ࡱ> po I@`\p Larry Alvarez Ba= į=x%48@"1Arial1Arial1Arial1Arial1Arial1Arial1Arial1Arial1Arial1Arial1Arial1 Arial"$"#,##0_);\("$"#,##0\)!"$"#,##0_);[Red]\("$"#,##0\)""$"#,##0.00_);\("$"#,##0.00\)'""$"#,##0.00_);[Red]\("$"#,##0.00\)7*2_("$"* #,##0_);_("$"* \(#,##0\);_("$"* "-"_);_(@_).))_(* #,##0_);_(* \(#,##0\);_(* "-"_);_(@_)?,:_("$"* #,##0.00_);_("$"* \(#,##0.00\);_("$"* "-"??_);_(@_)6+1_(* #,##0.00_);_(* \(#,##0.00\);_(* "-"??_);_(@_) 0.00000 0.000 0.00000.0 mm/dd/yymmmm\ d\,\ yyyy                + ) , *                        *8 (0  *8  *8@ (0@  (8  (8  *8@ !  ! " "  @! ! ! ! " !  " ! ! " " !  "  (x@@   @   @  *8@ @ *0@ *0@  (x@@  @   @ p@      8 ``i̜̙3f3333f3ffff333ff333f33f33BBB\` Y-Calculating Radial Loadst;First Critical Speed BK - Radial Thrust FactorNTest for VaporizationU Bearing Load6^Rotor Stiffness?c BPD to GPM&gqConvert Feet of Liquid to psig#Y|Aprox. Flow Through Orifice&To Estimate Force of ImbalancegFlow and Critical#Indicator Reverse Alignment`Rim and Face alignment[Sheet15gSheet16ZR3  @@  1Calculating Radial Loads on impellers in a volute type casing.Total suction head psig =psig&Total suction head converted to psia =psia sp. gr. =:Total suction head converted to feet of liquid, absolute =feetTotal discharge head psig =(Total discharge head converted to psia =<Total discharge head converted to feet of liquid, absolute = H = total head at Q gpm, in feetfeet **used to calculate Ns D2 = O.D. of impeller, in inches)B2 = width of impeller at O.D., in inches2Q = capacity, in gpm, at which radial thrust is to1Qn = capacity, in gpm, at best efficiency of pump$*used to calculate Nsss (S) and **NsN = rotative speed, in rpm's+hsv = net positive suction head required by*used to calculate Nsss (S) * maximum diameter impeller at best efficiency, in feet 3K = radial thrust factor at shutoff, (from sheet 3)Kq = capacity factor$where: Kq = 1 - (Q/Qn)(power n) n = !where: n = 0.7+2.6((Ns-500)/3000)Ns = specific speed of pump#where: Ns = NQ(power.5/H (power.75)2S = suction specific speed, ideal less than 12,000$where: S = NQ(power.5)/hsv(power.75)3 higher values indicate less NPSH requirements%P = Resultant radial force, in pounds.where: P = Kq x K x (H x sp gr/2.31) x D2 x B2overhung or centerhung9w = weight of mass (impeller and/or impeller and loading)poundsd = shaft diameterinchesL = shaft length 8L = length of shaft from first bearing to center of masss = distance between bearings,Y = maximum deflection, at end if (overhung)Y = WL (power3)/3EI2Y = maximum deflection, at center if (center hung)Y = WL (power3)/48EI3E = modulus of elasticity, 30,000,000 psi for steelE = 30,000,0001I = moment of inertia of the shaft, in. (power 4)I = pi*d(power4)/64/Ks = spring constant of the shaft if (overhung)Ks = 3EI/L(power3)2Ks = spring constant of the shaft if (center hung)Ks = 48EI/L(power3)M = mass divided by gravity/w = first critical speed in rpm's if (overhung)w =(square root)Ks/M(60/2pi)2w = first critical speed in rpm's if (center hung)Required NPSH in feet =%Vapor pressure of product, absolute =6Vapor pressure converted to feet of liquid, absolute =Available NPSH in feet =%Calculating radial loads on bearings R1 = Pa\s R2 = P(a+s)/sCalculating Rotor Stiffness#L = shaft length (overhung portion)!L3D4 = measure of rotor stiffness0seals are prone to leak with deflection of .0015'ANSI pumps have L3D4 ratios of 20 - 120To convert BPD to GPMBPD =Converted to GPM =Feet of head =Converted to PSI =)To Aproximate the flow through an orificeQ=AV/Q= The flow in cubic feet per second (ft3/sec.)/A= The area of the orifice in square feet (ft2):V= The velocity of the liquid in feet per second (ft/sec.)Q=AVK*h=V(2)/2g or V=su.rt 2gh or V=8.02 sq.rt.hg=32.2 ft/sec(2)h= Head across the orificeFlow =Differiential head =Area = Square InchesFeet of Liquid K factor = GPM's(water)High pressure side =Low pressure side =Differiential psig = Estimating first critical speed,"To estimate the force of imbalanceWeight of component =PoundsSpeed =Rpm'sBalance tolerance 4w/n = Ounce inches Gram inches50% for symmetrical weight =6For non symmetrical rotors the individual journal loadmust be calculated Acceptable weight of imbalance =2Weight of imbalance in grams converted to pounds = Pound inchesAcceleration of gravity =Inches per second per second!Radius of gyration of imbalance =Inches Velocity =Inches per minuteInches per secondAcceleration =Force =0Force should be less that 5% of component weightmm per second mm per secondconvert to inches per second4Balance quality grades are standardized in ISO 1940.Balance quality gradeVibration velocity in Rotor typesGGeneral examplesG 100)Crankshaft drives of large Diesel engines+Complete engines for trucks and locomotivesG 407Crankshaft drives for engines of trucks and locomotivesG 16Parts of crushing machineryParts of agricultural machineryG 6.3 Fly-wheelsFansAircraft gas turbine rotorsElectrical armaturesProcess plant machineryPump impellersG 2.5Machine-tool drivesTurbo compressorsSmall electric armaturesTurbine-driven pumpsG 1Grinding machine drivesTextile bobbinsAutomotive turbochargersG 0.4 Gyroscopes Disk-drives(Spindles for high-precision applications2The smaller the number, the smoother the operationISO Grade 2.5 at 3600 RPM'skg!centimeters per second per secondRadius of gyration = centimeterRpm's =revolutions per minutecentimeters per minutecentimeters per second kilogramsTo convert feet to psiTo convert psi to feetpsig =Converted to feet of head =To convert GPM to BPDGPM =Converted to BPD =CP-126L3D4 = Shaft length (power 3)/shaft diameter (power 4)0The lower the L3D4 the less the shaft deflection"R1 = load at bearing 1, in pounds !R2 = load at bearing 2, in poundsAt 534 GPM w = 79At 829 GPM w = 50 At 950 w = 35Test for Vaporization*Pressure experienced by the fluid particlein the pump suction, absolute =;If less than required vaporization is occurring and suctionhead should be increased.impeller = 35 lbs.L = length of shaft$M = weight / acceleration of gravity#Motor speed = 3560 + 15% = 4094 cpm#Motor speed = 3560 - 15% = 3026 cpm)At 534 GPM CPM = 3873 109% of motor speedTo keep the bolt from breaking%At 829 GPM shaft deflection is .0015"To keep the seal from leakingACP-12 flow and its affect on the first critical of the pump shaftBPD Resultant Load After Weight of Total LoadFirst Critical % of MotorRadial Loading BalancingImpeller of Pump ShaftSpeedAway 80%CPM's AcceptableBad Really BadTurbex, Inc. 281-485-8255Pump #KC-1Date =Time =Button to Button =Front foot to 1st. 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