Saddle Calculation

Saddle v1-8 per "Pressure Vessel Design Manual" by Dennis R. Moss Customer: Murphy / McDermott Desc: Horizontal Treater MBK 1070

H

Project: 5A379-A03 by: oab

H

L

B Fixed Saddle

A OD ts P Pe L H A B HType th V I Exp Z I Sc Tinst Tmin Tmax u fc S Fys Fy Emod Fbolt Fvbolt Av JE W

Sliding Saddle

Ls

Vessel Information Outside Diameter of Vessel Corroded Thickness of Shell Internal Design Pressure External Design Pressure Tangent to Tangent Length of Vessel Depth of Head Distance from Head Tangent to Saddle Center Line Height from vessel centerline to bottom of saddle Head Type Corroded Thickness of Head Wind Design (ASCE 7-98) Design Wind Speed Importance Factor Exposure Seismic Design (UBC 1997) UBC 1997 Seismic Zone Importance Factor Soil Coefficient (SA, SB, SC, SD, or SE) Temperature Installation Temperature of Vessel Minimum Temperature of Vessel Maximum Temperture of Vessel Coefficient of Friction between Saddle and Concrete Allowable bearing pressure on concrete Material Properties Allowable Stress: Vessel Shell Yield Stress of Shell at Design Temperature Yield Stress of Saddle Modulus of Elasticity of Saddle Allowable Tensile Stress on Bolts Allowable Shear Stress on Bolts Coefficient of Thermal Expansion of Vessel Joint Efficiency Weight Total Weight (If zero, program will estimate)

www.mecaconsulting.com

A 108.7500 in 0.7500 in 50.00 psig 0.00 psig 304.00 in 27 in 27.00 in 78.00 in Elliptical 0.25 in 150 mph 1 C 1 1 SC 70.00 Deg. F 70.00 Deg. F 170.00 Deg. F 1 750 psi 20,000 psi 38,000 psi 38,000 psi 2.900E+07 psi 20,000 psi 15,000 psi 7.00E-06 in/in/F 1.00 250,000 lbs

02/13/2015



wp wb

tw Theta

Lh

B

d1

d1

tb Lrib

E

F

Saddle Information (Note Click "Std Dims" button to get a standard saddle) Width of Saddle perpendicular to Longitudinal Axis Theta = 164.45 Width of Saddle at Bottom (along Longitudinal Vessel Axis) Width of Saddle at Top of Saddle (along longitudinal Vessel axis) Distance from Outside of Baseplate to First Rib Thickness of Base Plate Width of wear plate Wear Plt ext. above Horn Thickness of Wear Plate

E F wb d1 tb wp Lh tw

Nr Ribs Spaced Evenly

Toward Fixed Saddle J

Yc Ye

d2

d2 Lb tweb J Nr Nb Dbolt Ww

Saddle Information Distance from Outside of Baseplate to First Rib Center to Center bolt spacing in transverse direction Thickness of Web Thickness of Ribs Number of Ribs Number of Anchor Bolts per Saddle Nominal Diameter of Bolt Fillet Leg Size (Web to Baseplate)


d1

tw

F Sliding Saddle Bolt shown in cold as-installed Position

108.750 in 12.000 in 12.000 in 0.500 in 1.000 in 20.000 in 5.500 in 0.500 in

Lb

0.500 in 80.000 in 0.75 in 0.75 in 6 2 1.250 in 0.750 in

02/13/2015


Ar Yr dr Ir Rm Rs Ls Theta ThetaW Wtot De zg Alpha Kz Cf Gq qz Afl Flw Aft Ftw Ca V Fls Fts Ye Yc Flt Fl Ft Qo Q1 Q2 Q


Shell and Stiffening Ring Combinded Properties Area of Stiffening Ring Distance to centroid of Stiffening Ring Distance from Centroid to Outer Fiber Moment of Inertia of Stiffening Ring Calculated Parameters Mean Radius of Shell Radius of Shell Saddle Spacing: L-2*A Saddle Angle: 2*Atan((E-2*d1)/OD) Angle of Wear Plate Calculate Weights User Entered Total Weight Wind Loading: (Based upon ASCE 7-98) Effective Diameter based upon Table 3-24 Constant from table 6-4 Constant from table 6-4 2.01*((B+OD/2)/zg)^(2/Alpha) Shape Factor Gust Factor (Rigid Structure) Wind Pressure: 0.00256*Kz*V^2*I PI()*(De/12)^2/4 Af*Cf*Gq*qz De*(L+2*H)/144 (Aft*Cf*Gq*qz)*0.5 Seismic Loading: (Based upon UBC) Seismic Coefficient based upon Soil and Zone 2.5*Ca*I*W / R V / 1.4 V / (2 * 1.4) Thermal Expansion Maximum Expansion of Vessel Maximum Contraction of Vessel Frictional Force due to Expansion/Contraction (u*Wtot/2) Saddle Reactions Maximum Longitudinal Force: Max(Flw, Fls, Flt, Flp) Maximum Transverse Force: Max(Ftw, Fts) Operating Load on Saddles: (Wtot)/2 Reaction due to Long Force: Wo/2+Fl*B/Ls Reaction due to Tran Force: Wo/2+3*Ft*B/E Maximum of Q1 or Q2


6.000 51.700

in^2 in in in^4

54.000 in 54.375 in 250.000 in 164.4 Deg 176.0 Deg 250,000 lbs 128.3250 in 900.0000 9.5000 1.3426 0.8 0.85 77.33 psf 90 ft^2 4,723 lbs 319 ft^2 8,388 lbs 0.0900 19,397 lbs 13,855 lbs 6,927 lbs 0.175 in - in 125,000 lbs 125,000 8,388 125,000 164,000 143,050 164,000

lbs lbs lbs lbs lbs lbs

02/13/2015


A./Rs K1 K2 K3 K4 M1 M2 S3 S4 S5 Check # 1 Check # 2 Check # 3 tes tes1 tes2 S12 S13 S14 fx fp fs Element Shell Wear Plt Web Baseplt c1 c2 Is As Beta K1 fh ft d M fb

"K" Constants from Figure 3-46 K5 K6 K7 K8 K9 Longitudinal Bending 6*Q*(8*A*H+6*A^2-3*Rm^2+3*H^2)/(3*L+4*H) 3*Q*((3*L^2+6*Rm^2-6*H^2-12*A*L-16*A*H)/(3*L+4*H)) Long. Bending @ Saddle w/ Stiffeners: +/- M1/(PI()*Rs^2*ts) Long. Bending @ Midspan: +/- M2/(pi()*Rm^2*ts) Tangential Shear Tang. Shear - Shell Stiffened: (Q/(PI()*Rs*ts))*((L-2*A)/(L+4*H/3)) Circumferential Bending Lh >= Rm/10: 5.50 >= Is A <= 0.5*Rm: 27.00 >= Wp >= wb+1.56*(Rm*ts)^0.5 20.00 <= Both Check # 1 & # 2 Passed: ts+tw Check # 3 did not both pass: ts Both Check # 1 & # 2 Passed: ts^2+tw^2 Circ Compression: -KK5*Q/(tes1*(wb+1.56*(Rm*tes1)^0.5)) Circ in shell w/ stiffener: -KK8*Q/Ar-KK9*Q*Rs*Yr/Ir Circ in stiffener: -KK8*Q/Ar-KK9*Q*Rs*dr/Ir Pressure Stresses Longitudinal Pressure Stress P*Rm/(2*ts) Circumferential Pressure Stress P*Rm/ts Stress in Stiffener P*(1.56*(Rs*ts)^0.5)*Rm/Ar Saddle Design - Web b h Area I d in in in^2 in^4 in 31.924 0.750 23.9 1.12.E+00 0.38 21.962 0.500 11.0 2.29.E-01 1.00 0.750 49.313 37.0 7.49.E+03 25.91 12.000 1.000 12.0 1.00.E+00 51.06 Area = 83.9 A*Y = Dist from Id of Shell to Center of Gravity for Saddle (A*Y/Area) Dist from Center of Gravity to Base Plate Moment of Inertia of Saddle Area of Saddle Pi() - Theta/2 (1+COS(Beta)-0.5*(SIN(Beta))^2)/(PI()-Beta+(SIN(Beta))*(COS(Beta))) Saddle Splitting Force: K1*Q Tensile Stress in Saddle: fh/As B-Rs*Sin(Theta)/Theta fh * d Bending Stress in Saddle: M*C1/I = = = = =


0.4966 0.6021 0.6796 0.3616 0.2547


= = = = =

0.6461 1.0175 0.2811 0.0240 1.207E+08 in-lbs 7.244E+06 in-lbs 17,330 psi 1,054 psi 941 psi 5.40 27.00 21.93

1.00 1.00 0.00 1.2500 in 0.7500 in 0.8125 in -6,443 psi -7,684 psi -7,684 psi 1,800 psi 3,600 psi 4,483 psi

A*d in^3 8.979E+00 1.098E+01 9.581E+02 6.128E+02 1.591E+03

A*d^2 Itot in^4 in^4 3.367E+00 4.489E+00 1.098E+01 1.121E+01 2.482E+04 3.232E+04 3.129E+04 3.129E+04 I = 6.362E+04 18.96 in 4.67 in 6.362E+04 in^4 83.9 in^2 1.707 rads 0.2874 47,126 lbs 562 psi 72.92 in 3.436E+06 in-lbs 1,024 psi

02/13/2015



Saddle Design - Baseplate with Offset Web Lw Lr Lt fu l1 l2 w M fb

Tension? Pb Abolt fal fv M e E/6

E-2*d1-2*J Nr*(F-2*d2-tw) Lw + Lr Q/L D2 + tw + Ww + tb F - l1 Fu / (L1 + 0.5 * L2) w * l2^2 / 6 6 * M / tb^2 Saddle Design - Anchor Bolts Longitudinal Load Is Qo > Q1? 125,000 < 164,000 Since Q0>Q1 then Tensile Load will exist Each Bolt: ((Q1-Q0)/(Nb)) (Pi()/4) * Dbolt^2 Bolt Tensile Stress: Pb/Abolt Shear Load (Assume Fixed Saddle takes entire load) Shear Stress: Fl / Abolt Transverse Load Transverse Moment: Ft * B M / Q0 E/6 Since e < E / 6 --> There is No Uplift


106.250 in 63.000 in 169.250 in 11,628 lb/ft 2.750 in 9.250 in 131 psi 1,874 in-lbs 11,242 psi

0.000 19,500 lbs 1.23 in^2 15,890 psi 50,930 psi 654,296 in-lbs 5.234 in 18.125 in

02/13/2015


Project: 5A379-A03 by: oab Saddle Design - Ribs Outside Ribs

Lrib Lotrib Pr Ar fa I1 C1 r L1 Lr Cc Fa fu M fb SR Litrib Pr Ar fa I2 C2 r L2 Lr Cc Fa fu M fb SR

Rib Spacing: (E-2*d1)/(Nr-1) Tributary Length: Min (e , 0.5*Lrib) Axial Load on Ribs: Bp * F * Lotrib Area of Web and Rib: J*(F-2*d2-tweb) + tweb*(Lotrib-d1) Compressive Stress: Pr / Ar (J/12) * ((wb + F) / 2)^3 (wb + F) / 4 Radius of Gyration: (I1 / Ar)^0.5 Height of Saddle: B - Rs * Cos(Theta/2) Slenderness Ratio: L1 / r (2*PI()^2*Emod/Fy)^0.5 (1-Lr^2/(2*Cc^2))*Fy/(5/3+3*Lr/(8*Cc)-Lr^3/(8*Cc^3)) Unit Force: Fl / (2 * E) Bending Moment: 0.5 * fu * e * L1 Bending Stress: M * C1 / I1 Stress Ratio: fa/Fa+fb/Fb Inside Ribs Tributary Length: Min (e , Lrib) Axial Load on Ribs: Bp * F * Litrib Area of Web and Rib: J*(F-2*d2-tweb) + tweb*Litrib Compressive Stress: Pr / Ar (J/12) * ((wb + F) / 2)^3 0.5 * Wb Radius of Gyration: (I2 / Ar)^0.5 Height of Saddle: B - (Rs^2-(E/2-d1-Lrib)^2)^0.5 Slenderness Ratio: L1 / r (2*PI()^2*Emod/Fy)^0.5 (1-Lr^2/(2*Cc^2))*Fy/(5/3+3*Lr/(8*Cc)-Lr^3/(8*Cc^3)) Unit Force: Fl / (2 * E) Bending Moment: 0.5 * fu * e * L2 Bending Stress: M * C2 / I2 Stress Ratio: fa/Fa+fb/Fb


21.5500 in 5.2344 in 7,894 lbs 11.24 in^2 702 psi 1.080E+02 in^4 6.000 in 3.100 in 70.643 in 22.8 122.7 21,518 psi 6,897 lb/ft 1.063E+05 in-lbs 5,903 psi 0.27 5.234 7.894E+03 11.61 680 1.080E+02 6.000 3.050 34.3 11.2 122.7 22,247 6,897 5.156E+04 2,864 0.14

in lbs in^2 psi in^4 in in in

psi lb/ft in-lbs psi

02/13/2015


Description Shell Stiffened in plane of Saddle Circumferential Compressive Stress Longitudinal Tension at Saddles Longitudinal Bending @ Midspan Circumferential Stress in Shell Tensile Stress in Web Bending Stress in Saddle Bending stress in Baseplate Bearing pressure on Concrete Bending Stress due to Offset Web Bending Stress Axial Stress S.R. for Bending + Axial Bending Stress Axial Stress S.R. for Bending + Axial Tensile Stress Shear Stress


Stress Summary SR Result Tangential Shear S5 0.06 PASS Circumferential Bending S12 0.34 PASS Combined Stress - Tension S3+fx 0.96 PASS S4+fx 0.14 PASS S13+fp 0.14 PASS Saddle Web ft 0.02 PASS fb 0.04 PASS Saddle Base Plate fbplt 0.54 PASS Bp 0.17 PASS fb 0.45 PASS Saddle - Outside Ribs fb 0.24 PASS fa 0.03 PASS ftot 0.27 PASS Saddle - Inside Ribs fb 0.11 PASS fa 0.03 PASS ftot 0.14 PASS Saddle Design - Anchor Bolts fa 0.79 PASS fv 3.40 FAIL Equation


Actual

Allowable 941

16,000 psi

(6,443)

19,000 psi

19,130 2,854 -4,084

20,000 psi 20,000 psi 30,000 psi

562 1,024

22,800 psi 25,080 psi

13,572 126 11,242

25,080 psi 750 psi 25,080 psi

5,903 702 0.27

25,080 psi 21,518 psi 1.00

2,864 680 0.14

25,080 psi 22,247 psi 1.00

15,890 50,930

20,000 psi 15,000 psi

02/13/2015

Saddle Calculation

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