Units = [℉] Wet bulb temperature indicates the amount of water in the air. Measured with a sling psychrometer or hygrometer. Units = [℉] The temperature at which moist air must be cooled to, in order for water to condense out of the air. Units = [℉] Humidity ratio or specific humidity is the measure of the amount of water in air. 𝑈𝑛𝑖𝑡𝑠 = ] [ Relative Humidity indicates the amount of water in the air relative to the total amount of water the air can hold. Units = [%] Sensible heat indicates the amount of dry heat. It indicates the amount of energy either absorbed or released to change the dry bulb temperature of the air. Btu ] Units = [ lb of air Latent heat indicates the amount of energy in the air due to moisture. It is the amount of heat released when water in the air condenses out or the amount of heat absorbed by water in order to vaporize the water. Btu ] Units = [ lb of air Enthalpy is an indication of the total amount of energy in the air, both sensible and latent. Btu Units = [ ] lb of air T , =T , ∗% +T , ∗% T , ∗ CFM + T , ∗ CFM T , = CFM + CFM W Mixing of Air Streams W , h h =W , ∗% +W , ∗% W , ∗ CFM + W , ∗ CFM = CFM + CFM , , , 𝑄 =h , ∗% +h , ∗% h , ∗ CFM + h , ∗ CFM = CFM + CFM = 0.68 ∗ ∆𝑊 ∗ 𝐶𝐹𝑀 = 𝑚 ∗ 𝐻𝑉 𝑄 𝐻𝑉 = ℎ𝑒𝑎𝑡 𝑜𝑓 𝑣𝑎𝑝𝑜𝑟𝑖𝑧𝑎𝑡𝑖𝑜𝑛 𝐵𝑡𝑢 𝑎𝑡 𝑖𝑑𝑒𝑎𝑙 𝑐𝑜𝑛𝑑𝑖𝑡𝑖𝑜𝑛𝑠 𝐻𝑉 = 1,060 ℎ𝑟 Latent Heat (Air at Sea Level and Ideal Conditions) ∆𝑊 𝑔𝑟𝑎𝑖𝑛 𝑜𝑓 𝐻20 = 𝑐ℎ𝑎𝑛𝑔𝑒 𝑖𝑛 𝑠𝑝𝑒𝑐𝑖𝑓𝑖𝑐 ℎ𝑢𝑚𝑖𝑑𝑖𝑡𝑦 𝑙𝑏 𝑜𝑓 𝑑𝑟𝑦 𝑎𝑖𝑟 𝑄 = 4,734 ∗ ∆𝑊 9 http://www.engproguides.com ∗ 𝐶𝐹𝑀 𝑙𝑏 𝑜𝑓 𝐻20 = 𝑐ℎ𝑎𝑛𝑔𝑒 𝑖𝑛 𝑠𝑝𝑒𝑐𝑖𝑓𝑖𝑐 ℎ𝑢𝑚𝑖𝑑𝑖𝑡𝑦 𝑙𝑏 𝑜𝑓 𝑑𝑟𝑦 𝑎𝑖𝑟 𝑙𝑏𝑚 𝑊 𝑙𝑏𝑚 𝐻20 𝑚𝑖𝑛 , ∗ 0.075 ∗ ∗ 𝑚 = 𝐶𝐹𝑀 ∗ 60 ℎ𝑟 𝑓𝑡 𝑙𝑏𝑚 𝑑𝑟𝑦 𝑎𝑖𝑟 7000 𝑔𝑟𝑎𝑖𝑛𝑠 𝐻20 or 𝑙𝑏𝑚 𝑊 , 𝑚𝑖𝑛 ∗ 0.075 ∗ 𝑚 = 𝐶𝐹𝑀 ∗ 60 𝑓𝑡 𝑙𝑏𝑚 𝑑𝑟𝑦 𝑎𝑖𝑟 ℎ𝑟 ∆𝑊 Latent Heat 𝐵𝑡𝑢 [ ] = 𝑚𝑐 ∆𝑇 ℎ 𝑤ℎ𝑒𝑟𝑒 𝑐 = 0.240 ; 𝑄 Sensible Heat (Air at Sea Level and Ideal Conditions) . 𝑚= ( 𝑄 Sensible Heat Adjusted for Different Elevations 𝑄 ℉ )*( )*( ) . 𝐵𝑡𝑢 [ ] = 1.08 ∗ ∆𝑇 ∗ 𝐶𝐹𝑀 ℎ 𝐵𝑡𝑢 = 1.08 ∗ ∆𝑇 ∗ 𝐶𝐹𝑀 ∗ [1 − 𝑒𝑙𝑒𝑣 ∗ 6.8754𝑥10 ] . ℎ ; 𝑒𝑙𝑒𝑣 𝑖𝑛 𝑓𝑒𝑒𝑡 = 4.5 ∗ (∆h) ∗ CFM 𝐵𝑡𝑢 𝑄 = 𝑡𝑜𝑡𝑎𝑙 ℎ𝑒𝑎𝑡 [ ] ℎ𝑟 ∆h = 𝑐ℎ𝑎𝑛𝑔𝑒 𝑖𝑛 𝑒𝑛𝑡ℎ𝑎𝑙𝑝𝑦 𝑏𝑒𝑡𝑤𝑒𝑒𝑛 𝑒𝑛𝑡𝑒𝑟𝑖𝑛𝑔 𝑎𝑛𝑑 𝑙𝑒𝑎𝑣𝑖𝑛𝑔 𝐶𝐹𝑀 = 𝑣𝑜𝑙𝑢𝑚𝑒𝑡𝑟𝑖𝑐 𝑓𝑙𝑜𝑤 𝑟𝑎𝑡𝑒, 𝑐𝑢𝑏𝑖𝑐 𝑓𝑒𝑒𝑡 𝑝𝑒𝑟 𝑚𝑖𝑛𝑢𝑡𝑒 Q Total Heat Equation Total Heat Equation Relative Humidity as a Function of Humidity Ratio and Partial Pressures SHR 𝐵𝑡𝑢 = 4.5 ∗ 𝐶𝐹𝑀 ∗ (∆h) ∗ [1 − 𝑒𝑙𝑒𝑣 ∗ 6.8754𝑥10 ] . ; 𝑒𝑙𝑒𝑣 𝑖𝑛 𝑓𝑒𝑒𝑡 ℎ W p x 100% ≈ x 100% RH = p W RH = 𝑟𝑒𝑙𝑎𝑡𝑖𝑣𝑒 ℎ𝑢𝑚𝑖𝑑𝑖𝑡𝑦 p = 𝑝𝑎𝑟𝑡𝑖𝑎𝑙 𝑝𝑟𝑒𝑠𝑠𝑢𝑟𝑒 𝑜𝑓 𝑤𝑎𝑡𝑒𝑟 𝑣𝑎𝑝𝑜𝑟 𝑖𝑛 𝑡ℎ𝑒 𝑎𝑖𝑟 𝑠𝑡𝑟𝑒𝑎𝑚 p = 𝑠𝑎𝑡𝑢𝑟𝑎𝑡𝑒𝑑 𝑣𝑎𝑝𝑜𝑟 𝑝𝑟𝑒𝑠𝑠𝑢𝑟𝑒 𝑜𝑓 𝑤𝑎𝑡𝑒𝑟 𝑎𝑡 𝑡ℎ𝑒 𝑡𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒 𝑖𝑛 𝑞𝑢𝑒𝑠𝑡𝑖𝑜𝑛 W = ℎ𝑢𝑚𝑖𝑑𝑖𝑡𝑦 𝑟𝑎𝑡𝑖𝑜 𝑜𝑓 𝑡ℎ𝑒 𝑎𝑖𝑟 𝑠𝑡𝑟𝑒𝑎𝑚 W = ℎ𝑢𝑚𝑖𝑑𝑖𝑡𝑦 𝑟𝑎𝑡𝑖𝑜 𝑜𝑓 𝑡ℎ𝑒 𝑎𝑖𝑟 𝑠𝑡𝑟𝑒𝑎𝑚 𝑎𝑡 𝑠𝑎𝑡𝑢𝑟𝑎𝑡𝑖𝑜𝑛 𝑎𝑡 𝑡ℎ𝑒 𝑡𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒 𝑖𝑛 𝑞𝑢𝑒𝑠𝑡𝑖𝑜𝑛 𝑄 Btu Btu sensible heat ( ) sensible heat ( ) h h SHR = = Btu Btu total heat ( sensible heat + latent heat ( ) ) h h 10 http://www.engproguides.com Section 5.0 – Heat Transfer Term Equation Convert U-Factor to R-Value 1 𝑈= 𝑅 Addition of RValues Addition of UFactors Thermal Conductivity Units 1 = 𝐿𝑎𝑦𝑒𝑟𝑠 𝑖𝑛 𝑠𝑒𝑟𝑖𝑒𝑠 1 1 1 + + ⋯+ 𝑈 𝑈 𝑈 𝑘= 𝐿𝑎𝑦𝑒𝑟𝑠 𝑖𝑛 𝑠𝑒𝑟𝑖𝑒𝑠 𝐵𝑡𝑢 ℎ𝑟 ∗ 𝑓𝑡 ∗ ℉ Convert Thermal Conductivity to RValue and U-Factor 𝑡 𝑅= 𝑘 Heat Transfer Equation 𝑄 = 𝑈 ∗ 𝐴 ∗ ∆𝑇 Log Mean Temperature Difference (LMTD) 𝐵𝑡𝑢 ] ℎ𝑟 ∗ 𝑓𝑡 ∗ ℉ ℎ𝑟 ∗ 𝑓𝑡 ∗ ℉ 𝑅 = 𝑡ℎ𝑒𝑟𝑚𝑎𝑙 𝑟𝑒𝑠𝑖𝑠𝑡𝑎𝑛𝑐𝑒 [ ] 𝐵𝑡𝑢 𝑈 = ℎ𝑒𝑎𝑡 𝑡𝑟𝑎𝑛𝑠𝑓𝑒𝑟 𝑐𝑜𝑒𝑓𝑓𝑖𝑐𝑖𝑒𝑛𝑡 [ = 𝑅 + 𝑅 +⋯+𝑅 𝑅 𝑈 Description 𝐿𝑀𝑇𝐷 = ∆𝑇 − ∆𝑇 ∆𝑇 ln( ) ∆𝑇 𝑡 = 𝑡ℎ𝑖𝑐𝑘𝑛𝑒𝑠𝑠 𝑜𝑓 𝑚𝑎𝑡𝑒𝑟𝑖𝑎𝑙 [𝑓𝑡] 𝐵𝑡𝑢 𝑘 = 𝑡ℎ𝑒𝑟𝑚𝑎𝑙 𝑐𝑜𝑛𝑑𝑢𝑐𝑡𝑖𝑣𝑖𝑡𝑦 ℎ𝑟 ∗ 𝑓𝑡 ∗ ℉ 𝑘 𝑈= 𝑡 𝐵𝑡𝑢 ] 𝑈 = 𝑜𝑣𝑒𝑟𝑎𝑙𝑙 ℎ𝑒𝑎𝑡 𝑡𝑟𝑎𝑛𝑠𝑓𝑒𝑟 𝑐𝑜𝑒𝑓𝑓𝑖𝑐𝑖𝑒𝑛𝑡[ ℎ𝑟 ∗ 𝑓𝑡 ∗ ℉ 𝐴 = 𝑎𝑟𝑒𝑎 𝑜𝑓 ℎ𝑒𝑎𝑡 𝑡𝑟𝑎𝑛𝑠𝑓𝑒𝑟 [𝑓𝑡 ] ∆𝑇 = 𝑡𝑒𝑚𝑝. 𝑑𝑖𝑓𝑓𝑒𝑟𝑒𝑛𝑐𝑒 𝑏𝑒𝑡𝑤𝑒𝑒𝑛 ℎ𝑜𝑡 & 𝑐𝑜𝑙𝑑 𝑎𝑟𝑒𝑎𝑠 [℉] ∆𝑇 = 𝑡𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒 𝑑𝑖𝑓𝑓𝑒𝑟𝑒𝑛𝑐𝑒 𝑎𝑡 𝑒𝑛𝑡𝑟𝑎𝑛𝑐𝑒 ∆𝑇 = 𝑡𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒 𝑑𝑖𝑓𝑓𝑒𝑟𝑒𝑛𝑐𝑒 𝑎𝑡 𝑒𝑥𝑖𝑡 11 http://www.engproguides.com Counter-flow Heat Exchanger Parallel-flow Heat Exchanger 𝐵𝑡𝑢 ℎ𝑟 𝐵𝑡𝑢 𝑘 ∗ 𝐴 ∗ (𝑇 − 𝑇 ) 𝑘 = 𝑡ℎ𝑒𝑟𝑚𝑎𝑙 𝑐𝑜𝑛𝑑𝑢𝑐𝑡𝑖𝑣𝑖𝑡𝑦 𝑜𝑓 𝑚𝑎𝑡𝑒𝑟𝑖𝑎𝑙 𝑄= ℎ𝑟 ∗ 𝑓𝑡 ∗ ℉ 𝑡 𝑇 −𝑇 = 𝑡𝑒𝑚𝑝. 𝑑𝑖𝑓𝑓. 𝑏𝑒𝑡𝑤𝑒𝑒𝑛 𝑖𝑛𝑑𝑜𝑜𝑟𝑠 /𝑜𝑢𝑡𝑑𝑜𝑜𝑟𝑠 [℉] 𝑡 = 𝑡ℎ𝑖𝑐𝑘𝑛𝑒𝑠𝑠 𝑜𝑓 𝑚𝑎𝑡𝑒𝑟𝑖𝑎𝑙 [𝑓𝑡] 𝐴 = 𝑎𝑟𝑒𝑎 𝑜𝑓 ℎ𝑒𝑎𝑡 𝑡𝑟𝑎𝑛𝑠𝑓𝑒𝑟 [𝑓𝑡 ] 𝐵𝑡𝑢 ] ℎ = 𝑐𝑜𝑛𝑣𝑒𝑐𝑡𝑖𝑣𝑒 ℎ𝑒𝑎𝑡 𝑡𝑟𝑎𝑛𝑠𝑓𝑒𝑟 𝑐𝑜𝑒𝑓𝑓𝑖𝑐𝑖𝑒𝑛𝑡[ ℎ𝑟 ∗ 𝑓𝑡 ∗ ℉ 𝐴 = 𝑎𝑟𝑒𝑎 𝑜𝑓 ℎ𝑒𝑎𝑡 𝑡𝑟𝑎𝑛𝑠𝑓𝑒𝑟 [𝑓𝑡 ] 𝑄 = ℎ ∗ 𝐴 ∗ ∆𝑇 ∆𝑇 = 𝑡𝑒𝑚𝑝. 𝑑𝑖𝑓𝑓. 𝑏𝑒𝑡𝑤𝑒𝑒𝑛 ℎ𝑜𝑡 & 𝑐𝑜𝑙𝑑 𝑎𝑟𝑒𝑎𝑠 𝑜𝑓 ℎ𝑒𝑎𝑡 𝑡𝑟𝑎𝑛𝑠𝑓𝑒𝑟 [℉] 𝑄 = 𝑞𝑢𝑎𝑛𝑡𝑖𝑡𝑦 𝑜𝑓 ℎ𝑒𝑎𝑡 𝑡𝑟𝑎𝑛𝑠𝑓𝑒𝑟𝑟𝑒𝑑 Conduction Heat Transfer Equation, Through Wall Convection Heat Transfer Equation 12 http://www.engproguides.com Radiative Heat Transfer Equation Radiative Heat Transfer Between Two Objects 𝐵𝑡𝑢 = 𝑟𝑎𝑑𝑖𝑎𝑡𝑖𝑜𝑛 ℎ𝑒𝑎𝑡 𝑡𝑟𝑎𝑛𝑠𝑓𝑒𝑟 𝑐𝑜𝑒𝑓𝑓𝑖𝑐𝑖𝑒𝑛𝑡[ ] ℎ𝑟 ∗ 𝑓𝑡 ∗ ℉ 𝐴 = 𝑎𝑟𝑒𝑎 𝑜𝑓 ℎ𝑒𝑎𝑡 𝑡𝑟𝑎𝑛𝑠𝑓𝑒𝑟 [𝑓𝑡 ] ∆𝑇 = 𝑡𝑒𝑚𝑝. 𝑑𝑖𝑓𝑓. 𝑏𝑒𝑡𝑤𝑒𝑒𝑛 ℎ𝑜𝑡 & 𝑐𝑜𝑙𝑑 𝑎𝑟𝑒𝑎𝑠 𝑜𝑓 ℎ𝑒𝑎𝑡 𝑡𝑟𝑎𝑛𝑠𝑓𝑒𝑟 [℉] ℎ ∗ 𝐴 ∗ ∆𝑇 𝑄=ℎ 𝑄 = 𝜀 ∗ 𝜎 ∗ 𝐴 ∗ (𝑇 = 𝑄 ln −𝑇 𝑟 𝑟 𝑘 ) 𝑄 = 𝑟𝑎𝑑𝑖𝑎𝑡𝑖𝑜𝑛 ℎ𝑒𝑎𝑡 (𝐵𝑡𝑢ℎ); 𝐴 = 𝑎𝑟𝑒𝑎 (𝑓𝑡 ); 𝐵𝑡𝑢 𝜎 = 0.1713 𝑥 10 ; ℎ ∗ 𝑓𝑡 ∗ 𝑅 𝑇 = 𝑠𝑢𝑟𝑓𝑎𝑐𝑒 𝑡𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒 (°𝑅); 𝜀 = 𝑒𝑚𝑖𝑠𝑠𝑖𝑣𝑖𝑡𝑦 2𝜋𝐿 ∗ (𝑇 −𝑇 𝑟 ln 𝑟 1 ++ + ℎ 𝑘 𝑟 ) + 𝑟 1 ℎ 𝐵𝑡𝑢 ℎ𝑟 𝐵𝑡𝑢 𝑘 = 𝑡ℎ𝑒𝑟𝑚𝑎𝑙 𝑐𝑜𝑛𝑑𝑢𝑐𝑡𝑖𝑣𝑖𝑡𝑦 𝑜𝑓 𝑚𝑎𝑡𝑒𝑟𝑖𝑎𝑙 ℎ𝑟 ∗ 𝑓𝑡 ∗ ℉ 𝑇 = 𝑇𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒 𝑎𝑡 𝑡ℎ𝑒 𝑖𝑛𝑛𝑒𝑟 𝑝𝑖𝑝𝑒 𝑤𝑎𝑙𝑙 [℉] = 𝑇𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒 𝑎𝑡 𝑡ℎ𝑒 𝑝𝑖𝑝𝑒 𝑒𝑥𝑡𝑒𝑟𝑖𝑜𝑟 [℉] 𝑇 𝑟 = 𝑖𝑛𝑛𝑒𝑟 𝑟𝑎𝑑𝑖𝑢𝑠 𝑜𝑓 𝑝𝑖𝑝𝑒 [𝑓𝑡] = 𝑜𝑢𝑡𝑡𝑒𝑟 𝑟𝑎𝑑𝑖𝑢𝑠 𝑜𝑓 𝑝𝑖𝑝𝑒 [𝑓𝑡] 𝑟 𝐿 = 𝑝𝑖𝑝𝑒 𝑙𝑒𝑛𝑔𝑡ℎ [𝑓𝑡] 𝐵𝑡𝑢 ℎ = 𝑐𝑜𝑛𝑣𝑒𝑐𝑡𝑖𝑣𝑒 ℎ𝑒𝑎𝑡 𝑡𝑟𝑎𝑛𝑠𝑓𝑒𝑟 𝑐𝑜𝑒𝑓𝑓𝑖𝑐𝑖𝑒𝑛𝑡[ ℎ𝑟 ∗ 𝑓𝑡 ∗ ℉ 𝑄 = 𝑞𝑢𝑎𝑛𝑡𝑖𝑡𝑦 𝑜𝑓 ℎ𝑒𝑎𝑡 𝑡𝑟𝑎𝑛𝑠𝑓𝑒𝑟𝑟𝑒𝑑 Heat Transfer Equation, Through Pipe 𝑐 = 𝑠𝑝𝑒𝑐𝑖𝑓𝑖𝑐 ℎ𝑒𝑎𝑡 Prandtl Number Nusselt Number 𝑃𝑟 = 𝑁𝑢 = 𝜇∗𝑐 𝑘 𝐷∗ℎ 𝑘 𝑘 = 𝑡ℎ𝑒𝑟𝑚𝑎𝑙 𝑐𝑜𝑛𝑑𝑢𝑐𝑡𝑖𝑣𝑖𝑡𝑦 𝐵𝑡𝑢 ; 𝑙𝑏𝑚 ∗ ℉ 𝐵𝑡𝑢 ℎ ∗ 𝑓𝑡 ∗ 𝑙𝑏𝑚 ) 𝜇 = 𝑑𝑦𝑛𝑎𝑚𝑖𝑐 𝑣𝑖𝑠𝑐𝑜𝑠𝑖𝑡𝑦 ( ℎ𝑟 − 𝑓𝑡 ℉ 𝑓𝑡 𝐷 = 𝑑𝑖𝑎𝑚𝑒𝑡𝑒𝑟 𝑜𝑓 𝑝𝑖𝑝𝑒 (𝑓𝑡), 𝑘 = 𝑡ℎ𝑒𝑟𝑚𝑎𝑙 𝑐𝑜𝑛𝑑𝑢𝑐𝑡𝑖𝑣𝑖𝑡𝑦 𝑜𝑓 𝑡ℎ𝑒 𝑓𝑙𝑢𝑖𝑑 = 𝐶 Turbulent flow inside circular pipe (heating) Nusselt Number 𝑁𝑢 = 𝐷∗ℎ 𝑘 = .023 ∗ 𝑅𝑒 . ∗ 𝑃𝑟 . Turbulent flow inside circular pipe (cooling) Nusselt Number 𝑁𝑢 = 𝐷∗ℎ 𝑘 = .023 ∗ 𝑅𝑒 . ∗ 𝑃𝑟 . Laminar flow inside circular pipe (heating) Nusselt Number 𝑁𝑢 = 𝐷∗ℎ 𝑘 = 4.36 Laminar flow inside circular pipe (cooling) Nusselt Number 𝑁𝑢 = 𝐷∗ℎ 𝑘 = 3.66 13 http://www.engproguides.com ; Section 6.0 – Fluid Mechanics Term Kinematic and Dynamic Viscosity Specific Gravity Equation 𝑙𝑏 𝜇[ ] 𝑓𝑡 𝑓𝑡 ∗ 𝑠 =[ ] 𝑣= 𝑙𝑏 𝑠 𝜌[ ] 𝑓𝑡 𝜌 𝑆𝐺 = 𝜌 𝑀= Mach Number Speed of Sound Description 𝑐= 𝑤ℎ𝑒𝑟𝑒 𝜌 = 𝑑𝑒𝑛𝑠𝑖𝑡𝑦, 𝜇 = 𝑑𝑦𝑛𝑎𝑚𝑖𝑐 𝑣𝑖𝑠𝑐𝑜𝑠𝑖𝑡𝑦; 𝑣 = 𝑘𝑖𝑛𝑒𝑚𝑎𝑡𝑖𝑐 𝑣𝑖𝑠𝑐𝑜𝑠𝑖𝑡𝑦 𝑢 𝑐 𝑘∗𝑔∗𝑅∗𝑇 = 62.4 𝜌 𝑙𝑏 @ 60℉ 𝑓𝑡 𝑀 = 𝑀𝑎𝑐ℎ 𝑛𝑢𝑚𝑏𝑒𝑟 [𝑢𝑛𝑖𝑡𝑙𝑒𝑠𝑠]; 𝑢 = 𝑣𝑒𝑙𝑜𝑐𝑖𝑡𝑦 = 𝑠𝑝𝑒𝑒𝑑 𝑜𝑓 𝑠𝑜𝑢𝑛𝑑 𝑀 = 𝑀𝑎𝑐ℎ 𝑛𝑢𝑚𝑏𝑒𝑟; 𝑅 = 𝑆𝑝𝑒𝑐𝑖𝑓𝑖𝑐 𝑔𝑎𝑠 𝑐𝑜𝑛𝑠𝑡𝑎𝑛𝑡; 𝑇 = 𝑡𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒 𝑖𝑛 𝑅𝑎𝑛𝑘𝑖𝑛𝑒 𝑐 𝑘 = 𝑟𝑎𝑡𝑖𝑜 𝑜𝑓 𝑠𝑝𝑒𝑐𝑖𝑓𝑖𝑐 ℎ𝑒𝑎𝑡𝑠 = , 𝑐 𝑐 = 𝑠𝑝𝑒𝑐𝑖𝑓𝑖𝑐 ℎ𝑒𝑎𝑡 𝑜𝑓 𝑔𝑎𝑠 𝑎𝑡 𝑐𝑜𝑛𝑠𝑡𝑎𝑛𝑡 𝑝𝑟𝑒𝑠𝑠𝑢𝑟𝑒 𝑎𝑛𝑑 𝑐 = 𝑠𝑝𝑒𝑐𝑖𝑓𝑖𝑐 ℎ𝑒𝑎𝑡 𝑜𝑓 𝑔𝑎𝑠 𝑎𝑡 𝑐𝑜𝑛𝑠𝑡𝑎𝑛𝑡 𝑣𝑜𝑙𝑢𝑚𝑒 𝑓𝑡 𝑠𝑒𝑐 Air Properties Nozzles & Diffusers 𝑞 / ℎ / 𝑣 / 𝐴 Conservation of mass ∆𝑚 = 0 ∆𝑚 = 0 𝜌 ∗𝐴 ∗𝑣 =𝜌 ∗𝐴 ∗𝑣 Units 𝑓𝑡 − 𝑙𝑏 𝑠𝑙𝑢𝑔 − °𝑅 𝑘 1.4 N/A = 𝑎𝑛𝑦 ℎ𝑒𝑎𝑡 𝑒𝑛𝑡𝑒𝑟𝑖𝑛𝑔 𝑜𝑟 𝑒𝑥𝑖𝑡𝑖𝑛𝑔 𝑡ℎ𝑒 𝑠𝑦𝑠𝑡𝑒𝑚 = 𝑒𝑛𝑡ℎ𝑎𝑙𝑝𝑦 𝑎𝑡 𝑡ℎ𝑒 𝑒𝑛𝑡𝑟𝑎𝑛𝑐𝑒/𝑒𝑥𝑖𝑡 𝑜𝑓 𝑡ℎ𝑒 𝑛𝑜𝑧𝑧𝑙𝑒 = 𝑣𝑒𝑙 𝑎𝑡 𝑡ℎ𝑒 𝑒𝑛𝑡𝑟𝑎𝑛𝑐𝑒 𝑎𝑛𝑑 𝑒𝑥𝑖𝑡 𝑜𝑓 𝑡ℎ𝑒 𝑛𝑜𝑧𝑧𝑙𝑒 𝑅 1 𝑞 +ℎ + 𝑣 2 1 =𝑞 +ℎ + 𝑣 2 𝑓𝑡 ;𝑐 𝑠𝑒𝑐 1,716 = 𝑎𝑟𝑒𝑎 𝑎𝑡 𝑡ℎ𝑒 𝑒𝑛𝑡𝑟𝑎𝑛𝑐𝑒 /𝑒𝑥𝑖𝑡 𝑜𝑓 𝑡ℎ𝑒 𝑛𝑜𝑧𝑧𝑙𝑒 = 𝑣𝑒𝑙𝑜𝑐𝑖𝑡𝑦 𝑎𝑡 𝑡ℎ𝑒 𝑒𝑛𝑡𝑟𝑎𝑛𝑐𝑒 /𝑒𝑥𝑖𝑡 𝑜𝑓 𝑡ℎ𝑒 𝑛𝑜𝑧𝑧𝑙𝑒 / 𝜌 / 𝑙𝑏𝑓 ; 𝑓𝑡 𝑅 = 𝐼𝑛𝑑𝑖𝑣𝑖𝑑𝑢𝑎𝑙 𝐺𝑎𝑠 𝐶𝑜𝑛𝑠𝑡𝑎𝑛𝑡 𝑓𝑡 − 𝑙𝑏𝑓 𝑓𝑜𝑟 𝑎𝑖𝑟; = 53.35 𝑙𝑏𝑚 − 𝑅 𝑇 = 𝑡𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒 𝑖𝑛 𝑅𝑎𝑛𝑘𝑖𝑛𝑒 𝑝 = 𝑝𝑟𝑒𝑠𝑠𝑢𝑟𝑒 Ideal gas law Darcy Weisbach Equation 𝑝 =𝜌∗𝑅∗𝑇 ℎ= 𝑓𝐿𝑣 2𝐷𝑔 𝑤ℎ𝑒𝑟𝑒 ℎ = 𝑓𝑡 𝑜𝑓 ℎ𝑒𝑎𝑑; 𝑓 = 𝐷𝑎𝑟𝑐𝑦 𝑓𝑟𝑖𝑐𝑡𝑖𝑜𝑛 𝑓𝑎𝑐𝑡𝑜𝑟; 𝑣 𝑓𝑡 , = 𝑣𝑒𝑙𝑜𝑐𝑖𝑡𝑦 𝑠𝑒𝑐 𝑓𝑡 ] 𝐷 = 𝑖𝑛𝑛𝑒𝑟 𝑑𝑖𝑎𝑚𝑒𝑡𝑒𝑟 [𝑓𝑡], 𝑔 = 𝑔𝑟𝑎𝑣𝑖𝑡𝑦 [32.2 𝑠𝑒𝑐 14 http://www.engproguides.com Convert GPM to Cubic Feet Multiply GPM by ft 1 to get . 448.83 sec 𝑓𝑡 ; sec 𝑓𝑡 𝑉 = 𝑣𝑒𝑙𝑜𝑐𝑖𝑡𝑦 𝑜𝑓 𝑓𝑙𝑢𝑖𝑑 ; 𝑠𝑒𝑐 𝐷 = 𝑑𝑖𝑎𝑚𝑒𝑡𝑒𝑟 𝑜𝑓 𝑝𝑖𝑝𝑒𝑜𝑟 ℎ𝑦𝑑𝑟𝑎𝑢𝑙𝑖𝑐 𝑑𝑖𝑎𝑚𝑒𝑡𝑒𝑟 [𝑓𝑡] 𝜈 = 𝑘𝑖𝑛𝑒𝑚𝑎𝑡𝑖𝑐 𝑣𝑖𝑠𝑐𝑜𝑠𝑖𝑡𝑦 Reynolds Number 𝑉∗𝐷 𝑅𝑒𝑦𝑛𝑜𝑙𝑑𝑠 𝑛𝑢𝑚𝑏𝑒𝑟 = 𝜈 Lift 𝐹 =𝐶 ∗𝜌∗𝐴∗ 𝑣 2 𝑤ℎ𝑒𝑟𝑒 𝐶 = 𝑐𝑜𝑒𝑓𝑓𝑖𝑐𝑖𝑒𝑛𝑡 𝑜𝑓 𝑙𝑖𝑓𝑡; 𝜌 = 𝑓𝑙𝑢𝑖𝑑 𝑑𝑒𝑛𝑠𝑖𝑡𝑦; 𝐴 = 𝑎𝑟𝑒𝑎 𝑜𝑓 𝑜𝑏𝑗𝑒𝑐𝑡; 𝑣 = 𝑣𝑒𝑙𝑜𝑐𝑖𝑡𝑦 𝑜𝑓 𝑓𝑙𝑢𝑖𝑑 Drag 𝐹 =𝐶 ∗𝜌∗𝐴∗ 𝑣 2 𝑤ℎ𝑒𝑟𝑒 𝐶 = 𝑐𝑜𝑒𝑓𝑓𝑖𝑐𝑖𝑒𝑛𝑡 𝑜𝑓 𝑑𝑟𝑎𝑔; 𝜌 = 𝑓𝑙𝑢𝑖𝑑 𝑑𝑒𝑛𝑠𝑖𝑡𝑦; 𝐴 = 𝑎𝑟𝑒𝑎 𝑜𝑓 𝑜𝑏𝑗𝑒𝑐𝑡; 𝑣 = 𝑣𝑒𝑙𝑜𝑐𝑖𝑡𝑦 𝑜𝑓 𝑓𝑙𝑢𝑖𝑑 ∗ [𝑔] 𝐵 = 𝑏𝑢𝑜𝑦𝑎𝑛𝑐𝑦 𝑓𝑜𝑟𝑐𝑒; (𝑙𝑏𝑓 𝑜𝑟 𝑁) 𝑘𝑔 𝑙𝑏𝑚 = 𝑓𝑙𝑢𝑖𝑑 𝑑𝑒𝑛𝑠𝑖𝑡𝑦; ( 𝑜𝑟 ) 𝜌 𝑚 𝑓𝑡 = 𝑣𝑜𝑙𝑢𝑚𝑒 𝑜𝑓 𝑑𝑖𝑠𝑝𝑙𝑎𝑐𝑒𝑑 𝑓𝑙𝑢𝑖𝑑 𝑚 𝑓𝑜𝑟 𝑆𝐼 𝑔 = 9.81 𝑠 Buoyancy 𝐵= 𝜌 𝑝 = Fluid Power Bulk Modulus Viscosity ∗𝑉 𝛽= 𝑉 𝐹 𝐴 𝑙𝑏𝑠 ; 𝐹 = 𝑓𝑜𝑟𝑐𝑒 (𝑙𝑏𝑠); 𝑖𝑛 𝐴 = 𝜋𝑟 = 𝑎𝑟𝑒𝑎 (𝑖𝑛 ) 𝑝 = 𝑝𝑟𝑒𝑠𝑠𝑢𝑟𝑒 ∆𝑃 ; 𝑝𝑠𝑖 ∆𝑉/𝑉 𝐶𝑒𝑛𝑡𝑖𝑠𝑡𝑜𝑘𝑒𝑠 = 1.0764 𝑥 10 𝑓𝑡 𝑠 𝑙𝑏 𝑓𝑡 − 𝑠 𝑝𝑣 𝑝𝑔𝑧 𝑝𝑣 𝑝𝑔𝑧 + +ℎ =𝑃 + + 𝑃 + 2𝑔 𝑔 2𝑔 𝑔 𝑔 = 32.2 ; 𝑔 = 32.2 𝑓𝑡 𝑣 = ; 𝑧 = 𝑓𝑡; 𝑃 = 𝑙𝑏/𝑓𝑡 ; ℎ = 𝑙𝑏𝑚/𝑓𝑡 𝑠 𝑃𝑜𝑖𝑠𝑒 = 0.067197 Bernouli’s 15 http://www.engproguides.com Section 7.0 – Energy/Mass Balance Term Equation 𝑊 Dehumidification/ Humidification 𝑚 =𝑚 Mixing General Equations 𝑀 , ∗ (𝑊 − 𝑊 ) 𝑀 Mixing Air based on Temperature Mixing Air based on Enthalpy Mixing Air based on Humidity Ratio Latent Heat of Vaporization Description +𝑀 , +𝑀 𝑀 , , +𝑀 T T , , , = 𝑀 , 𝑙𝑏 𝑜𝑓 𝐻20 = 𝑠𝑝𝑒𝑐𝑖𝑓𝑖𝑐 ℎ𝑢𝑚𝑖𝑑𝑖𝑡𝑦 𝑙𝑏 𝑜𝑓 𝑑𝑟𝑦 𝑎𝑖𝑟 𝑚 = 𝑚𝑎𝑠𝑠 𝑓𝑙𝑜𝑤 𝑟𝑎𝑡𝑒 𝑜𝑓 𝑎𝑖𝑟; = 𝑚𝑎𝑠𝑠 𝑓𝑙𝑜𝑤 𝑟𝑎𝑡𝑒 𝑜𝑓 𝑤𝑎𝑡𝑒𝑟 𝑚 = 𝑀 , +𝑀 , , = 𝑀 , =T , ∗% +T , ∗% T , ∗ CFM + T , ∗ CFM = CFM + CFM =h , ∗% +h , ∗% h , ∗ CFM + h , ∗ CFM h , = CFM + CFM W , =W , ∗% +W , ∗% W , ∗ CFM + W , ∗ CFM W , = CFM + CFM h , 970 Btu/lbm 16 http://www.engproguides.com Section 8.0 – Heating/Cooling Loads Term Equation Convert U-Factor to R-Value 𝑈= Addition of R-Values Addition of U-Factors Thermal Conductivity Units Convert Thermal Conductivity to RValue and U-Factor Heat Transfer Equation 1 𝑅 1 = 𝐵𝑡𝑢 ] ℎ𝑟 ∗ 𝑓𝑡 ∗ ℉ ℎ𝑟 ∗ 𝑓𝑡 ∗ ℉ 𝑅 = 𝑡ℎ𝑒𝑟𝑚𝑎𝑙 𝑟𝑒𝑠𝑖𝑠𝑡𝑎𝑛𝑐𝑒 [ ] 𝐵𝑡𝑢 𝑈 = ℎ𝑒𝑎𝑡 𝑡𝑟𝑎𝑛𝑠𝑓𝑒𝑟 𝑐𝑜𝑒𝑓𝑓𝑖𝑐𝑖𝑒𝑛𝑡 [ = 𝑅 + 𝑅 + 𝑅 …+ 𝑅 𝑅 𝑈 Description 1 1 1 1 + + …+ 𝑈 𝑈 𝑈 𝑈 𝑘= 𝐵𝑡𝑢 ℎ𝑟 ∗ 𝑓𝑡 ∗ ℉ 𝑡 𝑘 𝑘 𝑈= 𝑡 𝑅= 𝑄 = 𝑈 ∗ 𝐴 ∗ ∆𝑇 𝑡 = 𝑡ℎ𝑖𝑐𝑘𝑛𝑒𝑠𝑠 𝑜𝑓 𝑚𝑎𝑡𝑒𝑟𝑖𝑎𝑙 [𝑓𝑡] 𝐵𝑡𝑢 𝑘 = 𝑡ℎ𝑒𝑟𝑚𝑎𝑙 𝑐𝑜𝑛𝑑𝑢𝑐𝑡𝑖𝑣𝑖𝑡𝑦 [ ℎ𝑟 ∗ 𝑓𝑡 ∗ ℉ 𝐵𝑡𝑢 ] 𝑈 = 𝑜𝑣𝑒𝑟𝑎𝑙𝑙 ℎ𝑒𝑎𝑡 𝑡𝑟𝑎𝑛𝑠𝑓𝑒𝑟 𝑐𝑜𝑒𝑓𝑓𝑖𝑐𝑖𝑒𝑛𝑡[ ℎ𝑟 ∗ 𝑓𝑡 ∗ ℉ 𝐴 = 𝑎𝑟𝑒𝑎 𝑜𝑓 ℎ𝑒𝑎𝑡 𝑡𝑟𝑎𝑛𝑠𝑓𝑒𝑟 [𝑓𝑡 ] ∆𝑇 = 𝑡𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒 𝑑𝑖𝑓𝑓𝑒𝑟𝑒𝑛𝑐𝑒 𝑏𝑒𝑡𝑤𝑒𝑒𝑛 ℎ𝑜𝑡 𝑎𝑛𝑑 𝑐𝑜𝑙𝑑 𝑎𝑟𝑒𝑎𝑠 𝑜𝑓 ℎ𝑒𝑎𝑡 𝑡𝑟𝑎𝑛𝑠𝑓𝑒𝑟 [℉] Roof/Wall 𝐶𝑜𝑛𝑑𝑢𝑐𝑡𝑖𝑣𝑒 𝐿𝑜𝑎𝑑𝑠 → 𝑄 = 𝑈 ∗ 𝐴 ∗ 𝐶𝐿𝑇𝐷 Skylight/Window 𝐶𝑜𝑛𝑑𝑢𝑐𝑡𝑖𝑣𝑒 𝐿𝑜𝑎𝑑𝑠 → 𝑄 = 𝑈 ∗ 𝐴 ∗ 𝐶𝐿𝑇𝐷 Or 𝐶𝑜𝑛𝑑𝑢𝑐𝑡𝑖𝑣𝑒 𝐿𝑜𝑎𝑑𝑠 → 𝑄 = 𝑈 ∗ 𝐴 ∗ ∆𝑇 𝑅𝑎𝑑𝑖𝑎𝑡𝑖𝑣𝑒 𝐿𝑜𝑎𝑑𝑠 → 𝑄 = 𝐴 ∗ 𝑆𝐶 ∗ 𝑆𝐶𝐿 𝑆𝐶 = 𝑠ℎ𝑎𝑑𝑖𝑛𝑔 𝑐𝑜𝑒𝑓𝑓𝑖𝑐𝑖𝑒𝑛𝑡 𝑆𝐶𝐿 = 𝑠𝑜𝑙𝑎𝑟 𝑐𝑜𝑜𝑙𝑖𝑛𝑔 𝑙𝑜𝑎𝑑 𝑓𝑎𝑐𝑡𝑜𝑟 People Sensible loads 𝑄 = 𝑁 ∗ 𝑆𝐻𝐺 ∗ 𝐶𝐿𝐹 𝑁 = 𝑛𝑢𝑚𝑏𝑒𝑟 𝑜𝑓 𝑝𝑒𝑜𝑝𝑙𝑒 𝑆𝐻𝐺 = 𝑠𝑒𝑛𝑠𝑖𝑏𝑙𝑒 ℎ𝑒𝑎𝑡 𝑔𝑎𝑖𝑛, 𝑎𝑐𝑡𝑖𝑣𝑖𝑡𝑦 𝑑𝑒𝑝𝑒𝑛𝑑𝑒𝑛𝑡 𝐶𝐿𝐹 = 𝑐𝑜𝑜𝑙𝑖𝑛𝑔 𝑙𝑜𝑎𝑑 𝑓𝑎𝑐𝑡𝑜𝑟 𝑄 = 𝑁 ∗ 𝐿𝐻𝐺 ∗ 𝐶𝐿𝐹 𝑁 = 𝑛𝑢𝑚𝑏𝑒𝑟 𝑜𝑓 𝑝𝑒𝑜𝑝𝑙𝑒 People Latent loads 𝐿𝑎𝑡𝑒𝑛𝑡 = 𝑙𝑎𝑡𝑒𝑛𝑡 ℎ𝑒𝑎𝑡 𝑔𝑎𝑖𝑛, 𝑎𝑐𝑡𝑖𝑣𝑖𝑡𝑦 𝑑𝑒𝑝𝑒𝑛𝑑𝑒𝑛𝑡 𝐶𝐿𝐹 = 𝑐𝑜𝑜𝑙𝑖𝑛𝑔 𝑙𝑜𝑎𝑑 𝑓𝑎𝑐𝑡𝑜𝑟 17 http://www.engproguides.com 𝐵𝑡𝑢 ℎ𝑟 𝐵𝑡𝑢 ℎ𝑟 𝐵𝑡𝑢 ℎ𝑟 ∗ 𝑈𝐹 ∗ 𝑆𝐴𝐹 ∗ 𝑆𝐹 𝑄 = 𝑁 ∗ 𝑊𝑎𝑡𝑡𝑠 ∗ 𝑤𝑎𝑡𝑡𝑠 𝑤ℎ𝑒𝑟 𝑁 = 𝑛𝑢𝑚𝑏𝑒𝑟 𝑜𝑓 𝑙𝑖𝑔ℎ𝑡 𝑡𝑦𝑝𝑒. 𝑈𝐹 = 𝑢𝑠𝑎𝑔𝑒 𝑓𝑎𝑐𝑡𝑜𝑟 𝑆𝐴𝐹 = 𝑠𝑝𝑒𝑐𝑖𝑎𝑙 𝑎𝑙𝑙𝑜𝑤𝑎𝑛𝑐𝑒 𝑓𝑎𝑐𝑡𝑜𝑟 𝑆𝐹 = 𝑠𝑝𝑎𝑐𝑒 𝑓𝑟𝑎𝑐𝑡𝑖𝑜𝑛 3.412 Lighting 𝑃 (𝐻𝑃) 𝐵𝑡𝑢ℎ ∗ 𝐻𝑃 𝐸𝑓𝑓𝑖𝑐𝑖𝑒𝑛𝑐𝑦 𝑀𝑜𝑡𝑜𝑟 𝐻𝑒𝑎𝑡 𝐿𝑜𝑠𝑠 = 𝑇𝑜𝑡𝑎𝑙 𝐻𝑒𝑎𝑡 ∗ (1 − 𝐸𝑓𝑓𝑖𝑐𝑖𝑒𝑛𝑐𝑦) 𝐸𝑞𝑢𝑖𝑝𝑚𝑒𝑛𝑡 𝐻𝑒𝑎𝑡 𝐿𝑜𝑠𝑠 = 𝑇𝑜𝑡𝑎𝑙 𝐻𝑒𝑎𝑡 ∗ (𝐸𝑓𝑓𝑖𝑐𝑖𝑒𝑛𝑐𝑦) 𝑇𝑜𝑡𝑎𝑙 𝐻𝑒𝑎𝑡 = 𝑄 = 2545 = 𝑇𝑜𝑡𝑎𝑙 𝐻𝑒𝑎𝑡 ∗ (1 − 𝜀 )∗𝐹 ∗𝐹 = 𝑇𝑜𝑡𝑎𝑙 𝐻𝑒𝑎𝑡 ∗ (𝜀 )∗𝐹 ∗𝐹 𝑃 = ℎ𝑜𝑟𝑒𝑠𝑝𝑜𝑤𝑒𝑟 𝑜𝑓 𝑚𝑜𝑡𝑜𝑟 = 𝑒𝑓𝑓𝑖𝑐𝑖𝑒𝑛𝑐𝑦 𝑜𝑓 𝑚𝑜𝑡𝑜𝑟 𝜀 𝐹 = 𝑢𝑠𝑎𝑔𝑒 𝑓𝑎𝑐𝑡𝑜𝑟 𝑜𝑓 𝑡ℎ𝑒 𝑚𝑜𝑡𝑜𝑟 𝐹 = 𝑙𝑜𝑎𝑑 𝑓𝑎𝑐𝑡𝑜𝑟 𝑜𝑓 𝑡ℎ𝑒 𝑚𝑜𝑡𝑜𝑟 𝑄 𝑄 Miscellaneous Equipment ∗𝐹 ∗𝐹 𝐵𝑡𝑢 = 𝑖𝑛𝑝𝑢𝑡 𝑡𝑜 𝑡ℎ𝑒 𝑒𝑞𝑢𝑖𝑝𝑚𝑒𝑛𝑡 𝑞 ℎ 𝐹 = 𝑓𝑟𝑎𝑐𝑡𝑖𝑜𝑛 𝑜𝑓 𝑡ℎ𝑒 𝑡𝑜𝑡𝑎𝑙 ℎ𝑒𝑎𝑡 𝑡ℎ𝑎𝑡 𝑖𝑠 𝑟𝑎𝑑𝑖𝑎𝑡𝑒𝑑 𝑡𝑜 𝑡ℎ𝑒 𝑠𝑝𝑎𝑐𝑒 𝐹 = 𝑢𝑠𝑎𝑔𝑒 𝑓𝑎𝑐𝑡𝑜𝑟 𝑄=𝑞 𝐵𝑡𝑢 = 4.5 ∗ 𝐶𝐹𝑀 ∗ ∆ℎ [ ] 𝑙𝑏 = 1.08 ∗ 𝐶𝐹𝑀 ∗ (𝑇 −𝑇 = 4,840 ∗ 𝐶𝐹𝑀 ∗ (𝑊 −𝑊 𝑊 = ℎ𝑢𝑚𝑖𝑑𝑖𝑡𝑦 𝑟𝑎𝑡𝑖𝑜 [𝑙𝑏𝑚 /𝑙𝑏𝑚 𝑄 Infiltration 𝑄 𝑄 18 http://www.engproguides.com ) ) ] Section 9.0 – Equipment & Components Term Simplified Sensible Heat Equation Affinity laws (For when given a system curve and diameter change is less than 5%) Contact Factor Equation for Coils Equation 𝑄 Description 𝐵𝑡𝑢 = 1.08 ∗ 𝐶𝐹𝑀 ∗ ∆𝑇[℉] ℎ 𝐷 𝑄 = ; 𝑖𝑓 𝑠𝑝𝑒𝑒𝑑 𝑖𝑠 ℎ𝑒𝑙𝑑 𝑐𝑜𝑛𝑠𝑡𝑎𝑛𝑡, 𝑄 𝐷 𝑤ℎ𝑒𝑟𝑒 𝑄 = 𝑓𝑙𝑜𝑤 𝑎𝑛𝑑 𝐷 = 𝑑𝑖𝑎𝑚𝑒𝑡𝑒𝑟 𝑁 𝑄 = ; 𝑖𝑓 𝑑𝑖𝑎𝑚𝑒𝑡𝑒𝑟 𝑖𝑠 ℎ𝑒𝑙𝑑 𝑐𝑜𝑛𝑠𝑡𝑎𝑛𝑡 𝑄 𝑁 𝐷 𝐻 = ; 𝑖𝑓 𝑠𝑝𝑒𝑒𝑑 𝑖𝑠 ℎ𝑒𝑙𝑑 𝑐𝑜𝑛𝑠𝑡𝑎𝑛𝑡, 𝐻 𝐷 𝑤ℎ𝑒𝑟𝑒 𝐻 = 𝑝𝑟𝑒𝑠𝑠𝑢𝑟𝑒, 𝐷 = 𝑑𝑖𝑎𝑚𝑒𝑡𝑒𝑟 𝐻 𝑁 = ; 𝑖𝑓 𝑑𝑖𝑎𝑚𝑒𝑡𝑒𝑟 𝑖𝑠 ℎ𝑒𝑙𝑑 𝑐𝑜𝑛𝑠𝑡𝑎𝑛𝑡 𝐻 𝑁 𝐷 𝑃 = ; 𝑖𝑓 𝑠𝑝𝑒𝑒𝑑 𝑖𝑠 ℎ𝑒𝑙𝑑 𝑐𝑜𝑛𝑠𝑡𝑎𝑛𝑡 𝑃 𝐷 𝑤ℎ𝑒𝑟𝑒 𝑃 = 𝑝𝑜𝑤𝑒𝑟 𝑎𝑛𝑑 𝐷 = 𝑑𝑖𝑎𝑚𝑒𝑡𝑒𝑟 𝑃 𝑁 = ; 𝑖𝑓 𝑑𝑖𝑎𝑚𝑒𝑡𝑒𝑟 𝑖𝑠 ℎ𝑒𝑙𝑑 𝑐𝑜𝑛𝑠𝑡𝑎𝑛𝑡 𝑃 𝑁 −ℎ ℎ 𝐶𝑜𝑛𝑡𝑎𝑐𝑡 𝐹𝑎𝑐𝑡𝑜𝑟 = ℎ −ℎ Contact Factor Equation for Coils 𝐶𝑜𝑛𝑡𝑎𝑐𝑡 𝐹𝑎𝑐𝑡𝑜𝑟 = Contact Factor Equation for Coils 𝐶𝑜𝑛𝑡𝑎𝑐𝑡 𝐹𝑎𝑐𝑡𝑜𝑟 = Bypass Factor ∗ 𝑎𝑖𝑟 𝑐𝑜𝑛𝑑𝑖𝑡𝑖𝑜𝑛𝑠 𝑎𝑡 70℉ 𝑎𝑛𝑑 1 𝑎𝑡𝑚. −𝑇 𝑇 𝑇 where h is equal to the enthalpy where T is equal to the dry bulb temperature −𝑇 𝑊 𝑊 −𝑊 −𝑊 𝐵𝑦𝑝𝑎𝑠𝑠 𝐹𝑎𝑐𝑡𝑜𝑟 = 1 − 𝐶𝑜𝑛𝑡𝑎𝑐𝑡 𝐹𝑎𝑐𝑡𝑜𝑟 𝐻 = 60 ∗ 𝜌 ∗ 𝑄 ∗ (𝑊 −𝑊 ) 𝑊 = 𝑡ℎ𝑒 ℎ𝑢𝑚𝑖𝑑𝑖𝑡𝑦 𝑟𝑎𝑡𝑖𝑜 𝑒𝑛𝑡𝑒𝑟𝑖𝑛𝑔 𝑜𝑟 𝑙𝑒𝑎𝑣𝑖𝑛𝑔 𝑡ℎ𝑒 𝑠𝑦𝑠𝑡𝑒𝑚 Moisture Transfer Equation 𝑙𝑏 𝜌 = 𝑑𝑒𝑛𝑠𝑖𝑡𝑦 𝑜𝑓 𝑎𝑖𝑟 [ ] 𝑓𝑡 𝑓𝑡 𝑄 = 𝑎𝑖𝑟 𝑓𝑙𝑜𝑤 𝑟𝑎𝑡𝑒 [ ] 𝑚𝑖𝑛 𝑙𝑏 𝐻 = 𝑚𝑜𝑖𝑠𝑡𝑢𝑟𝑒 𝑡𝑟𝑎𝑛𝑠𝑓𝑒𝑟𝑟𝑒𝑑 [ ] ℎ𝑟 𝑅𝑎𝑛𝑔𝑒 = 𝑇 Cooling Tower 𝐴𝑝𝑝𝑟𝑜𝑎𝑐ℎ = 𝑇 [℉] − 𝑇 , , 𝐸𝑓𝑓𝑒𝑐𝑡𝑖𝑣𝑒𝑛𝑒𝑠𝑠 = [℉] − 𝑇 [℉] , , [℉] 𝑅𝑎𝑛𝑔𝑒 𝑅𝑎𝑛𝑔𝑒 + 𝐴𝑝𝑝𝑟𝑜𝑎𝑐ℎ 19 http://www.engproguides.com [𝑙𝑏 𝑜𝑓 𝑤𝑎𝑡𝑒𝑟] [𝑙𝑏 𝑜𝑓 𝑑𝑟𝑦 𝑎𝑖𝑟] 𝑄[𝐵𝑡𝑢ℎ] = 500 ∗ 𝑓𝑙𝑜𝑤 𝑟𝑎𝑡𝑒 𝑔𝑎𝑙 ∗ 𝑇 𝑚𝑖𝑛 𝑔𝑎𝑙 = 𝑒𝑣𝑎𝑝𝑜𝑟𝑎𝑡𝑖𝑜𝑛 𝑟𝑎𝑡𝑒 𝑚𝑖𝑛 . 000943 ∗ 𝑐𝑜𝑜𝑙𝑖𝑛𝑔 𝑡𝑜𝑤𝑒𝑟 𝑓𝑙𝑜𝑤 𝑟𝑎𝑡𝑒 Cooling Tower Evaporation Rate Fans 𝑔𝑎𝑙 ∗ (𝑇 𝑚𝑖𝑛 , −𝑇 , 𝑀𝑜𝑡𝑜𝑟 𝐻𝑃 = 𝐵𝐻𝑃 ∗ 𝑙𝑏𝑚 𝑝∗𝑣 = 2∗𝑔 𝑓𝑡 𝑓𝑡 − 𝑙𝑏𝑚 𝑔 = 32.2 𝑙𝑏𝑓 − 𝑠 𝑓𝑡 𝑣 = ; 𝑧 = 𝑓𝑡; 𝑉𝑃 = 𝑙𝑏/𝑓𝑡 𝑠 𝑉𝑃 = Shortcut Equation 𝐹𝑃𝑀 [𝑖𝑛. 𝑤𝑔] 𝐹𝑎𝑛 𝑣𝑒𝑙𝑜𝑐𝑖𝑡𝑦 𝑝𝑟𝑒𝑠𝑠𝑢𝑟𝑒 = 4005 𝑤ℎ𝑒𝑟𝑒 𝐹𝑃𝑀 = 𝑣𝑒𝑙𝑜𝑐𝑖𝑡𝑦 𝑓𝑒𝑒𝑡 𝑝𝑒𝑟 𝑚𝑖𝑛𝑢𝑡𝑒 𝑄 𝑄 𝐻 𝐻 𝑃 𝑃 𝑄 𝑄 𝑁 𝑁 𝑃 𝑃 𝑁 𝑁 𝐻 𝐻 𝑃 𝑃 Affinity Laws for all other cases (fans and pumps) N = speed, Q = flow rate, H = head or pressure, p = density, D = diameter, P = power ACFM vs. SCFM 𝑃 𝑇 −𝑇 ) , 1 ) 𝐵𝑟𝑎𝑘𝑒 ℎ𝑜𝑟𝑠𝑒𝑝𝑜𝑤𝑒𝑟 = 𝑀𝐻𝑃 ∗ ( 𝑓𝑎𝑛 𝑒𝑓𝑓𝑖𝑐𝑖𝑒𝑛𝑐𝑦 𝐹𝑎𝑛 𝑚𝑒𝑐ℎ𝑎𝑛𝑖𝑐𝑎𝑙 ℎ𝑜𝑟𝑠𝑒𝑝𝑜𝑤𝑒𝑟 𝐶𝐹𝑀 ∗ 𝑇𝑆𝑃[𝑖𝑛. 𝑤𝑔] = 6,356 Fans , 𝑁 ( ) 𝑁 𝑁 𝑝 𝐷 = ( ) 𝐷 𝑁 𝑝 𝑁 𝑝 𝐷 = ( ) 𝐷 𝑁 𝑝 𝐻 . 𝑝 . 𝐷 = 𝐷 𝐻 𝑝 𝐷 𝐻 . 𝑝 . = ( ) 𝐷 𝐻 𝑝 𝐷 𝐻 . 𝑝 . = 𝐷 𝐻 𝑝 𝑄 𝐷 = ( ) 𝐷 𝑄 𝑄 𝑝 𝐷 = ( ) 𝐷 𝑄 𝑝 𝑄 𝑝 𝐷 = ( ) 𝐷 𝑄 𝑝 𝑃 519 𝑆𝐶𝐹𝑀 = 𝐴𝐶𝐹𝑀 ∗ ∗( ) 𝑇 14.7 = 𝑎𝑐𝑡𝑢𝑎𝑙 𝑝𝑟𝑒𝑠𝑠𝑢𝑟𝑒 𝑖𝑛 𝑎𝑏𝑠𝑜𝑙𝑢𝑡𝑒 𝑡𝑒𝑟𝑚𝑠 (𝑝𝑠𝑖𝑎); = 𝑎𝑐𝑡𝑢𝑎𝑙 𝑡𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒 𝑖𝑛 𝑅𝑎𝑛𝑘𝑖𝑛𝑒 (°𝑅) = 𝐷 𝐷 20 http://www.engproguides.com 1 𝑚𝑜𝑡𝑜𝑟 𝑒𝑓𝑓𝑖𝑐𝑖𝑒𝑛𝑐𝑦 𝑅 𝑡 10 → 𝑡ℎ𝑖𝑛 𝑤𝑎𝑙𝑙𝑒𝑑 𝑝𝑟𝑒𝑠𝑠𝑢𝑟𝑒 𝑣𝑒𝑠𝑠𝑒𝑙 𝑎𝑠𝑠𝑢𝑚𝑝𝑡𝑖𝑜𝑛 𝑃𝑅 𝑓𝑜𝑟 𝑐𝑦𝑙𝑖𝑛𝑑𝑟𝑖𝑐𝑎𝑙 𝑡ℎ𝑖𝑛 𝑤𝑎𝑙𝑙𝑒𝑑 𝑝𝑟𝑒𝑠𝑠𝑢𝑟𝑒 𝑣𝑒𝑠𝑠𝑒𝑙𝑠 → 𝜎 = 𝑡 𝑃𝑅 𝑓𝑜𝑟 𝑠𝑝ℎ𝑒𝑟𝑖𝑐𝑎𝑙 𝑡ℎ𝑖𝑛 𝑤𝑎𝑙𝑙𝑒𝑑 𝑝𝑟𝑒𝑠𝑠𝑢𝑟𝑒 𝑣𝑒𝑠𝑠𝑒𝑙𝑠 → 𝜎 = 2𝑇 𝜎 = 𝑠𝑡𝑟𝑒𝑠𝑠 (𝑝𝑠𝑖); 𝑃 = 𝑝𝑟𝑒𝑠𝑠𝑢𝑟𝑒 (𝑝𝑠𝑖); 𝑅 = 𝑟𝑎𝑑𝑖𝑢𝑠 (𝑖𝑛) 𝑡 = 𝑡ℎ𝑖𝑐𝑘𝑛𝑒𝑠𝑠 (𝑖𝑛) Pressure vessel 𝐺𝑎𝑠 𝑝𝑟𝑒𝑠𝑠𝑢𝑟𝑒 𝑟𝑒𝑙𝑖𝑒𝑓 𝑣𝑎𝑙𝑣𝑒 𝑠𝑖𝑧𝑖𝑛𝑔 𝑊 ∗ √𝑇𝑍 → 𝐴= 𝐶 ∗ 𝐾 ∗ 𝑃 ∗ 𝐾 ∗ √𝑀 Pressure relief ∆𝑃 𝑆𝐺 𝑄=𝐶 Control valve liquid 𝑄 = 59.64 ∗ 𝐶 Control valve gas ∆𝑃 ∗𝑃 520 𝑆𝐺 ∗ 𝑇 𝑃 520 𝑄 =𝐶 ∗𝑃 ∗ 𝑆𝐺 ∗ 𝑇 Control valve critical point 𝑄 Boiler fuel energy = 𝑚 ∗ 𝐻𝐻𝑉 𝐴 = 𝑣𝑎𝑙𝑣𝑒 𝑒𝑓𝑓𝑒𝑐𝑡𝑖𝑣𝑒 𝑜𝑟𝑖𝑓𝑖𝑐𝑒 𝑎𝑟𝑒𝑎 (𝑖𝑛 ); 𝐶 = 𝑐𝑜𝑒𝑓𝑓𝑖𝑐𝑖𝑒𝑛𝑡 𝑜𝑓 𝑔𝑎𝑠 (315 𝑓𝑜𝑟 𝑎𝑖𝑟); 𝐾 = 𝑐𝑜𝑒𝑓𝑓𝑖𝑐𝑖𝑒𝑛𝑡 𝑜𝑓 𝑑𝑖𝑠𝑐ℎ𝑎𝑟𝑔𝑒 (𝑡𝑦𝑝𝑖𝑐𝑎𝑙𝑙𝑦 0.975); 𝐾 = 𝑐𝑜𝑟𝑟𝑒𝑐𝑡𝑖𝑜𝑛 𝑓𝑎𝑐𝑡𝑜𝑟 𝑓𝑜𝑟 𝑏𝑎𝑐𝑘 𝑝𝑟𝑒𝑠𝑠𝑢𝑟𝑒 𝑀 = 𝑚𝑜𝑙𝑒𝑐𝑢𝑙𝑎𝑟 𝑤𝑒𝑖𝑔ℎ𝑡 𝑜𝑓 𝑔𝑎𝑠 (𝑠𝑒𝑒 𝑝𝑒𝑟𝑖𝑜𝑑𝑖𝑐 𝑡𝑎𝑏𝑙𝑒); 𝑃 = 𝑟𝑒𝑙𝑖𝑒𝑣𝑖𝑛𝑔 𝑝𝑟𝑒𝑠𝑠𝑢𝑟𝑒 (𝑝𝑠𝑖𝑎); 𝑇 = 𝑎𝑏𝑠𝑜𝑙𝑢𝑡𝑒 𝑡𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒 (°𝑅); 𝑙𝑏𝑠 ; 𝑊 = 𝑟𝑒𝑙𝑖𝑒𝑣𝑖𝑛𝑔 𝑐𝑎𝑝𝑎𝑐𝑖𝑡𝑦 ℎ𝑟 𝑍 = 𝑐𝑜𝑚𝑝𝑟𝑒𝑠𝑠𝑖𝑏𝑖𝑙𝑖𝑡𝑦 𝑓𝑎𝑐𝑡𝑜𝑟 𝑄 = 𝑣𝑜𝑙𝑢𝑚𝑒𝑡𝑟𝑖𝑐 𝑓𝑙𝑜𝑤 𝑟𝑎𝑡𝑒 (𝑔𝑝𝑚); 𝐶 = 𝑣𝑎𝑙𝑣𝑒 𝑐𝑜𝑒𝑓𝑓𝑖𝑐𝑖𝑒𝑛𝑐𝑡; ∆𝑃 = 𝑝𝑟𝑒𝑠𝑠𝑢𝑟𝑒 𝑑𝑟𝑜𝑝 (𝑝𝑠𝑖) 𝑆𝐺 = 𝑠𝑝𝑒𝑐𝑖𝑓𝑖𝑐 𝑔𝑟𝑎𝑣𝑖𝑡𝑦 𝑜𝑓 𝑓𝑙𝑢𝑖𝑑 𝑄 = 𝑣𝑜𝑙𝑢𝑚𝑒𝑡𝑟𝑖𝑐 𝑓𝑙𝑜𝑤 𝑟𝑎𝑡𝑒 (𝑠𝑐𝑓ℎ − 𝑠𝑡𝑎𝑛𝑑𝑎𝑟𝑑 𝑐𝑢𝑏𝑖𝑐 𝑓𝑒𝑒𝑡 𝑝𝑒𝑟 ℎ𝑜𝑢𝑟); 𝐶 = 𝑣𝑎𝑙𝑣𝑒 𝑐𝑜𝑒𝑓𝑓𝑖𝑐𝑖𝑒𝑛𝑐𝑡; ∆𝑃 = 𝑝𝑟𝑒𝑠𝑠𝑢𝑟𝑒 𝑑𝑟𝑜𝑝 (𝑝𝑠𝑖); 𝑇 = 𝑎𝑏𝑠𝑜𝑙𝑢𝑡𝑒 𝑡𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒 (°𝑅) 𝑆𝐺 = 𝑠𝑝𝑒𝑐𝑖𝑓𝑖𝑐 𝑔𝑟𝑎𝑣𝑖𝑡𝑦 𝑜𝑓 𝑔𝑎𝑠 (𝑎𝑖𝑟 = 1.0); 𝑃 = 𝑜𝑝𝑒𝑟𝑎𝑡𝑖𝑛𝑔 𝑝𝑟𝑒𝑠𝑠𝑢𝑟𝑒 (𝑝𝑠𝑖) 𝑤ℎ𝑒𝑟𝑒 𝐶 = 𝑔𝑎𝑠 𝑣𝑎𝑙𝑣𝑒 𝑐𝑜𝑒𝑓𝑓𝑖𝑐𝑖𝑒𝑛𝑡 𝐵𝑡𝑢 𝐻𝐻𝑉 = ℎ𝑖𝑔ℎ𝑒𝑟 ℎ𝑒𝑎𝑡𝑖𝑛𝑔 𝑣𝑎𝑙𝑢𝑒 𝑜𝑓 𝑓𝑢𝑒𝑙 [ ] 𝑙𝑏 𝑙𝑏 𝑚 = 𝑚𝑎𝑠𝑠 𝑓𝑙𝑜𝑤 𝑟𝑎𝑡𝑒 𝑜𝑓 𝑓𝑢𝑒𝑙 ℎ𝑟 𝜀 Boiler efficiency Boiler energy for water temperature increase = (𝑚 ) ∗ (ℎ 𝑚 −ℎ ∗ 𝐻𝐻𝑉 , ∗ ∆𝑇 = 𝑚 ∗ 𝑐 ∗ ∆𝑇 = 𝑙𝑏𝑠/ℎ𝑟 𝐵𝑡𝑢 𝑐 = ℎ𝑒𝑎𝑡 𝑐𝑎𝑝𝑎𝑐𝑖𝑡𝑦 𝑜𝑓 𝑤𝑎𝑡𝑒𝑟 = 1.00 𝑙𝑏𝑚 ∗ ℉ ∆𝑇 = 𝑐ℎ𝑎𝑛𝑔𝑒 𝑖𝑛 𝑡𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒 𝑜𝑓 𝑎𝑖𝑟 [℉] 𝑄 = 500 ∗ 𝐺𝑃𝑀 𝑚 21 http://www.engproguides.com ∗ℎ 𝑄=𝑚 𝐵𝑡𝑢 𝑙𝑏𝑚 = 𝑚𝑎𝑠𝑠 𝑓𝑙𝑜𝑤 𝑟𝑎𝑡𝑒 𝑖𝑛 𝑙𝑏𝑠/ℎ𝑟 𝑚 1 𝑓𝑡 62.4 𝑙𝑏 60 𝑚𝑖𝑛𝑢𝑡𝑒 𝑔𝑎𝑙𝑙𝑜𝑛 𝑜𝑓 𝑤𝑎𝑡𝑒𝑟 ∗ ∗ ∗ 1 7.48 𝑔𝑎𝑙𝑙𝑜𝑛 𝑓𝑡 ℎ𝑜𝑢𝑟 𝑚𝑖𝑛𝑢𝑡𝑒 ℎ Boiler energy for vaporization of water = ℎ𝑒𝑎𝑡 𝑜𝑓 𝑣𝑎𝑝𝑜𝑟𝑖𝑧𝑎𝑡𝑖𝑜𝑛 𝑜𝑓 𝑤𝑎𝑡𝑒𝑟 𝑄 = 500 ∗ 𝐺𝑃𝑀 ∗ℎ =𝑚 Desuperheating Region ∗𝑐 , ∗ (𝑇 1𝑠𝑡 𝑆𝑡𝑒𝑝: 𝑄 = 𝑚 Feedwater heater ∗ℎ −𝑇 Condensing Region ∗ℎ 2𝑛𝑑 𝑆𝑡𝑒𝑝: 𝑄 = 𝑚 Subcooling Region ∗𝑐 , ∗ 𝑇 3𝑟𝑑 𝑆𝑡𝑒𝑝: 𝑄 = 𝑚 −𝑇 22 http://www.engproguides.com ) Section 10.0 – Systems & Components Term Rectangular Duct Oval Duct Equation 𝐷 = 1.30 ∗ (𝑎 ∗ 𝑏) . (𝑎 + 𝑏) . Description 𝑤ℎ𝑒𝑟𝑒 a and b are the width[ft] and height[ft] of the duct (𝐴 ∗ 𝐴𝑟𝑒𝑎) . (𝑃𝑒𝑟𝑖𝑚𝑒𝑡𝑒𝑟) . 𝑃𝑒𝑟𝑖𝑚𝑒𝑡𝑒𝑟 = 𝜋 ∗ 𝑎 + 2 ∗ (𝐴 − 𝑎) 𝐷 = 1.55 ∗ 𝑤ℎ𝑒𝑟𝑒 A is the major axis and a is the minor axis Velocity Pressure as a Function of Air Velocity 𝑉𝑃 = Friction loss due to length of duct 𝐹 𝑖𝑛. 𝑤𝑔 [𝑖𝑛. 𝑤𝑔] = 𝐿[𝑓𝑡] ∗ 𝑓[ ] 100 𝑓𝑡 Friction loss due to duct fitting 𝐹 [𝑖𝑛. 𝑤𝑔] = 𝐶 ∗ 𝑉𝑃 Compressed air piping loss 0.1025𝐿𝑞 𝑟𝑑 . Where, 𝑓 = 𝑝𝑟𝑒𝑠𝑠𝑢𝑟𝑒 𝑑𝑟𝑜𝑝 (𝑝𝑠𝑖) 𝐿 = 𝑝𝑖𝑝𝑒 𝑙𝑒𝑛𝑔𝑡ℎ (𝑓𝑡) 𝑞 = 𝑎𝑖𝑟𝑓𝑙𝑜𝑤 (𝑐𝑓𝑚) 𝑑𝑖𝑠𝑐ℎ𝑎𝑟𝑔𝑒 𝑝𝑟𝑒𝑠𝑠𝑢𝑟𝑒 @ 𝑝𝑖𝑝𝑒 𝑒𝑛𝑡𝑟𝑎𝑛𝑐𝑒 𝑟 = 𝑟𝑎𝑡𝑖𝑜 𝑜𝑓𝑐𝑜𝑚𝑝𝑟𝑒𝑠𝑠𝑖𝑜𝑛 𝑓𝑟𝑒𝑒 𝑎𝑖𝑟 𝑝𝑟𝑒𝑠𝑠𝑢𝑟𝑒 𝑑 = 𝑖𝑛𝑡𝑒𝑟𝑛𝑎𝑙 𝑝𝑖𝑝𝑒 𝑑𝑖𝑎𝑚𝑡𝑒𝑟 (𝑖𝑛) 𝐹𝑃𝑀 4005 𝐹𝑃𝑀 = 𝑎𝑖𝑟 𝑣𝑒𝑙𝑜𝑐𝑖𝑡𝑦 𝑖𝑛 𝑓𝑒𝑒𝑡 𝑝𝑒𝑟 𝑚𝑖𝑛𝑢𝑡𝑒 𝑉𝑃 = 𝑣𝑒𝑙𝑜𝑐𝑖𝑡𝑦 𝑝𝑟𝑒𝑠𝑠𝑢𝑟𝑒 [𝑖𝑛. 𝑤𝑔] [𝑖𝑛. 𝑤𝑔] 𝑓= Darcy Weisbach Pressure h= fLv 2Dg 1 psi is equal to 2.31 feet of head (water) NPSH = Suction Head NPSHA = (P Net positive suction head 𝑁𝑃𝑆𝐻𝐴 = 𝑃 𝑁𝑃𝑆𝐻𝐴 = 𝑃 Velocity pressure (Pumps) h = ft of head; f = Darcy friction factor; ft , v = velocity sec D = inner diameter [ft], ft g = gravity [32.2 ] sec 𝑉 [𝑓𝑡 𝑜𝑓 ℎ𝑒𝑎𝑑]; 2𝑔 P − Vapor Pressure − P ) − VP 𝑃 −𝑃 or +𝑃 −𝑃 −𝑃 𝑣𝑒𝑙𝑜𝑐𝑖𝑡𝑦 𝑖𝑛 23 http://www.engproguides.com 𝑓𝑡 𝑓𝑡 ; 𝑔𝑟𝑎𝑣𝑖𝑡𝑦 = 32.2 𝑠𝑒𝑐 sec 𝑞 𝑞 , 𝑞 𝑞 Air to air energy recovery devices 𝑞 𝑞 = 4.5 ∗ 𝐶𝐹𝑀 = 4.5 ∗ 𝐶𝐹𝑀 , , , , , ∗ (ℎ ∗ (ℎ −ℎ −ℎ ) ) = 1.08 ∗ 𝐶𝐹𝑀 = 1.08 ∗ 𝐶𝐹𝑀 ∗ (𝑇 ∗ (𝑇 −𝑇 −𝑇 ) ) = 4,770 ∗ 𝐶𝐹𝑀 = 4,770 ∗ 𝐶𝐹𝑀 ∗ (𝑊 ∗ (𝑊 −𝑊 −𝑊 ) ) 𝜀 𝑞 𝑞 𝑞 = 𝑞 𝑞 = 𝑞 , = 𝜀 𝜀 , , , , , 24 http://www.engproguides.com Section 11.0 – Supportive Knowledge Term Fresh air flow based on ASHRAE 62.1 Equation 𝐹𝑟𝑒𝑠ℎ 𝑎𝑖𝑟 𝑓𝑙𝑜𝑤 𝑟𝑎𝑡𝑒 = 𝑅 ∗ (# 𝑜𝑓 𝑝𝑒𝑜𝑝𝑙𝑒) + 𝑅 ∗ (𝐴𝑟𝑒𝑎) Refrigeration Room Ventilation Rate Vibration Control: Natural Frequency of Spring Vibration Control: Transmissibility and Vibration Isolation Efficiency Combining the Sound Levels of Multiple Sources Description 𝑄[𝐶𝐹𝑀] = 100𝑋𝐺 . , where G = lbs of refrigerant. 𝑓 (𝐻𝑧) = 3.13 ∗ 𝑇= 1 𝑠𝑡𝑎𝑡𝑖𝑐 𝑑𝑒𝑓𝑙𝑒𝑐𝑡𝑖𝑜𝑛 (𝑖𝑛𝑐ℎ𝑒𝑠) 𝑇𝑟𝑎𝑛𝑠𝑚𝑖𝑠𝑠𝑖𝑏𝑖𝑙𝑖𝑡𝑦% = 100% − 𝑉𝑖𝑏𝑟𝑎𝑡𝑖𝑜𝑛 𝐼𝑠𝑜𝑙𝑎𝑡𝑖𝑜𝑛 𝐸𝑓𝑓𝑖𝑐𝑖𝑒𝑛𝑐𝑦% 1 𝑓 𝑓 −1 𝐿 = 10 ∗ log (10 Sound Level at a Distance from a Point Source (Spherical Propagation) + 10 + 10 + 10 + 10 +. . ) − 20 ∗ log 𝑥 − 1 𝐿 =𝐿 𝐿 = 𝑆𝑜𝑢𝑛𝑑 𝑙𝑒𝑣𝑒𝑙 𝑎𝑡 𝑎 𝑑𝑖𝑠𝑡𝑎𝑛𝑐𝑒 𝑜𝑓 𝑥 [𝐷𝐵] = 𝑆𝑜𝑢𝑛𝑑 𝑙𝑒𝑣𝑒𝑙 𝑜𝑓 𝑒𝑞𝑢𝑖𝑝𝑚𝑒𝑛𝑡 [𝐷𝐵] 𝐿 𝑥 = 𝑑𝑖𝑠𝑡𝑎𝑛𝑐𝑒 𝑓𝑟𝑜𝑚 𝑒𝑞𝑢𝑖𝑝𝑚𝑒𝑛𝑡 [𝑓𝑡 ] Sound Level at a Distance from a Point Source (Half-Spherical Propagation) 𝐿 =𝐿 − 20 ∗ log 𝑥+2 Sound Level at a Distance from a Point Source (Quarter-Spherical Propagation) 𝐿 =𝐿 − 20 ∗ log 𝑥+5 Sound Level at a Distance from a Point Source (Eighth-Spherical Propagation) 𝐿 =𝐿 − 20 ∗ log 𝑥+8 25 http://www.engproguides.com

16.1 HVAC Master Cheat Sheet Document Revised

Add this document to collection(s)

Add this document to saved

Suggest us how to improve StudyLib