Saddle Analysis

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PV Elite 2011 Licensee: L&T - Chiyoda Limited FileName : 7030-TK-3100-------------------------------------- Horizontal Vessel Analysis (Ope.) : Step: 9 4:00p Sep 7,2011 Saddle Analysis Learning

Transcript of Saddle Analysis

Page 1: Saddle Analysis

PV Elite 2011 Licensee: L&T - Chiyoda Limited FileName : 7030-TK-3100-------------------------------------- Horizontal Vessel Analysis (Ope.) : Step: 9 4:00p Sep 7,2011

Saddle Analysis

Learning

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Reference : 1. Deniss R Moss 2. ASME Sec.VIII Div.2 Legend : Pink & red colour block are added reference text Other text are pv-elite output
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PV Elite 2011 Licensee: L&T - Chiyoda Limited FileName : 7030-TK-3100-------------------------------------- Horizontal Vessel Analysis (Ope.) : Step: 9 4:00p Sep 7,2011 ASME Horizontal Vessel Analysis: Stresses for the Left Saddle (per ASME Sec. VIII Div. 2 based on the Zick method.) Horizontal Vessel Stress Calculations : Operating Case Note: Wear Pad Width (250.00) is less than 1.56*sqrt(rm*t) and less than 2a. The wear plate will be ignored.

Minimum Wear Plate Width to be considered in analysis [b1]: = min( b + 1.56*sqrt( Rm * t ), 2a ) = min( 220.000 + 1.56*sqrt( 1807.5001 * 9.0000 ), 2 * 1440.000 ) = 418.9688 mm.

Input and Calculated Values: Vessel Mean Radius Rm 1807.50 mm. Rm = (ID + Thk. + CA)/2 Stiffened Vessel Length per 4.15.6 L 7200.00 mm. L = Tan Line Distance from Saddle to Vessel tangent a 1440.00 mm. Saddle Width b 220.00 mm. Saddle Bearing Angle theta 150.00 degrees Inside Depth of Head h2 903.00 mm. h2 = Corroded ID /4

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PV Elite 2011 Licensee: L&T - Chiyoda Limited FileName : 7030-TK-3100-------------------------------------- Horizontal Vessel Analysis (Ope.) : Step: 9 4:00p Sep 7,2011 Shell Allowable Stress used in Calculation 1406.14 KG/CM2 Head Allowable Stress used in Calculation 1406.14 KG/CM2 Circumferential Efficiency in Plane of Saddle 1.00 Circumferential Efficiency at Mid-Span 1.00 Saddle Force Q, Operating Case 121529.89 KG From Step - 5 Horizontal Vessel Analysis Results: Actual Allowable Basis of allow. stress ------------------------------------------------------------------- Long. Stress at Top of Midspan 351.35 1406.14 KG/CM2 ( SE ) Long. Stress at Bottom of Midspan 416.61 1406.14 KG/CM2 ( SE ) Long. Stress at Top of Saddles 424.40 1406.14 KG/CM2 ( SE ) Long. Stress at Bottom of Saddles 343.56 1406.14 KG/CM2 ( SE ) Tangential Shear in Shell 122.26 1124.91 KG/CM2 (0.8S) Circ. Compressive Stress in Shell 85.33 1406.14 KG/CM2 (S) Stiffener Circ. Stress at Shell 1245.17 1757.68 KG/CM2 (1.25 SE) Stiffener Circ. Stress at Tip 1624.91 1757.68 KG/CM2 (1.25 SE) Intermediate Results: Saddle Reaction Q due to Wind or Seismic Step - 1 Saddle Reaction Force due to Wind Ft [Fwt]: = Ftr * ( Ft/Num of Saddles + Z Force Load ) * B / E = 3.00 * ( 4186.2 /2 + 0 ) * 2026.0000 / 3200.0000 = 3975.6 KG Fwt = Sum of wind load of all elements from wind load cal. Divided by 2 because it is taken by 2 saddles E is base plate length will play role in transverse load Ls length between saddle centrline will play role in long. load Ref. Deniss Moss page no.130

Step - 2 Saddle Reaction Force due to Wind Fl or Friction [Fwl]: = Max( Fl, Friction Load, Sum of X Forces) * B / Ls = Max( 3201.93 , 36822.13 , 0 ) * 2026.0000 / 4320.0000 = 17268.9 KG Fwl = calculated but not shown in detail in pv-elite calculation It is same as trasverse load only wind area is changing which is acting on single saddle See Ls length between saddle will play role in long. load

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PV Elite 2011 Licensee: L&T - Chiyoda Limited FileName : 7030-TK-3100-------------------------------------- Horizontal Vessel Analysis (Ope.) : Step: 9 4:00p Sep 7,2011

Friction load = friction factor mu * saddle load from step – 2 i.e. friction load = 0.45 * 81826 = 36821.7 Ref. Deniss Moss page no.181

Step – 3 Saddle Reaction Force due to Earthquake Fl or Friction [Fsl]: = Max( Fl, Friction Force, Sum of X Forces ) * B / Ls = Max( 41806.33 , 36822.13 , 0 ) * 2026.0000 / 4320.0000 = 19606.4 KG Fst is same as Fsl in case of earth quake because it does not depend up on direction as in case of Wind loading i.e. Fl = Ft = 41806

If we have specified any force in X or Z direction like bundle pulling force than it will come in sum of X force or Z force load Accordingly transverse & long. Load will change Ref. Deniss Moss page no.181

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PV Elite 2011 Licensee: L&T - Chiyoda Limited FileName : 7030-TK-3100-------------------------------------- Horizontal Vessel Analysis (Ope.) : Step: 9 4:00p Sep 7,2011

Step - 4 Saddle Reaction Force due to Earthquake Ft [Fst]: = Ftr * ( Ft/Num of Saddles + Z Force Load ) * B / E = 3.00 * ( 41806 /2 + 0 ) * 2026.0000 / 3200.0000 = 39702.9 KG Fst is same as Fsl in case of earth quake because it does not depends up on direction as in case of Wind loading Step - 5 Load Combination Results for Q + Wind or Seismic [Q]: = Saddle Load + Max( Fwl, Fwt, Fsl, Fst ) = 81826 + Max( 17268 , 3975 , 19606 , 39702 ) = 121529.9 KG Saddle load 81826 is calculated by finding reaction at saddle as per SFBM calculation. Step - 6 Summary of Loads at the base of this Saddle: Vertical Load (including saddle weight) 122652.01 KG Vertical load = Q + Saddle weights from weight summary / 2 = 121529.9 + (2244.2/2) Transverse Shear Load Saddle 20903.16 KG Transverse load higher of wind or seismic from step – 1 or step – 4 divide by 2 Longitudinal Shear Load Saddle 41806.33 KG Long. load higher of wind or seismic from step – 2 or step – 3 Formulas and Substitutions for Horizontal Vessel Analysis: Step -7 Note: Wear Plate is Welded to the Shell, k = 0.1 The Computed K values from Table 4.15.1: K1 = 0.1607 K2 = 0.7988 K3 = 0.4851 K4 = 0.2952 K5 = 0.6733 K6 = 0.0317 K7 = 0.0220 K8 = 0.3021 K9 = 0.2177 K10 = 0.0355 K1* = 0.2792 Please refer table 4.15.1 in ASME Sec.VIII Div 2 page no.531 Based on angles theta,alpha,bita,delta,rho various factor are calculated by pv-elite

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PV Elite 2011 Licensee: L&T - Chiyoda Limited FileName : 7030-TK-3100-------------------------------------- Horizontal Vessel Analysis (Ope.) : Step: 9 4:00p Sep 7,2011 This factors will be utilised in calculation of moments at various points Which moments will be used for calculating stress at diff. points.

Note: Dimension a is greater than or equal to Rm / 2. Here a = 0.2* L = 1440 is greater than Rm/2 = 1807.5 / 2 =903.75 Step -7 : Calculating moment M1 & M2 Moment per Equation 4.15.3 [M1]: = -Q*a [1 - (1- a/L + (R²-h2²)/(2a*L))/(1+(4h2)/3L)] = -121529*1440.00[1-(1-1440.00/7200.00+(1807.500²-903.000²)/ (2*1440.00*7200.00))/(1+(4*903.00)/(3*7200.00))] = -37324.3 KG-M Moment per Equation 4.15.4 [M2]: = Q*L/4(1+2(R²-h2²)/(L²))/(1+(4h2)/( 3L))-4a/L = 121529*7200/4(1+2(1807²-903²)/(7200²))/(1+(4*903)/ (3*7200))-4*1440/7200 = 30131.7 KG-M

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PV Elite 2011 Licensee: L&T - Chiyoda Limited FileName : 7030-TK-3100-------------------------------------- Horizontal Vessel Analysis (Ope.) : Step: 9 4:00p Sep 7,2011 Step -7 : Calculating Stress sigma 1 & sigma 2 at mid span due to moment M2 Longitudinal stress at midspan sigma 1 is in top which is compressive in nature & sigma 2 is in bottom which is tensile Longitudinal Stress at Top of Shell (4.15.6) [Sigma1]: = P * Rm/(2t) - M2/(pi*Rm²t) = 3.82 * 1807.500 /(2*9.00 ) - 30131.7 /(pi*1807.5²*9.00 ) = 351.35 KG/CM2 Compare with Allowable stress = SE = 1406.14 Here Longitudinal stress is combination of membrane stress + bending stress PR/2t = PD/4t = is longitudinal membrane stress acting on circumferntial joints PD/4t = Is circumferntial ( HOOP) membrane stress acting on long. Joint.Thk of shell is governing

due to Hoop stress M/Z = Is bending stress where Z is section modulas of cylinder with thin wall

Longitudinal Stress at Bottom of Shell (4.15.7) [Sigma2]: = P * Rm/(2t) + M2/(pi * Rm² * t) = 3.82 * 1807.500 /(2 * 9.00 ) + 30131.7 /(pi * 1807.5² * 9.00 ) = 416.61 KG/CM2 Compare with Allowable stress = SE = 1406.14 Step - 8 : Calculating Stress sigma 3 & sigma 4 at saddle support due to moment M1 Longitudinal stress at midspan sigma 3 is in top which is tensile & sigma 4 is in bottom compressive in nature The values of these stresses depend on the rigidity of the shell at the saddle support. The cylindrical shell may be considered as suitably stiffened if it incorporates stiffening rings at, or on both sides of the saddle support, or if the support is sufficiently close defined as a ≤ 0.5R , to a torispherical or elliptical head (a hemispherical head is not considered a stiffening element), a flat cover, or tubesheet. Formulas for sigma 3 & sigma 4 are different for stiffened shell & unstiffned shell(Sigma3* & sigma 4*)Pv-elite will change formula as per criteria given in Div.2 Longitudinal Stress at Top of Shell at Support (4.15.8) [Sigma3]: = P * Rm/(2t) - M1/(pi * Rm² * t) = 3.82 * 1807.500 /(2 * 9.00 ) - -37324.3 /(pi * 1807.5² * 9.00 ) = 424.40 KG/CM2 Compare with Allowable stress = SE = 1406.14 Longitudinal Stress at bottom of Shell at Support (4.15.9) [Sigma4]: = P * Rm/(2t) + M1/(pi*Rm²t) = 3.82 * 1807.500 /(2*9.00 ) + -37324.3 /(pi*1807.5²*9.00 ) = 343.56 KG/CM2

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PV Elite 2011 Licensee: L&T - Chiyoda Limited FileName : 7030-TK-3100-------------------------------------- Horizontal Vessel Analysis (Ope.) : Step: 9 4:00p Sep 7,2011 Compare with Allowable stress = SE = 1406.14

Where Sc = allowable compressive stress of shell material at design temp Sigma3* & sigma 4* = longitudinal stress at saddle support if not considered shell as stiffened Step - 9 : Calculating Shear Stress sigma due to shear force T So far we have calculated longitudinal bending stress Now its turn for shear stress There are four different cases in which shell shear stress is calculated Case – 1 Shell having single stiffner ring in plane of saddle Case – 2 Shell having two stiffner rings on both side of saddle support Case – 3 Shell without stiffening ring(s) & not stiffened by a formed head, flat cover, or

tubesheet, (a > 0.5 Rm ) Case – 4 shell without stiffening ring(s) and stiffened by a torispherical or elliptical head,

flat cover, or tubesheet, ( a <=0.5Rm ) Depends up on this different case the point at which maximum shear stress will change & formula for shear stress will also change. Fig.4.15.5 (b) for case-1 Fig.4.15.5 (c) for case-2,3,4

Points C,D,E,F indicates location of max. shear stress Pv-elite will check stress as per applicable case. Maximum Shear Force in the Saddle (4.15.5) [T]: = Q(L-2a)/(L+(4*h2/3)) = 121529 ( 7200.00 - 2 * 1440.00 )/(7200.00 + ( 4 * 903.00 /3)) = 62471.3 KG

Shear Stress in the shell with a single ring (4.15.13) [tau1]: = T / ( pi * Rm * t ) = 62471.34 / ( pi * 1807.5001 * 9.0000 ) = 122.26 KG/CM2

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PV Elite 2011 Licensee: L&T - Chiyoda Limited FileName : 7030-TK-3100-------------------------------------- Horizontal Vessel Analysis (Ope.) : Step: 9 4:00p Sep 7,2011

For case – 1 tau1 is calculated For case – 2 & 3 tau2 is calculated For case – 4 tau3 is calculated If we have placed saddle like case – 4 such that a <= 0.5Rm than additional output for Shear stress in formed head tou3* Membrane stress in torispherical,elliptical formed head Sigma 5 will come in pv-elite.

Where Sh = allowable stress of head at design temp. Step - 9 : Calculating circumferntial Stress sigma 7,8,9,10,11 Find out width of cylindrical shell contributes to the strength of saddle at the saddle location Decay Length (4.15.22) [x1,x2]: = 0.78 * sqrt( Rm * t ) = 0.78 * sqrt( 1807.500 * 9.000 ) = 99.484 mm. Here also so many case based on different possibility are given in Div.2 Case – 1 No stiffening ring

a. find Sigma 6 = maximum compressive circ. Stress at the base of saddle support b. find Sigma 7 = compressive circ. Stress + bending Stresses at horn of the saddle i.e at point G & H

Case – b1 if L = Tan to tan line length > = 8 * Rm find Sigma 7 Case – b1 if L = Tan to tan line length < 8 * Rm find Sigma 7*

c. If wear plate has been provided as per min. width required as per code clause 4.15.3.1.C Above stress can be calculated as per given formula Sigma 6r Sigma 7r Sigma 7*r where r indicates it is considering reinforcement (wear) plate

d. if provided wear plate thk. tr > 2 * t than compressive membrane plus bending stress at the ends of the reinforcing plate is calculated as shown in fig.b point G1,H1 fig. b fig.a

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PV Elite 2011 Licensee: L&T - Chiyoda Limited FileName : 7030-TK-3100-------------------------------------- Horizontal Vessel Analysis (Ope.) : Step: 9 4:00p Sep 7,2011

Case – 2 Stiffening ring in plane of saddle a.find Sigma 6* = maximum compressive circ. stress at the base of saddle support Circ. Stress in shell w/ring in Plane of Saddle (4.15.32) [sigma6*]:

= -K5 * Q * k/A = -0.673 * 121529 * 0.1 /9591.31 = -85.33 KG/CM2

Note: Single Ring in Plane of Saddle Outside the Shell. b.Claculte circumferential compressive membrane plus bending stress at Points G and H as shown in fig.a above case b -1 If internal stiffening ring is provided calculate sigma 8 = stress in shell sigma 9 = stress in ring case b - 2 If external stiffening ring is provided calculate sigma 8* = stress in shell sigma 9* = stress in ring

Circ. + Bending Stress in shell w/ring in Plane of Saddle (4.15.35) [sigma8*] = -K8 * Q/A + K6 * Q * Rm * c1/I = -0.3021*121529/9591.31+0.0317*121529*1807.50*104.94/44857792 = 1245.17 KG/CM2 Circ. + Bending Stress in ring w/ring in Plane of Saddle (4.15.36) [sigma9*]: = -K8 * Q/A - K6 * Q * Rm * c2/I = -0.3021*121529/9591.31-0.0317*121529*1807.50*80.06/44857788 = -1624.91 KG/CM2 Case – 3 cylindrical shell with stiffening rings on both sides of the saddle support

a.find Sigma 6 = maximum compressive circ. stress at the base of saddle support b.Claculte circumferential compressive membrane plus bending stress at Points I and J as shown in fig.C below case b -1 If internal stiffening ring is provided calculate sigma 10 = stress in shell sigma 11 = stress in ring case b - 2 If external stiffening ring is provided calculate sigma 10* = stress in shell sigma 11* = stress in ring Fig – C

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PV Elite 2011 Licensee: L&T - Chiyoda Limited FileName : 7030-TK-3100-------------------------------------- Horizontal Vessel Analysis (Ope.) : Step: 9 4:00p Sep 7,2011

Step – 10 Calculate thermal expansion Free Un-Restrained Thermal Expansion between the Saddles [Exp]: = Alpha * Ls * ( Design Temperature - Ambient Temperature ) = 0.126E-04 * 4320.000 * ( 170.0 - 21.1 ) = 8.076 mm. Alpha shall be used from Part II D – alpha C Linear coefficient of thermal expansiom Step-11 Check saddle in lateral loading in tension & bending

Results for Vessel Ribs, Web and Base: Baseplate Length Bplen 3200.0000 mm. Baseplate Thickness Bpthk 22.0000 mm. Baseplate Width Bpwid 250.0000 mm. Number of Ribs ( inc. outside ribs ) Nribs 4 Rib Thickness Ribtk 30.0000 mm. Web Thickness Webtk 30.0000 mm. Web Location Webloc Center Calculate MOI of saddle section as per Deniss moss reference method

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PV Elite 2011 Licensee: L&T - Chiyoda Limited FileName : 7030-TK-3100-------------------------------------- Horizontal Vessel Analysis (Ope.) : Step: 9 4:00p Sep 7,2011

Moment of Inertia of Saddle - Lateral Direction Y A AY Io Shell 4. 4039. 18173. 109039. Wearplate 17. 4000. 68000. 1241329. Web 102. 4590. 465885. 56241080. BasePlate 189. 5500. 1039500. 196686640. Totals 312. 18130. 1591558. 254278064. Value C1 = Sumof(Ay)/Sumof(A) = 88. mm. Value I = Sumof(Io) - C1*Sumof(Ay) = 114550568. mm**4 Value As = Sumof(A) - Ashell = 14091. sq.mm. Find factor K1 from following table

K1 = (1+Cos(beta)-.5*Sin(beta)² )/(pi-beta+Sin(beta)*Cos(beta)) = 0.2594

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PV Elite 2011 Licensee: L&T - Chiyoda Limited FileName : 7030-TK-3100-------------------------------------- Horizontal Vessel Analysis (Ope.) : Step: 9 4:00p Sep 7,2011 Fh = K1 * Q = 0.2594 * 121529.891 = 31521.4961 KG Where Q is taken from step - 5 Tension Stress, St = ( Fh/As ) = 223.7611 KG/CM2 Allowed Stress, Sa = 0.6 * Yield Str = 1529.5380 KG/CM2 Where As = Saddle area is calualted in MOI step calculation d = B - R*Sin(theta) / theta = 672.5430 mm. Bending Moment, M = Fh * d = 21195.4492 KG-M

Bending Stress, Sb = ( M * C1 / I ) = 1625.0912 KG/CM2 Allowed Stress, Sa = 2/3 * Yield Str = 1699.4867 KG/CM2 Bending stress = M/Z where Z = I / Y here Y is C1 calculated in MOI step Actual bending stress will be compare with allowable bending stress = 0.66 * Yield stress Step -12 calculate Base plate thk Minimum Thickness of Baseplate per Moss : = ( 3 * ( Q + Saddle_Wt ) * BasePlateWidth / ( 4 * BasePlateLength * AllStress ))½ = ( 3 * (121529 + 1122 ) * 250.00 / ( 4 * 3200.000 * 1699.487 ))½ = 20.566 mm.

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PV Elite 2011 Licensee: L&T - Chiyoda Limited FileName : 7030-TK-3100-------------------------------------- Horizontal Vessel Analysis (Ope.) : Step: 9 4:00p Sep 7,2011

Calculation of Axial Load, Intermediate Values and Compressive Stress Effective Baseplate Length [e]: = ( Bplen - Clearance ) / ( Nribs - 1) = ( 3200.0000 - 25.4 ) / ( 4 - 1 ) = 1058.2001 mm. Baseplate Pressure Area [Ap]: = e * Bpwid / 2 = 1058.2001 * 250.0000 / 2 = 0.1E+06 sq.mm. Axial Load [P]: = Ap * Bp = 132283.2 * 0.15 = 20094.2 KG Area of the Rib and Web [Ar]: = ( Bpwid - Clearance - Webtk ) * Ribtk + e/2 * Webtk = ( 250.000 - 25.4 - 30.000 ) * 30.000 + 1058.2001 /2 * 30.000 = 21712.348 sq.mm. Combined area of web & ribs will take axial load P Compressive Stress [Sc]: = P/Ar = 20094.2 / 21712.3477 = 92.5720 KG/CM2 Check of Outside Ribs: Inertia of Saddle, Outer Ribs - Longitudinal Direction Y A AY Ay² Io Rib 110.0 5769.4 634589.9 0.0 27463564.0 Web 110.0 15874.0 1746029.9 0.0 2380942.0 Values 110.0 21643.3 2380620.0 0.0 29844506.0 Bending Moment [Rm]: = Fl /( 2 * Bplen ) * e * rl / 2 = 41806.3 /( 2 * 3200.00 ) * 1058.200 * 1534.02 / 2 = 5300.864 KG-M Formula is like this

Fl * Effective base plate length * length of outer rib

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PV Elite 2011 Licensee: L&T - Chiyoda Limited FileName : 7030-TK-3100-------------------------------------- Horizontal Vessel Analysis (Ope.) : Step: 9 4:00p Sep 7,2011 (2 * Base plate length ) Bending Momennt = 2 Fl = Logidudional shear load from Step – 6

We can rewrite this equation (l/k) = Sqrt ( 2*Pi^2*E*A / W) Cc = Sqrt ( 2*Pi^2*E/Fy) Where C = 2 for one end fixed & one end hinged Fy = W/A i.e. load / area KL/R how it is calculated is not clear so far ? KL/R < Cc ( 41.3750 < 125.6488 ) per AISC E2-1 Sca = (1-(Klr)²/(2*Cc²))*Fy/(5/3+3*(Klr)/(8*Cc)-(Klr³)/(8*Cc³) Sca = ( 1-( 41.38 )²/(2 * 125.65² )) * 2549 / ( 5/3+3*(41.38 )/(8* 125.65 )-( 41.38³)/(8*125.65³) Sca = 1350.19 KG/CM2 Allowable stress is calculated from following formula of AISC manual

AISC Unity Check on Outside Ribs ( must be <= 1.0 ) Check = Sc/Sca + (Rm/Z)/Sba Check = 92.57 / 1350.19 + (5300.86 /260423.266) / 1699.49 Check = 1.27 [Failed] In unity check compression & bending loading both are combined It shall be less than 1 Inside ribs will checked same way. Check of Inside Ribs Inertia of Saddle, Inner Ribs - Axial Direction Y A AY Ay² Io

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PV Elite 2011 Licensee: L&T - Chiyoda Limited FileName : 7030-TK-3100-------------------------------------- Horizontal Vessel Analysis (Ope.) : Step: 9 4:00p Sep 7,2011 Rib 112.3 5838.4 655607.4 0.0 28324862.0 Web 112.3 31748.0 3565075.8 0.0 2380942.0 Values 112.3 37586.3 4220683.5 0.0 30705804.0 KL/R < Cc ( 8.8600 < 125.6488 ) per AISC E2-1 Sca = (1-(Klr)²/(2*Cc²))*Fy/(5/3+3*(Klr)/(8*Cc)-(Klr³)/(8*Cc³) Sca = ( 1-( 8.86 )²/(2 * 125.65² )) * 2549 / ( 5/3+3*(8.86 )/(8* 125.65 )-( 8.86³)/(8*125.65³) Sca = 1501.95 KG/CM2 AISC Unity Check on Inside Ribs ( must be <= 1.0 ) Check = Sc/Sca + (Rm/Z)/Sba Check = 106.95 / 1501.95 + ( 1750.21 /273426.562) / 1699.49 Check = 0.45 Where Rm bending moment for inside ribs is calculated in same manner like outside ribs but not shown in Details in output. Input Data for Base Plate Bolting Calculations: Total Number of Bolts per BasePlate Nbolts 8 Total Number of Bolts in Tension/Baseplate Nbt 4 Bolt Material Specification SA-193 B7 Bolt Allowable Stress Stba 693.00 KG/CM2 (shear stress of bolts) Bolt Corrosion Allowance Bca 0.0000 mm. Distance from Bolts to Edge Edgedis 40.0050 mm. Nominal Bolt Diameter Bnd 42.0000 mm. Thread Series Series TEMA Metric BasePlate Allowable Stress S 1162.45 KG/CM2 Area Available in a Single Bolt BltArea 1018.2812 sq.mm. Saddle Load QO (Weight) QO 82949.1 KG (from step – 5) Saddle Load QL (Wind/Seismic contribution) QL 19606.4 KG ( higher of wind / seismic Long. Load) Maximum Transverse Force Ft 20903.2 KG (from Step – 5) Maximum Longitudinal Force Fl 41806.3 KG (from Step – 5) Saddle Bolted to Steel Foundation No Bolt Area Calculation per Dennis R. Moss Bolt Area Requirement Due to Longitudinal Load [Bltarearl]: = 0.0 (QO > QL --> No Uplift in Longitudinal direction) Bolt Area due to Shear Load [Bltarears]: = Fl / (Stba * Nbolts) = 41806.33 / (693.00 * 8.00 ) = 754.2833 sq.mm. Bolt Area due to Transverse Load Moment on Baseplate Due to Transverse Load [Rmom]: = B * Ft + Sum of X Moments = 2026.00 * 20903.16 + 0.00 = 42341.60 KG-M Eccentricity (e): = Rmom / QO = 42341.60 / 82949.07 = 510.55 mm. < Bplen/6 --> No Uplift in Transverse direction Bolt Area due to Transverse Load [Bltareart]: = 0 (No Uplift) Required of a Single Bolt [Bltarear]

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PV Elite 2011 Licensee: L&T - Chiyoda Limited FileName : 7030-TK-3100-------------------------------------- Horizontal Vessel Analysis (Ope.) : Step: 9 4:00p Sep 7,2011 = max[Bltarearl, Bltarears, Bltareart] = max[0.0000 , 754.2833 , 0.0000 ] = 754.2833 sq.mm. Same as left saddle Pv-elite will check right saddle Than for hydrotest case will check both saddle for hydro test condition

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