Is Compliance

8/10/2019 Is Compliance

http://slidepdf.com/reader/full/is-compliance 1/91

Para 6.2 & 9.3 Corrosion Allowance

The shell and cover plate shall consider 1.5 mm corrosion allowance

1.5 mm corrosion is considered in design calculation. Hence requirement is met.

Para 7.1 Material

Steel plates and section used in tank construction shall conform to any one of following

specification.

IS 22 !IS "1 ! IS 2##2 $ IS 2#%1 $ IS 2#2 $ IS &5##

IS 2#2 'r.( is used in tank construction. Hence requirement is met.

)ote * +s ,-,T is # / ! Impact testing is not required for any part of tank.

Para 8 Permissible stress

0ollowing permissile stress are considered in shell and other structrual design as per

para &.11$&.1.2 and &.1. for IS 2#2 'r.3 material.

3 4 oint efficiency #.6

Sa 4 +llowale tensile stress 4 #.6 7 15 115.5 ,pa

1162.% kg8cm2

Para 9.1 Internal Design Pressure

Tank shall e designed for #.#5 ,pa when full of liquid.

Internal design pressure #.#5 ,pa g when tank is full of water is considered in design calculation.

Hence! requirement is met.

Para 9.1 !ell an" !ea" t!ic#ness

9rovided thickness shall not e less than the thickness mentioned in tale:1.

Thickness as pe tale:1 for tank capacity 1 m ; 1 kl< .

Shell 5 mm

Head & mm

Stiffners 6# = 6# = & mm

9rovided thickness

Shell & mm

Head 1# mm

Stiffners 6# = 6# = & mm

Hence! thickness requirements are met.

Para 9.2 $%ternal Design Pressure

Tank shall e designed for e=ternal earth pressure acting on tank when it is empty.

Tank is designed for e=ternal soid pressure #.#%2 ,pa.Hence! requirement is met.

/>,9?I+)/3 T> IS 1#"&6*1""2 ;@3+00I@,3- 2## <



/>,9?I+)/3 T> IS 1#"&6*1""2 ;@3+00I@,3- 2## <

Para 12.1.3 'ening rein(orcement

The opening in tank largen than 5 mm in diameter shall e reinforced.

+ll noAAle aove 2B are reinforced as per aove requirement.

Para 12.2 Man!ole

3ach tank shall have minimum of one manhole of not less than 5## m diameter.

,anhole of siAe 2%B is provided in vessel! Hence requirement is met.

Para 1).3 *+"ro,test 'ressure

+ll tanks shall e suCect to hydraulic test at a pressure of #.#5 ,pa and checked for leaks.

The minimum thickness of the reinforcing pad shall e the same as the shell thickness and diameter

shall e twice the diameter of the hole cut suCect to diameter of the opening plus 2## mm.



PROJECT:- LPG PIPELINE PROEJCT,HPCL

EQPT.NO :-500-T-001, DIESEL TANK

Inside diameter of vessel (Di) = 1900 mmThickness of shell (ts) = 8 mm

Thickness of head (th) = 10 mm

Internal+External C = 1!"

T# to T# len$th (#) = %"00 mm

Total len$th& #total = # + 'th = 4520.00 mm

ei$ht of *rond elevation from ,essels center line () = 1%"0 mm

Densit- of soil (d) 1.!" KN/m3 = 174.!2 "#/m3

/ressre of soil actin$ on the vessel = d = 0.25$ "#/%m2

= 0.025 &'(

,olme of ,essel& ,s = (i Do' #total ) 2 % = 13.034 m3

,olme of no33les& ,n )R*+* '+ +%* C(%( - m* A6 = 0.40 m3

,total = alf of vessel volme + ,olme of no33les = !.$1 m3

,sv = ,olme of soil a4ove the ,essel (from Center line of vessel) = #total Do 5 ,total = 5.!40 m3

6ei$ht of soil& 6s = ,sv d = 100!4.$0 "#

7eratin$ ei$ht of vessel from PVELITE = 1'00!00 "#

Total ei$ht to 4e considered for concrete saddle anal-sis = 2!2!4.$0 "#

(ei$ht of soil + 7eratin$ ei$ht of ,essel)

E:TE;<# /;E>;E <D 7I# 6EI*T C#C>#TI7<





SHELL ID 1900 mm

SHELL LENGTH 4500 mm

SHELL THK 8 mm

HEAD THK 10 mm

BOOT SHELL OD 0 mm

BOOT SHELL LENGTH 0 mm

NUMBER OF BOOTS 1

CORRODED EMPTY WT OF VESSEL (Wv !450"0 kg

BOLT SI#E M$4

BOLT CORROSION ALLOWANCE 1"% mm

CORRODED ROOT AREA OF BOLT& A' !"01$8 cm2

NO" OF BOLTS& N 4

ENTER TENSILE STRESS OF THE OLT 15!0 kg!cm2ENTER SHEAR STRESS OF THE OLT 10$0 kg!cm2

NO##LE DATA

MARKM

N$)

N!

N4)

N5N%

N11)

N1$

N1)

N1!*TY 1 $ $ 1 $ $

OD %10 508 88"9 114"! $19"08 %0"!!

LENGTH 500 500 500 500 500 500

VOLUME(M! OF NO##LES + A 0"15 0"$0 0"01 0"01 0"04 0"00 0"40

VOLUME OF VESSEL + 14"8 M!

VOLUME OF BOOT + C 0"0 M!

TOTAL VOLUME OF VESSEL& " , A--C 15 M!

WATER FORCE& #$ , " % 1000 15$$8 KG

NET UPLIFT FORCE& &' , #$ + #( 118 KG

UPLIFT FORCE CONSIDERING 10. E/TRA&

&') 1$9%0 KG

SEISMIC SHEAR STRESS& F* 1%$0 KG

INDUCED TENSILE STRESS IN BOLTS&

ST , &') ) N A+ 104 KG)CM$

INDUCED SHEAR STRESS IN BOLTS&

SS , F*) N A+ 1!4 KG)CM!

UPLIFT FORCE CALCULATION

DESIGN IS SAFE

DESIGN IS SAFE

TOTAL



PV Elite 2013 Licensee:FileName : 500-T-100-R0 ----------------------------------

Input Echo : Step: 1 1:26p Aug 15,2014

SHELL THICKNESS CALCULATION UNDER INT. PRESSURE

PV Elite Vessel Analysis Program: Input Data

Design Internal Pressure (for test) 0.05000 MPa

Design Internal Temperature 65 °C

Type of Test User Entered Pressure

Test Position Horizontal

Projection of Nozzle from Vessel Top 800.00 mm

Projection of Nozzle from Vessel Bottom 0.0000 mm

Minimum Design Metal Temperature 0 °C

Type of Construction Welded

Special Service None

Degree of Radiography RT-4

Miscellaneous Weight Percent 0.0

Use Higher Longitudinal Stresses (Flag) Y

Select t for Internal Pressure (Flag) N

Select t for External Pressure (Flag) NSelect t for Axial Stress (Flag) N

Select Location for Stiff. Rings (Flag) N

Consider Vortex Shedding N

Perform a Corroded Pressure test N

Is this a Heat Exchanger No

User Defined Test Press. (Used if > 0) 0.05000 MPa

User defined MAWP 0.0000 MPa

User defined MAPnc 0.0000 MPa

Load Case 1 NP+EW+WI+FW+BW

Load Case 2 NP+EW+EE+FS+BS

Load Case 3 NP+OW+WI+FW+BW

Load Case 4 NP+OW+EQ+FS+BSLoad Case 5 NP+HW+HI

Load Case 6 NP+HW+HE

Load Case 7 IP+OW+WI+FW+BW

Load Case 8 IP+OW+EQ+FS+BS

Load Case 9 EP+OW+WI+FW+BW

Load Case 10 EP+OW+EQ+FS+BS

Load Case 11 HP+HW+HI

Load Case 12 HP+HW+HE

Load Case 13 IP+WE+EW

Load Case 14 IP+WF+CW

Load Case 15 IP+VO+OW

Load Case 16 IP+VE+EW

Load Case 17 NP+VO+OW

Load Case 18 FS+BS+IP+OW

Load Case 19 FS+BS+EP+OW

Wind Design Code No Wind Loads

Seismic Design Code No Seismic

Design Nozzle for Des. Press. + St. Head Y

Consider MAP New and Cold in Noz. Design N

Consider External Loads for Nozzle Des. Y

Use ASME VIII-1 Appendix 1-9 N





Material Database Year Current w/Addenda or Code Year

Configuration Directives:

Do not use Nozzle MDMT Interpretation VIII-1 01-37 NoUse Table G instead of exact equation for "A" Yes

Shell Head Joints are Tapered Yes

Compute "K" in corroded condition Yes

Use Code Case 2286 No

Use the MAWP to compute the MDMT Yes

Using Metric Material Databases, ASME II D No

Complete Listing of Vessel Elements and Details:

Element From Node 10

Element To Node 20

Element Type Flat

Description Head-LHSDistance "FROM" to "TO" 10.0000 mm

Inside Diameter 1900.0 mm

Element Thickness 10.000 mm

Internal Corrosion Allowance 1.5000 mm

Nominal Thickness 0.0000 mm

External Corrosion Allowance 0.0000 mm

Design Internal Pressure 0.05000 MPa

Design Temperature Internal Pressure 65 °C

Design External Pressure 0.02500 MPa

Design Temperature External Pressure 65 °C

Effective Diameter Multiplier 1.2

Material Name SA-516 70

Allowable Stress, Ambient 137.90 MPa

Allowable Stress, Operating 137.90 MPa

Allowable Stress, Hydrotest 179.27 MPa

Material Density 0.007750 kg/cm^3

P Number Thickness 31.750 mm

Yield Stress, Operating 246.47 MPa

UCS-66 Chart Curve Designation B

External Pressure Chart Name CS-2

UNS Number K02700

Product Form Plate

Efficiency, Longitudinal Seam 1.0

Efficiency, Circumferential Seam 1.0

Flat Head Attachment Factor 0.2

Small diameter if Non-Circular 0.0000 mm

--------------------------------------------------------------------


Element To Node 30

Element Type Cylinder

Description shell

Distance "FROM" to "TO" 4500.0 mm













Design Temperature External Pressure 65 °CEffective Diameter Multiplier 1.2





Detail Type Liquid

Detail ID WATER

Dist. from "FROM" Node / Offset dist 0.0000 mm

Height/Length of Liquid 1900.0 mm

Liquid Density 0.0009984 kg/cm^3

Element From Node 20Detail Type Nozzle

Detail ID N1


Nozzle Diameter 2.0 in.

Nozzle Schedule 80

Nozzle Class 150

Layout Angle 90.0

Blind Flange (Y/N) N

Weight of Nozzle ( Used if > 0 ) 219.23 N

Grade of Attached Flange GR 1.1

Nozzle Matl SA-106 B


Detail Type Nozzle

Detail ID N2



Nozzle Schedule None

Nozzle Class 150

Layout Angle 90.0




Nozzle Matl SA-516 70


Detail Type Nozzle

Detail ID N3




Nozzle Class 150

Layout Angle 90.0










Detail Type Nozzle

Detail ID N4


Nozzle Diameter 3.0 in.Nozzle Schedule 80

Nozzle Class 150

Layout Angle 90.0






Detail Type Nozzle

Detail ID N5


Nozzle Diameter 3.0 in.Nozzle Schedule 80

Nozzle Class 150

Layout Angle 90.0






Detail Type Nozzle

Detail ID N6



Nozzle Schedule 80

Nozzle Class 150

Layout Angle 90.0

Blind Flange (Y/N) Y





Detail Type Nozzle

Detail ID N11



Nozzle Schedule 40

Nozzle Class 150

Layout Angle 90.0






Detail Type Nozzle

Detail ID N12







Nozzle Schedule 40

Nozzle Class 150

Layout Angle 90.0

Blind Flange (Y/N) YWeight of Nozzle ( Used if > 0 ) 716.37 N




Detail Type Nozzle

Detail ID N13



Nozzle Schedule 80

Nozzle Class 150

Layout Angle 90.0

Blind Flange (Y/N) NWeight of Nozzle ( Used if > 0 ) 219.23 N




Detail Type Nozzle

Detail ID M




Nozzle Class 150

Layout Angle 90.0





--------------------------------------------------------------------


Element To Node 40

Element Type Flat

Description Head-RHS

Distance "FROM" to "TO" 10.0000 mm









Design Temperature External Pressure 65 °C

Effective Diameter Multiplier 1.2








Flat Head Attachment Factor 0.2

Small diameter if Non-Circular 0.0000 mm

PV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2013




Internal Pressure Calculations : Step: 3 1:26p Aug 15,2014

Element Thickness, Pressure, Diameter and Alloa!le "tress :

| | Int. Press | Nominal | Total Corr| Element | Allowable |

From| To | + Liq. Hd | Thickness | Allowance | Diameter | Stress(SE)|

| | MPa | mm | mm | mm | MPa |

---------------------------------------------------------------------------shell| 0.06864 | ... | 1.5000 | 1900.0 | 96.530 |

Element #e$uired Thickness and %A&P :

| | Design | M.A.W.P. | M.A.P. | Minimum | Required |

From| To | Pressure | Corroded | New & Cold | Thickness | Thickness |

| | MPa | MPa | MPa | mm | mm |

----------------------------------------------------------------------------

shell| 0.050000 | No Calc | No Calc | 8.00000 | 3.00000 |

Internal Pressure Calculation #esults :

Cylindrical Shell 'rom () To *) "A+-. /) , 0C"+.. Cr12 3 at . °C

shell

Material UNS Number: K02700

Required Thickness due to Internal Pressure tr!:

= (P*R)/(S*E-0.6*P) per UG-27 (c)(1)

= (0.069*951.5001)/(137.90*0.70-0.6*0.069)

= 0.6769 + 1.5000 = 2.1769 mm

Note: The thickness required was less than the Code Minimum, therefore

the Code Minimum value of 1.5000 mm per UG-16 will be used.

"ctual stress at #i$en %ressure and thickness& corroded Sact!:

= (P*(R+0.6*t))/(E*t)

= (0.069*(951.5001+0.6*6.5000))/(0.70*6.5000)

= 14.413 MPa

Percent Elongation per UCS-79 (50*tnom/Rf)*(1-Rf/Ro) 0.419 %

Minimum Design Metal Temperature Results:

Govrn. thk, tg = 8.000 , tr = 18.795 , c = 1.5000 mm , E* = 0.80

Stress Ratio = tr * (E*)/(tg - c) = 1.000 , Temp. Reduction = 0 °C

Min Metal Temp. w/o impact per UCS-66, Curve B -29 °C





External Pressure Calculations : Step: 4 1:26p Aug 15,2014

SHELL THICKNESS CALCULATION UNDER EXT. PRESSURE

E4ternal Pressure Calculation #esults :

A"%E Code, "ection VIII, Di1ision -, ()-), ()--a

&elded 'lat 5ead

Head-LHS

Note: This element's required thickness was computed in the internal

Pressure Report using the maximum of the Internal and External

pressures.

Cylindrical Shell 'rom () to *) E4t2 Chart: C"+( at . °C

shell

Elastic Modulus from Chart: CS-2 at 65 °C : 0.200E+06 MPa

Results for Maximum Allowable External Pressure (MAEP):

Tca OD SLEN D/t L/D Factor A B

6.500 1916.00 4500.00 294.77 2.3486 0.0001080 10.80

EMAP = (4*B)/(3*(D/t)) = (4*10.7969 )/(3*294.7693 ) = 0.0488 MPa

Results for Required Thickness (Tca):

Tca OD SLEN D/t L/D Factor A B

4.954 1916.00 4500.00 386.76 2.3486 0.0000725 7.25

EMAP = (4*B)/(3*(D/t)) = (4*7.2521 )/(3*386.7646 ) = 0.0250 MPa

Results for Maximum Stiffened Length (Slen): Tca OD SLEN D/t L/D Factor A B

6.500 1916.00 8535.94 294.77 4.4551 0.0000553 5.53

EMAP = (4*B)/(3*(D/t)) = (4*5.5315 )/(3*294.7693 ) = 0.0250 MPa

&elded 'lat 5ead

Head-RHS

Note: This element's required thickness was computed in the internal

Pressure Report using the maximum of the Internal and External

pressures.

E4ternal Pressure Calculations

| | Section | Outside | Corroded | Factor | Factor |

From| To | Length | Diameter | Thickness | A | B |

| | mm | mm | mm | | MPa |

---------------------------------------------------------------------------

10| 20| No Calc | ... | 8.50000 | No Calc | No Calc |

20| 30| 4500.00 | 1916.00 | 6.50000 | 0.00010799 | 10.7969 |

30| 40| No Calc | ... | 8.50000 | No Calc | No Calc |





External Pressure Calculations : Step: 4 1:26p Aug 15,2014

| | External | External | External | External |

From| To | Actual T. | Required T.|Des. Press. | M.A.W.P. |

| | mm | mm | MPa | MPa |

----------------------------------------------------------------

10| 20| 10.0000 | No Calc | 0.025000 | No Calc |

20| 30| 8.00000 | 6.45392 | 0.025000 | 0.048838 |30| 40| 10.0000 | No Calc | 0.025000 | No Calc |

Minimum 0.049


| | Actual Len.| Allow. Len.| Ring Inertia | Ring Inertia |

From| To | Bet. Stiff.| Bet. Stiff.| Required | Available |

| | mm | mm | mm^4 | mm^4 |

-------------------------------------------------------------------

10| 20| No Calc | No Calc | No Calc | No Calc |

20| 30| 4500.00 | 8535.94 | No Calc | No Calc |

30| 40| No Calc | No Calc | No Calc | No Calc |

Elements Suitable for External Pressure.





Element and Detail Weights : Step: 5 1:26p Aug 15,2014

WEIGHT CALCULATION

Element and Detail &eights

| | Element | Element | Corroded | Corroded | Extra due |

From| To | Metal Wgt. | ID Volume |Metal Wgt. | ID Volume | Misc % |

| | kg | ltr | kg | ltr | kg |

---------------------------------------------------------------------------

10| 20| 219.749 | ... | 186.787 | ... | 21.9749 |

20| 30| 1672.47 | 12761.1 | 1359.95 | 12801.4 | 167.247 |

30| 40| 219.749 | ... | 186.787 | ... | 21.9749 |

---------------------------------------------------------------------------

Total 2111 12761.08 1733 12801.41 211

&eight of Details

| | Weight of | X Offset, | Y Offset, |

From|Type| Detail | Dtl. Cent. |Dtl. Cent. | Description| | kg | mm | mm |

-------------------------------------------------

20|Liqd| 12753.3 | 2250.00 | ... | WATER

20|Nozl| 24.5919 | 150.000 | 974.625 | N1

20|Nozl| 168.794 | 630.000 | 1204.00 | N2

20|Nozl| 168.794 | 1380.00 | 1204.00 | N3

20|Nozl| 50.3101 | 1870.00 | 986.830 | N4

20|Nozl| 50.5056 | 2110.00 | 986.830 | N5

20|Nozl| 36.0362 | 2370.00 | 998.590 | N6

20|Nozl| 80.3599 | 2710.00 | 1059.54 | N11

20|Nozl| 80.3599 | 3110.00 | 1059.54 | N12

20|Nozl| 24.5919 | 3630.00 | 974.625 | N13

20|Nozl| 435.458 | 3900.00 | 1254.80 | M

Total &eight of Each Detail Type

Total Weight of Liquid 12753.3

Total Weight of Nozzles 1119.8

---------------------------------------------------------------

Sum of the Detail Weights 13873.1 kg

Weight Summation

Fabricated Shop Test Shipping Erected Empty Operating

------------------------------------------------------------------------------

2323.2 3443.0 2323.2 3443.0 2323.2 3443.0

... 12753.3 ... ... ... 12753.3

1119.8 ... 1119.8 ... ... ...

... ... ... ... ... ...

... ... ... ... ... ...

... ... ... ... 1119.8 ...

------------------------------------------------------------------------------

3443.0 16196.3 3443.0 3443.0 3443.0 16196.3 kg

%iscellaneous &eight Percent: -)2) 6




Element and Detail Weights : Step: 5 1:26p Aug 15,2014

Note that the above value for the miscellaneous weight percent has

been applied to the shells/heads/flange/tubesheets/tubes etc. in the

weight calculations for metallic components.

Note: The shipping total has been modified because some items have been specified as being installed in the shop.

Weight Summary

Fabricated Wt. - Bare Weight W/O Removable Internals 3443.0 kg

Shop Test Wt. - Fabricated Weight + Water ( Full ) 16196.3 kg

Shipping Wt. - Fab. Wt + Rem. Intls.+ Shipping App. 3443.0 kg

Erected Wt. - Fab. Wt + Rem. Intls.+ Insul. (etc) 3443.0 kg

Ope. Wt. no Liq - Fab. Wt + Intls. + Details + Wghts. 3443.0 kg

Operating Wt. - Empty Wt + Operating Liq. Uncorroded 16196.3 kg

Oper. Wt. + CA - Corr Wt. + Operating Liquid 15780.0 kg

Field Test Wt. - Empty Weight + Water (Full) 16196.3 kg

Note: The 'orroded (ei#ht and thickness are used in the )ori*ontal

+essel "nal,sis -.%e 'ase/ and arthquake 1oad 'alculations

7utside "urface Areas of Elements

| | Surface |

From| To | Area |

| | mm^2 |

----------------------------

10| 20| ... |

20| 30| 27.09E+06 |

30| 40| ... |

-------------------------------

Total 27086818.000 mm^2





Nozzle Flange MAWP : Step: 6 1:26p Aug 15,2014

NOZZLE NECK AND ITS REINFORCEMENT CALCULATION

8o99le 'lange %A&P #esults :

Nozzle ----- Flange Rating

Description Operating Ambient Temperature Class Grade|Group

MPa MPa °C

----------------------------------------------------------------------------

N1 1.9 2.0 65 150 GR 1.1

N2 1.9 2.0 65 150 GR 1.1

N3 1.9 2.0 65 150 GR 1.1

N4 1.9 2.0 65 150 GR 1.1

N5 1.9 2.0 65 150 GR 1.1

N6 1.9 2.0 65 150 GR 1.1

N11 1.9 2.0 65 150 GR 1.1

N12 1.9 2.0 65 150 GR 1.1

N13 1.9 2.0 65 150 GR 1.1M 1.9 2.0 65 150 GR 1.1

----------------------------------------------------------------------------

Minimum Rating 1.9 2.0 MPa

Note: ANSI Ratings are per ANSI/ASME B16.5 2009 Metric Edition





Center of Gravity Calculation : Step: 7 1:26p Aug 15,2014

"hop'ield Installation 7ptions :

Note : The CG is computed from the first Element From Node

Center of Gravity of Liquid 2260.000 mm

Center of Gravity of Nozzles 2585.695 mm

Center of Gravity of Bare Shell New and Cold 2260.000 mm

Center of Gravity of Bare Shell Corroded 2260.000 mm

Vessel CG in the Operating Condition 2283.113 mm

Vessel CG in the Fabricated (Shop/Empty) Condition 2365.930 mm





Nozzle Calcs. : N1 Nozl: 11 1:26p Aug 15,2014

I8P0T VAL0E", 8o99le Description: 8- 'rom : ()

Pressure for Reinforcement Calculations P 0.0500 MPa

Temperature for Internal Pressure Temp 65 °C

Design External Pressure Pext 0.03 MPaTemperature for External Pressure Tempex 65 °C

Shell Material SA-516 70

Shell Allowable Stress at Temperature S 137.90 MPa

Shell Allowable Stress At Ambient Sa 137.90 MPa

Inside Diameter of Cylindrical Shell D 1900.00 mm

Design Length of Section L 4500.0005 mm

Shell Finished (Minimum) Thickness t 8.0000 mm

Shell Internal Corrosion Allowance c 1.5000 mm

Shell External Corrosion Allowance co 0.0000 mm

Distance from Bottom/Left Tangent 160.0000 mm

User Entered Minimum Design Metal Temperature 0.00 °C

Type of Element Connected to the Shell : Nozzle

Material SA-106 B

Material UNS Number K03006

Material Specification/Type Smls. pipe

Allowable Stress at Temperature Sn 117.90 MPa

Allowable Stress At Ambient Sna 117.90 MPa

Diameter Basis (for tr calc only) ID

Layout Angle 90.00 deg

Diameter 2.0000 in.

Size and Thickness Basis Nominal

Nominal Thickness tn 80

Flange Material SA-105

Flange Type Slip on

Corrosion Allowance can 1.5000 mm

Joint Efficiency of Shell Seam at Nozzle E1 1.00

Joint Efficiency of Nozzle Neck En 1.00

Outside Projection ho 800.0000 mm

Weld leg size between Nozzle and Pad/Shell Wo 6.0000 mm

Groove weld depth between Nozzle and Vessel Wgnv 8.0000 mm

Inside Projection h 1900.0001 mm

Weld leg size, Inside Element to Shell Wi 0.0000 mm

ASME Code Weld Type per UW-16 None

Class of attached Flange 150

Grade of attached Flange GR 1.1

The Pressure Design option was Design Pressure + static head.





Nozzle Sketch (may not represent actual weld type/configuration)

| |

| |

| |

| | ____________/| |

| \ | |

| \ | |

|____________\| |

\| |

|__|

Insert Nozzle No Pad, with Inside projection

#einforcement CALC0LATI78, Description: 8-

ASME Code, Section VIII, Division 1, 2010, 2011a, UG-37 to UG-45

Actual Inside Diameter Used in Calculation 1.939 in.

Actual Thickness Used in Calculation 0.218 in.

No**le in%ut data check com%leted 3ithout errors

Reqd thk %er U4567-a/o ',lindrical Shell& Tr Int Press!

= (P*R)/(S*E-0.6*P) per UG-27 (c)(1)

= (0.05*951.5001)/(137*1.00-0.6*0.05)

= 0.3451 mm

Reqd thk %er U4567-a/o No**le (all& Trn Int Press!

= (P*R)/(S*E-0.6*P) per UG-27 (c)(1)

= (0.05*26.13)/(117*1.00-0.6*0.05)

= 0.0111 mm

Required Nozzle thickness under External Pressure per UG-28 : 0.3175 mm

UG-40, Limits of Reinforcement : [External Pressure]

Parallel to Vessel Wall (Diameter Limit) Dl 104.5012 mm

Parallel to Vessel Wall, opening length d 52.2506 mm

Normal to Vessel Wall (Thickness Limit), no pad Tlnp 10.0930 mm

Normal to Vessel Wall, Inward 6.3430 mm

Note:

Taking a UG-36(c)(3)(a) exemption for nozzle: N1.

This calculation is valid for nozzles that meet all the requirements of

paragraph UG-36. Please check the Code carefully, especially for nozzles

that are not isolated or do not meet Code spacing requirements. To force

the computation of areas for small nozzles go to Tools->Configuration

and check the box to force the UG-37 small nozzle area calculation or

force the Appendix 1-10 computation in Nozzle Design Options.

UG-45 Minimum Nozzle Neck Thickness Requirement: [Int. Press.]

Wall Thickness for Internal/External pressures ta = 1.8175 mm

Wall Thickness per UG16(b), tr16b = 3.0000 mm

Wall Thickness, shell/head, internal pressure trb1 = 1.8451 mm





Wall Thickness tb1 = max(trb1, tr16b) = 3.0000 mm


Wall Thickness per table UG-45 tb3 = 4.9200 mm

Determine Nozzle Thickness candidate [tb]:

= min[ tb3, max( tb1,tb2) ]= min[ 4.920 , max( 3.000 , 3.000 ) ]

= 3.0000 mm

Minimum Wall Thickness of Nozzle Necks [tUG-45]:

= max( ta, tb )

= max( 1.8175 , 3.0000 )

= 3.0000 mm

Available Nozzle Neck Thickness = 0.875 * 5.537 = 4.845 mm --> OK

8o99le ;unction %inimum Design %etal Temperature <%D%T= Calculations:

MDMT of the Nozzle Neck to Flange Weld, Curve: B ----------------------------------------------------------------------




Min Metal Temp. at Required thickness (UCS 66.1) -104 °C

MDMT of Nozzle-Shell/Head Weld for the Nozzle (UCS-66(a)1(b)), Curve: B

----------------------------------------------------------------------





Governing MDMT of all the sub-joints of this Junction : -104 °C

ANSI Flange MDMT including Temperature reduction per UCS-66.1:

Unadjusted MDMT of ANSI B16.5/47 flanges per UCS-66(c) -29 °C

Flange MDMT with Temp reduction per UCS-66(b)(1)(b) -104 °C

Flange MDMT with Temp reduction per UCS-66(b)(1)(c) -104 °C

Where the Stress Reduction Ratio per UCS-66(b)(1)(b) is :

Design Pressure/Ambient Rating = 0.05/1.96 = 0.026

Note: Using the minimum value from (b)(1)(b) and (b)(1)(c) above

as the calculated nozzle flange MDMT.

(eld Si*e 'alculations& 8escri%tion: N9

Intermediate Calc. for nozzle/shell Welds Tmin 4.0372 mm

Results Per UW-16.1:

Required Thickness Actual Thickness

Nozzle Weld 2.8260 = 0.7 * tmin. 4.2420 = 0.7 * Wo mm





NOTE : Skipping the nozzle attachment weld strength calculations.

Per UW-15(b)(2) the nozzles exempted by UG-36(c)(3)(a)

(small nozzles) do not require a weld strength check.

The Drop for this Nozzle is : 0.4789 mm The Cut Length for this Nozzle is, Drop + Ho + H + T : 2708.0002 mm






I8P0T VAL0E", 8o99le Description: 8( 'rom : ()















Material SA-516 70


Material Specification/Type Plate



Diameter Basis (for tr calc only) OD


Diameter 20.0000 in.

Size and Thickness Basis Actual

Actual Thickness tn 8.0000 mm


Flange Type Slip on









Pad Material SA-516 70

Pad Allowable Stress at Temperature Sp 137.90 MPa

Pad Allowable Stress At Ambient Spa 137.90 MPa

Diameter of Pad along vessel surface Dp 700.0000 mm

Thickness of Pad te 8.0000 mm

Weld leg size between Pad and Shell Wp 6.0000 mm





= 1.000

Weld Strength Reduction Factor [fr4]:

= min( 1, Sp/S )

= min( 1, 137.9/137.9 )

= 1.000


= min( fr2, fr4 )

= min( 1.0 , 1.0 )

= 1.000

Results of Nozzle Reinforcement Area Calculations:

AREA AVAILABLE, A1 to A5 Design External Mapnc

Area Required Ar NA 1226.095 NA mm^2

Area in Shell A1 NA 765.311 NA mm^2

Area in Nozzle Wall A2 NA 175.113 NA mm^2

Area in Inward Nozzle A3 NA 0.000 NA mm^2

Area in Welds A41+A42+A43 NA 85.000 NA mm^2Area in Element A5 NA 1536.000 NA mm^2

TOTAL AREA AVAILABLE Atot NA 2561.424 NA mm^2

Nozzle Angle Used in Area Calculations 90.00 Degs.

The area available without a pad is Insufficient.

The area available with the given pad is Sufficient.

SELECTION OF POSSIBLE REINFORCING PADS: Diameter Thickness

Based on given Pad Thickness: 533.0839 8.0000 mm

Based on given Pad Diameter: 700.0000 1.0452 mm

Based on Shell or Nozzle Thickness: 533.0839 8.0000 mm

"rea Required "!:

= 0.5( d * tr*F + 2 * tn * tr*F * (1-fr1) ) per UG-37(d) or UG-39

= 0.5(495.0000*4.9539*1+2*6.5000*4.9539*1*(1-1.00))

= 1226.095 mm^2

Reinforcement Areas per Figure UG-37.1

Area Available in Shell [A1]:

= d( E1*t - F*tr ) - 2 * tn( E1*t - F*tr ) * ( 1 - fr1 )

= 495.000 ( 1.00 * 6.5000 - 1.0 * 4.954 ) - 2 * 6.500

( 1.00 * 6.5000 - 1.0 * 4.9539 ) * ( 1 - 1.000 )

= 765.311 mm^2

Area Available in Nozzle Wall Projecting Outward [A2]:

= ( 2 * Tlwp ) * ( tn - trn ) * fr2

= ( 2 * 16.25 ) * ( 6.50 - 1.11 ) * 1.0000

= 175.113 mm^2

Area Available in Welds [A41 + A42 + A43]:

= Wo²*fr3+(Wi-can/0.707)²*fr2+Wp²*fr4

= 7.0000² *1.00 + (0.0000 )² *1.00 + 6.0000² * 1.00

= 85.000 mm^2

Area Available in Element [A5]:





= (min(Dp,DL)-(Nozzle OD))*(min(tp,Tlwp,te))*fr4

= ( 700.0000 - 508.0000 ) * 8.0000 * 1.0000

= 1536.000 mm^2


Wall Thickness for Internal/External pressures ta = 2.6119 mmWall Thickness per UG16(b), tr16b = 3.0000 mm






= min[ tb3, max( tb1,tb2) ]

= min[ 9.831 , max( 3.000 , 3.000 ) ]

= 3.0000 mm


= max( ta, tb )= max( 2.6119 , 3.0000 )

= 3.0000 mm

Available Nozzle Neck Thickness = 8.0000 mm --> OK


MDMT of the Nozzle Neck to Flange Weld, Curve: B

----------------------------------------------------------------------





MDMT of Nozzle Neck to Pad Weld for the Nozzle, Curve: B

----------------------------------------------------------------------





MDMT of Nozzle Neck to Pad Weld for Reinforcement pad, Curve: B

----------------------------------------------------------------------





MDMT of Shell to Pad Weld at Pad OD for pad, Curve: B

----------------------------------------------------------------------










----------------------------------------------------------------------





Governing MDMT of the Nozzle : -104 °C

Governing MDMT of the Reinforcement Pad : -104 °C










Nozzle Calculations per App. 1-10: Internal Pressure Case:

Thickness of Nozzle [tn]:

= thickness - corrosion allowance

= 8.000 - 1.500

= 6.500 mm

Effective Pressure Radius [Reff]:

= Di/2 + corrosion allowance

= 1900.000/2 + 1.500

= 951.500 mm

Effective Length of Vessel Wall [LR]:

Note : Pad Thk >= 0.5T and Pad Width < 8(Shell Thk + Pad Thk)

= 10 * t

= 10 * 6.500

= 65.000 mm

Thickness Limit Candidate [LH1]:

= t + 0.78 * sqrt( Rn * tn )

= 6.500 + 0.78 * sqrt( 247.500 * 6.500 )

= 37.785 mm


= Lpr1 + T

= 800.000 + 6.500

= 806.500 mm






= 8( t + te )

= 8( 6.500 + 8.000 )

= 116.000 mm

Effective Nozzle Wall Length Outside the Vessel [LH]:

= min[ LH1, LH2, LH3 ]= min[ 37.785 , 806.500 , 116.000 )

= 37.785 mm

Effective Vessel Thickness [teff]:

= t

= 6.500 mm

Determine Parameter [Lamda]:

= min( 10, ( Dn + Tn )/( sqrt( ( Di + teff ) * teff )) )

= min( 10, (495.00 + 6.500 )/( sqrt((1903.00 + 6.500 ) * 6.500 )) )

= 4.501

Compute Areas A1-A43 (No Pad) or A1-A5 (With Pad) :

Area Contributed by the Vessel Wall [A1]:

= t * LR * max( Lamda/4, 1 )

= 6.500 * 65.000 * max( 4.501/4, 1 )

= 475.468 mm^2

Area Contributed by the Nozzle Outside the Vessel Wall [A2]:

= tn * LH

= 6.500 * 37.785

= 245.604 mm^2

Area Contributed by the Outside Fillet Weld [A41]:

= 0.5 * Leg412

= 0.5 * 7.0002

= 24.500 mm^2

Area Contributed by the Reinforcing Pad [A5]:

= min( W * te , LR * te )

= min( 96.000 * 8.000 , 65.000 * 8.000 )

= 520.000 mm^2

The total area contributed by A1 through A5 [AT]:

= A1 + frn( A2 + A3 ) + A41 + A42 + A43 + frp( A5 )

= 475.468+1.000(245.604+0.000)+24.500+0.000+0.000+1.000(520.000)

= 1265.572 mm^2

Allowable Local Primary Membrane Stress [Sallow]:

= 1.5 * S * E

= 1.5 * 137.900 * 1.000

= 206.9 MPa

Determine Force acting on the Nozzle [fN]:

= P * Rn( LH - t )

= 0.050 * 247.500 ( 37.785 - 6.500 )

= 387.1 N

Determine Force acting on the Shell [fS]:





= P * Reff * ( LR + tn )

= 0.050 * 951.500 * ( 65.000 + 6.500 )

= 3401.3 N

Discontinuity Force from Internal Pressure [fY]:

= P * Reff * Rnc= 0.050 * 951.500 * 247.500

= 11773.8 N

Area Resisting Internal Pressure [Ap]:

= Rn( LH - t ) + Reff( LR + tn + Rnc )

= 247.500 ( 37.785 - 6.500 ) + 951.500 ( 65.000 + 6.500 + 247.500 )

= 311271.6 mm^2

Maximum Allowable Working Pressure Candidate [Pmax1]:

= Sallow /( 2 * Ap/AT - Rxs/teff )

= 206.850/( 2 * 311271.594/1265.572 - 951.500/6.500 )

= 0.6 MPa


= S[t/Reff]

= 137.900 [6.500/951.500 ]

= 0.9 MPa

Maximum Allowable Working Pressure [Pmax]:

= min( Pmax1, Pmax2 )

= min( 0.599 , 0.942 )

= 0.599 MPa

Average Primary Membrane Stress [SigmaAvg]:

= ( fN + fS + fY ) / AT

= ( 387.121 + 3401.323 + 11773.812 )/1265.572

= 12.298 MPa

General Primary Membrane Stress [SigmaCirc]:

= P * Reff / teff

= 0.050 * 951.500/6.500

= 7.3 MPa

Maximum Local Primary Membrane Stress [PL]:

= max( 2 * SigmaAvg - SigmaCirc, SigmaCirc )

= max( 2 * 12.298 - 7.319 , 7.319 )

= 17.3 MPa

Summary of Nozzle Pressure/Stress Results:

Allowed Local Primary Membrane Stress Sallow 206.85 MPa

Local Primary Membrane Stress PL 17.28 MPa

Maximum Allowable Working Pressure Pmax 0.60 MPa

Strength of Nozzle Attachment Welds per 1-10 and U-2(g)

Discontinuity Force Factor [ky]:

= ( Rnc + tn ) / Rnc

= ( 247.500 + 6.500 )/247.500

= 1.026 For set-in Nozzles





Weld Length of Nozzle to Shell Weld [Ltau]:

= pi/2 * ( Rn + tn )

= pi/2 * ( 247.500 + 6.500 )

= 398.982 mm

Weld Length of Pad to Shell Weld [LtauP]: = pi/2 * ( Rn + tn + W )

= pi/2 * ( 247.500 + 6.500 + 96.000 )

= 549.779 mm

Weld Throat Dimensions, (0.7071*Leg Dimensions) [L41T, L42T, L43T]:

= 4.950, 4.243, 0.000, mm

Weld Load Value [fwelds]:

= min( fy * ky, 1.5 * Sn( A2 + A3 ), pi/4*P*Rn^2*ky^2 )

= min(11773*1.03,1.5*137.9(245.604+0.000),pi/4*0.1*247.50^2*1.03^2)

= 2533.322 N

Discontinuity Force [fws]: = fwelds * t * S/( t * S + te * Sp )

= 2533.3*6.50*137/(6.500*137+8.000*137)

= 1135.627 N

Discontinuity Force [fwp]:

= fwelds * te * Sp / ( t * S + te * Sp )

= 2533.3*8.00*137/(6.500*137+8.000*137)

= 1397.695 N

Shear Stress [tau1]:

= fws / ( Ltau * ( 0.6 * tw1 + 0.49 * L43T ) )

= 1135.627/( 398.982 * ( 0.6 * 6.500 + 0.49 * 0.000 ) )

= 0.730 MPa


= fwp / ( Ltau * ( 0.6 * tw2 + 0.49 * L41T ) )

= 1397.695/( 398.982 * ( 0.6 * 8.000 + 0.49 * 4.950 ) )

= 0.485 MPa


= fwp / ( Ltau * ( 0.49 * L42T ) )

= 1397.695/( 549.779 * ( 0.49 * 4.243 ) )

= 1.223 MPa

Maximum Shear Stress in the Welds:

= max( tau1, tau2, tau3 )

= max( 0.730 , 0.485 , 1.223 )

= 1.2 must be less than or equal to 137.9 MPa



Intermediate Calc. for pad/shell Welds TminPad 6.5000 mm








Pad Weld 3.2500 = 0.5*TminPad 4.2420 = 0.7 * Wp mm

Nozzle is O.K. for the External Pressure 0.025 MPa

The Drop for this Nozzle is : 34.5854 mm

The Cut Length for this Nozzle is, Drop + Ho + H + T : 842.5854 mm

Percent Elongation Calculations:







I8P0T VAL0E", 8o99le Description: 8* 'rom : ()















Material SA-516 70











Flange Type Slip on



















Groove weld depth between Pad and Nozzle Wgpn 8.0000 mm

Reinforcing Pad Width 96.0000 mm






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Insert Nozzle With Pad, no Inside projection

#einforcement CALC0LATI78, Description: 8*


Actual Outside Diameter Used in Calculation 20.000 in.




= (P*R)/(S*E-0.6*P) per UG-27 (c)(1)

= (0.05*951.5001)/(137*1.00-0.6*0.05)

= 0.3451 mm


= (P*Ro)/(S*E+0.4*P) per Appendix 1-1 (a)(1)

= (0.05*254.0000)/(137*1.00+0.4*0.05)

= 0.0921 mm





Normal to Vessel Wall (Thickness Limit), pad side Tlwp 16.2500 mm


= min( 1, Sn/S )

= min( 1, 137.9/137.9 )

= 1.000


= min( 1, Sn/S )

= min( 1, 137.9/137.9 )





= 1.000


= min( 1, Sp/S )

= min( 1, 137.9/137.9 )

= 1.000


= min( fr2, fr4 )

= min( 1.0 , 1.0 )

= 1.000
















"rea Required "!:


= 0.5(495.0000*4.9539*1+2*6.5000*4.9539*1*(1-1.00))

= 1226.095 mm^2




= 495.000 ( 1.00 * 6.5000 - 1.0 * 4.954 ) - 2 * 6.500

( 1.00 * 6.5000 - 1.0 * 4.9539 ) * ( 1 - 1.000 )

= 765.311 mm^2


= ( 2 * Tlwp ) * ( tn - trn ) * fr2

= ( 2 * 16.25 ) * ( 6.50 - 1.11 ) * 1.0000

= 175.113 mm^2



= 7.0000² *1.00 + (0.0000 )² *1.00 + 6.0000² * 1.00

= 85.000 mm^2







= ( 700.0000 - 508.0000 ) * 8.0000 * 1.0000

= 1536.000 mm^2


Wall Thickness for Internal/External pressures ta = 2.6119 mmWall Thickness per UG16(b), tr16b = 3.0000 mm







= min[ 9.831 , max( 3.000 , 3.000 ) ]

= 3.0000 mm


= max( ta, tb )= max( 2.6119 , 3.0000 )

= 3.0000 mm

Available Nozzle Neck Thickness = 8.0000 mm --> OK



----------------------------------------------------------------------






----------------------------------------------------------------------






----------------------------------------------------------------------






----------------------------------------------------------------------










----------------------------------------------------------------------



















= 8.000 - 1.500

= 6.500 mm



= 1900.000/2 + 1.500

= 951.500 mm



= 10 * t

= 10 * 6.500

= 65.000 mm


= t + 0.78 * sqrt( Rn * tn )

= 6.500 + 0.78 * sqrt( 247.500 * 6.500 )

= 37.785 mm


= Lpr1 + T

= 800.000 + 6.500

= 806.500 mm






= 8( t + te )

= 8( 6.500 + 8.000 )

= 116.000 mm


= min[ LH1, LH2, LH3 ]= min[ 37.785 , 806.500 , 116.000 )

= 37.785 mm


= t

= 6.500 mm



= min( 10, (495.00 + 6.500 )/( sqrt((1903.00 + 6.500 ) * 6.500 )) )

= 4.501



= t * LR * max( Lamda/4, 1 )

= 6.500 * 65.000 * max( 4.501/4, 1 )

= 475.468 mm^2


= tn * LH

= 6.500 * 37.785

= 245.604 mm^2


= 0.5 * Leg412

= 0.5 * 7.0002

= 24.500 mm^2



= min( 96.000 * 8.000 , 65.000 * 8.000 )

= 520.000 mm^2


= A1 + frn( A2 + A3 ) + A41 + A42 + A43 + frp( A5 )

= 475.468+1.000(245.604+0.000)+24.500+0.000+0.000+1.000(520.000)

= 1265.572 mm^2


= 1.5 * S * E

= 1.5 * 137.900 * 1.000

= 206.9 MPa


= P * Rn( LH - t )

= 0.050 * 247.500 ( 37.785 - 6.500 )

= 387.1 N







= pi/2 * ( Rn + tn )

= pi/2 * ( 247.500 + 6.500 )

= 398.982 mm

Weld Length of Pad to Shell Weld [LtauP]: = pi/2 * ( Rn + tn + W )

= pi/2 * ( 247.500 + 6.500 + 96.000 )

= 549.779 mm


= 4.950, 4.243, 0.000, mm



= min(11773*1.03,1.5*137.9(245.604+0.000),pi/4*0.1*247.50^2*1.03^2)

= 2533.322 N

Discontinuity Force [fws]: = fwelds * t * S/( t * S + te * Sp )

= 2533.3*6.50*137/(6.500*137+8.000*137)

= 1135.627 N



= 2533.3*8.00*137/(6.500*137+8.000*137)

= 1397.695 N


= fws / ( Ltau * ( 0.6 * tw1 + 0.49 * L43T ) )

= 1135.627/( 398.982 * ( 0.6 * 6.500 + 0.49 * 0.000 ) )

= 0.730 MPa


= fwp / ( Ltau * ( 0.6 * tw2 + 0.49 * L41T ) )

= 1397.695/( 398.982 * ( 0.6 * 8.000 + 0.49 * 4.950 ) )

= 0.485 MPa


= fwp / ( Ltau * ( 0.49 * L42T ) )

= 1397.695/( 549.779 * ( 0.49 * 4.243 ) )

= 1.223 MPa



= max( 0.730 , 0.485 , 1.223 )












I8P0T VAL0E", 8o99le Description: 8> 'rom : ()















Material SA-106 B







Diameter 3.0000 in.




Flange Type Slip on


























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Insert Nozzle With Pad, with Inside projection

#einforcement CALC0LATI78, Description: 8>






= (P*R)/(S*E-0.6*P) per UG-27 (c)(1)

= (0.05*951.5001)/(137*1.00-0.6*0.05)

= 0.3451 mm


= (P*R)/(S*E-0.6*P) per UG-27 (c)(1)

= (0.05*38.33)/(117*1.00-0.6*0.05)

= 0.0163 mm







Note:





















= min[ 6.300 , max( 3.000 , 3.000 ) ]

= 3.0000 mm


= max( ta, tb )

= max( 1.9091 , 3.0000 )

= 3.0000 mm




----------------------------------------------------------------------






----------------------------------------------------------------------






----------------------------------------------------------------------






----------------------------------------------------------------------










----------------------------------------------------------------------Govrn. thk, tg = 6.668 , tr = 0.016 , c = 1.5000 mm , E* = 1.00








Unadjusted MDMT of ANSI B16.5/47 flanges per UCS-66(c) -29 °CFlange MDMT with Temp reduction per UCS-66(b)(1)(b) -104 °C






(eld Si*e 'alculations& 8escri%tion: N

















I8P0T VAL0E", 8o99le Description: 8 'rom : ()















Material SA-106 B







Diameter 3.0000 in.




Flange Type Slip on


























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____/|__________\| |

| \ | |

| \ | | |________________\| |

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Insert Nozzle With Pad, with Inside projection

#einforcement CALC0LATI78, Description: 8






= (P*R)/(S*E-0.6*P) per UG-27 (c)(1)

= (0.05*951.5001)/(137*1.00-0.6*0.05)

= 0.3451 mm


= (P*R)/(S*E-0.6*P) per UG-27 (c)(1)

= (0.05*38.33)/(117*1.00-0.6*0.05)

= 0.0163 mm







Note:





















= min[ 6.300 , max( 3.000 , 3.000 ) ]

= 3.0000 mm


= max( ta, tb )

= max( 1.9091 , 3.0000 )

= 3.0000 mm




----------------------------------------------------------------------






----------------------------------------------------------------------






----------------------------------------------------------------------






----------------------------------------------------------------------


















Unadjusted MDMT of ANSI B16.5/47 flanges per UCS-66(c) -29 °CFlange MDMT with Temp reduction per UCS-66(b)(1)(b) -104 °C






(eld Si*e 'alculations& 8escri%tion: N;

















I8P0T VAL0E", 8o99le Description: 8. 'rom : ()















Material SA-106 B







Diameter 4.0000 in.




Flange Type Slip on



















= 0.855


= min( 1, Sp/S )

= min( 1, 137.9/137.9 )

= 1.000


= min( fr2, fr4 )

= min( 0.9 , 1.0 )

= 0.855










The area available without a pad is Sufficient.


"rea Required "!:


= 0.5(100.1804*4.9539*1+2*7.0598*4.9539*1*(1-0.86))

= 253.214 mm^2




= 100.180 ( 1.00 * 6.5000 - 1.0 * 4.954 ) - 2 * 7.060

( 1.00 * 6.5000 - 1.0 * 4.9539 ) * ( 1 - 0.855 )

= 151.722 mm^2


= ( 2 * Tlwp ) * ( tn - trn ) * fr2

= ( 2 * 16.25 ) * ( 7.06 - 0.47 ) * 0.8550

= 183.104 mm^2


= (Wo² - Ar Lost)*Fr3+((Wi-can/0.707)² - Ar Lost)*fr2 + Trapfr4

= (49.0000 ) * 0.86 + (0.0000 ) * 0.86 + 2.1323² * 1.00

= 44.027 mm^2



= ( 200.0000 - 114.3000 ) * 8.0000 * 1.0000

= 514.200 mm^2

Note: Per user request, A5 multiplied by 0.75, see UG-37(h).









Wall Thickness tb1 = max(trb1, tr16b) = 3.0000 mmWall Thickness tb2 = max(trb2, tr16b) = 3.0000 mm




= min[ 6.758 , max( 3.000 , 3.000 ) ]

= 3.0000 mm


= max( ta, tb )

= max( 1.9704 , 3.0000 )

= 3.0000 mm




----------------------------------------------------------------------






----------------------------------------------------------------------






----------------------------------------------------------------------






----------------------------------------------------------------------










----------------------------------------------------------------------



















= 8.560 - 1.500

= 7.060 mm



= 1900.000/2 + 1.500

= 951.500 mm



= 10 * t

= 10 * 6.500

= 65.000 mm


= t + 0.78 * sqrt( Rn * tn )

= 6.500 + 0.78 * sqrt( 50.090 * 7.060 )

= 21.168 mm


= Lpr1 + T

= 800.000 + 6.500

= 806.500 mm


= 8( t + te )

= 8( 6.500 + 8.000 )

= 116.000 mm






= min[ LH1, LH2, LH3 ]

= min[ 21.168 , 806.500 , 116.000 )

= 21.168 mm


= t

= 6.500 mm



= min( 10, (100.18 + 7.060 )/( sqrt((1903.00 + 6.500 ) * 6.500 )) )

= 0.963



= t * LR * max( Lamda/4, 1 )= 6.500 * 65.000 * max( 0.963/4, 1 )

= 422.500 mm^2


= tn * LH

= 7.060 * 21.168

= 149.441 mm^2

Area Contributed by the Pad Fillet Weld [A42]:

= 0.5 * Leg422

= 0.5 * 6.0002

= 18.000 mm^2


= 0.5 * Leg412 - Area cut by thickness limit

= 0.5 * 7.0002 - 0.055

= 24.445 mm^2



= min( 42.850 * 8.000 , 65.000 * 8.000 )

= 342.800 mm^2


= A1 + frn( A2 + A3 ) + A41 + A42 + A43 + frp( A5 )

= 422.500+1.000(149.441+0.000)+24.445+18.000+0.000+1.000(342.800)

= 957.186 mm^2


= 1.5 * S * E

= 1.5 * 137.900 * 1.000

= 206.9 MPa


= P * Rn( LH - t )

= 0.050 * 50.090 ( 21.168 - 6.500 )

= 36.7 N






= P * Reff * ( LR + tn )

= 0.050 * 951.500 * ( 65.000 + 7.060 )

= 3428.0 N


= P * Reff * Rnc

= 0.050 * 951.500 * 50.090

= 2382.8 N



= 50.090 ( 21.168 - 6.500 ) + 951.500 ( 65.000 + 7.060 + 50.090 )

= 116960.4 mm^2



= 206.850/( 2 * 116960.445/957.186 - 951.500/6.500 )= 2.1 MPa


= S[t/Reff]

= 137.900 [6.500/951.500 ]

= 0.9 MPa



= min( 2.111 , 0.942 )

= 0.942 MPa


= ( fN + fS + fY ) / AT

= ( 36.733 + 3427.954 + 2382.839 )/957.186

= 6.110 MPa


= P * Reff / teff

= 0.050 * 951.500/6.500

= 7.3 MPa



= max( 2 * 6.110 - 7.319 , 7.319 )

= 7.3 MPa








= ( 50.090 + 7.060 )/50.090







= pi/2 * ( Rn + tn )

= pi/2 * ( 50.090 + 7.060 )

= 89.771 mm

Weld Length of Pad to Shell Weld [LtauP]:

= pi/2 * ( Rn + tn + W )

= pi/2 * ( 50.090 + 7.060 + 42.850 )

= 157.080 mm


= 4.950, 4.243, 0.000, mm



= min(2382*1.14,1.5*117.9(149.441+0.000),pi/4*0.1*50.09^2*1.14^2)

= 128.249 N

Discontinuity Force [fws]:

= fwelds * t * S/( t * S + te * Sp )

= 128.2*6.50*137/(6.500*137+8.000*137)

= 57.491 N



= 128.2*8.00*137/(6.500*137+8.000*137)

= 70.758 N


= fws / ( Ltau * ( 0.6 * tw1 + 0.49 * L43T ) )

= 57.491/( 89.771 * ( 0.6 * 6.500 + 0.49 * 0.000 ) )

= 0.164 MPa


= fwp / ( Ltau * ( 0.6 * tw2 + 0.49 * L41T ) )

= 70.758/( 89.771 * ( 0.6 * 6.000 + 0.49 * 4.950 ) )

= 0.131 MPa


= fwp / ( Ltau * ( 0.49 * L42T ) )

= 70.758/( 157.080 * ( 0.49 * 4.243 ) )

= 0.217 MPa



= max( 0.164 , 0.131 , 0.217 )


(eld Si*e 'alculations& 8escri%tion: N<








I8P0T VAL0E", 8o99le Description: 8-- 'rom : ()















Material SA-106 B







Diameter 8.0000 in.




Flange Type Slip on


























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#einforcement CALC0LATI78, Description: 8--






= (P*R)/(S*E-0.6*P) per UG-27 (c)(1)

= (0.05*951.5001)/(137*1.00-0.6*0.05)

= 0.3451 mm



= (0.05*109.5375)/(117*1.00+0.4*0.05)

= 0.0464 mm







= min( 1, Sn/S )

= min( 1, 117.9/137.9 )

= 0.855


= min( 1, Sn/S )

= min( 1, 117.9/137.9 )





= 0.855


= min( 1, Sp/S )

= min( 1, 137.9/137.9 )

= 1.000


= min( fr2, fr4 )

= min( 0.9 , 1.0 )

= 0.855












"rea Required "!:


= 0.5(205.7174*4.9539*1+2*6.6788*4.9539*1*(1-0.86))

= 514.351 mm^2




= 205.717 ( 1.00 * 6.5000 - 1.0 * 4.954 ) - 2 * 6.679

( 1.00 * 6.5000 - 1.0 * 4.9539 ) * ( 1 - 0.855 )

= 315.061 mm^2


= ( 2 * Tlwp ) * ( tn - trn ) * fr2

= ( 2 * 16.25 ) * ( 6.68 - 0.68 ) * 0.8550

= 166.679 mm^2



= (49.0000 ) * 0.86 + (0.0000 ) * 0.86 + 8.0941² * 1.00

= 49.989 mm^2



= ( 410.0000 - 219.0750 ) * 8.0000 * 1.0000

= 1145.550 mm^2














= min[ 8.660 , max( 3.000 , 3.000 ) ]

= 3.0000 mm


= max( ta, tb )

= max( 2.1805 , 3.0000 )

= 3.0000 mm




----------------------------------------------------------------------






----------------------------------------------------------------------






----------------------------------------------------------------------






----------------------------------------------------------------------










----------------------------------------------------------------------



















= 8.179 - 1.500

= 6.679 mm



= 1900.000/2 + 1.500

= 951.500 mm



= 10 * t

= 10 * 6.500

= 65.000 mm


= t + 0.78 * sqrt( Rn * tn )

= 6.500 + 0.78 * sqrt( 102.859 * 6.679 )

= 26.944 mm


= Lpr1 + T

= 800.000 + 6.500

= 806.500 mm


= 8( t + te )

= 8( 6.500 + 8.000 )

= 116.000 mm







= min[ 26.944 , 806.500 , 116.000 )

= 26.944 mm


= t

= 6.500 mm



= min( 10, (205.72 + 6.679 )/( sqrt((1903.00 + 6.500 ) * 6.500 )) )

= 1.906



= t * LR * max( Lamda/4, 1 )= 6.500 * 65.000 * max( 1.906/4, 1 )

= 422.500 mm^2


= tn * LH

= 6.679 * 26.944

= 179.953 mm^2


= 0.5 * Leg412

= 0.5 * 7.0002

= 24.500 mm^2



= min( 95.463 * 8.000 , 65.000 * 8.000 )

= 520.000 mm^2


= A1 + frn( A2 + A3 ) + A41 + A42 + A43 + frp( A5 )

= 422.500+1.000(179.953+0.000)+24.500+0.000+0.000+1.000(520.000)

= 1146.953 mm^2


= 1.5 * S * E

= 1.5 * 137.900 * 1.000

= 206.9 MPa


= P * Rn( LH - t )

= 0.050 * 102.859 ( 26.944 - 6.500 )

= 105.1 N


= P * Reff * ( LR + tn )

= 0.050 * 951.500 * ( 65.000 + 6.679 )

= 3409.8 N






= P * Reff * Rnc

= 0.050 * 951.500 * 102.859

= 4893.1 N



= 102.859 ( 26.944 - 6.500 ) + 951.500 ( 65.000 + 6.679 + 102.859 )

= 168175.3 mm^2



= 206.850/( 2 * 168175.281/1146.953 - 951.500/6.500 )

= 1.4 MPa


= S[t/Reff]

= 137.900 [6.500/951.500 ]= 0.9 MPa



= min( 1.408 , 0.942 )

= 0.942 MPa


= ( fN + fS + fY ) / AT

= ( 105.133 + 3409.829 + 4893.087 )/1146.953

= 7.331 MPa


= P * Reff / teff

= 0.050 * 951.500/6.500

= 7.3 MPa



= max( 2 * 7.331 - 7.319 , 7.319 )

= 7.3 MPa








= ( 102.859 + 6.679 )/102.859



= pi/2 * ( Rn + tn )

= pi/2 * ( 102.859 + 6.679 )





= 172.061 mm


= pi/2 * ( Rn + tn + W )

= pi/2 * ( 102.859 + 6.679 + 95.463 )

= 322.013 mm


= 4.950, 4.243, 0.000, mm



= min(4893*1.06,1.5*117.9(179.953+0.000),pi/4*0.1*102.86^2*1.06^2)

= 471.139 N


= fwelds * t * S/( t * S + te * Sp )

= 471.1*6.50*137/(6.500*137+8.000*137)

= 211.200 N



= 471.1*8.00*137/(6.500*137+8.000*137)

= 259.939 N


= fws / ( Ltau * ( 0.6 * tw1 + 0.49 * L43T ) )

= 211.200/( 172.061 * ( 0.6 * 6.500 + 0.49 * 0.000 ) )

= 0.315 MPa


= fwp / ( Ltau * ( 0.6 * tw2 + 0.49 * L41T ) )

= 259.939/( 172.061 * ( 0.6 * 6.000 + 0.49 * 4.950 ) )

= 0.251 MPa


= fwp / ( Ltau * ( 0.49 * L42T ) )

= 259.939/( 322.013 * ( 0.49 * 4.243 ) )

= 0.388 MPa



= max( 0.315 , 0.251 , 0.388 )














I8P0T VAL0E", 8o99le Description: 8-( 'rom : ()















Material SA-106 B







Diameter 8.0000 in.




Flange Type Slip on


























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#einforcement CALC0LATI78, Description: 8-(






= (P*R)/(S*E-0.6*P) per UG-27 (c)(1)

= (0.05*951.5001)/(137*1.00-0.6*0.05)

= 0.3451 mm



= (0.05*109.5375)/(117*1.00+0.4*0.05)

= 0.0464 mm







= min( 1, Sn/S )

= min( 1, 117.9/137.9 )

= 0.855


= min( 1, Sn/S )

= min( 1, 117.9/137.9 )





= 0.855


= min( 1, Sp/S )

= min( 1, 137.9/137.9 )

= 1.000


= min( fr2, fr4 )

= min( 0.9 , 1.0 )

= 0.855












"rea Required "!:


= 0.5(205.7174*4.9539*1+2*6.6788*4.9539*1*(1-0.86))

= 514.351 mm^2




= 205.717 ( 1.00 * 6.5000 - 1.0 * 4.954 ) - 2 * 6.679

( 1.00 * 6.5000 - 1.0 * 4.9539 ) * ( 1 - 0.855 )

= 315.061 mm^2


= ( 2 * Tlwp ) * ( tn - trn ) * fr2

= ( 2 * 16.25 ) * ( 6.68 - 0.68 ) * 0.8550

= 166.679 mm^2



= (49.0000 ) * 0.86 + (0.0000 ) * 0.86 + 8.0941² * 1.00

= 49.989 mm^2



= ( 410.0000 - 219.0750 ) * 8.0000 * 1.0000

= 1145.550 mm^2














= min[ 8.660 , max( 3.000 , 3.000 ) ]

= 3.0000 mm


= max( ta, tb )

= max( 2.1805 , 3.0000 )

= 3.0000 mm




----------------------------------------------------------------------






----------------------------------------------------------------------






----------------------------------------------------------------------






----------------------------------------------------------------------










----------------------------------------------------------------------



















= 8.179 - 1.500

= 6.679 mm



= 1900.000/2 + 1.500

= 951.500 mm



= 10 * t

= 10 * 6.500

= 65.000 mm


= t + 0.78 * sqrt( Rn * tn )

= 6.500 + 0.78 * sqrt( 102.859 * 6.679 )

= 26.944 mm


= Lpr1 + T

= 800.000 + 6.500

= 806.500 mm


= 8( t + te )

= 8( 6.500 + 8.000 )

= 116.000 mm







= min[ 26.944 , 806.500 , 116.000 )

= 26.944 mm


= t

= 6.500 mm



= min( 10, (205.72 + 6.679 )/( sqrt((1903.00 + 6.500 ) * 6.500 )) )

= 1.906



= t * LR * max( Lamda/4, 1 )= 6.500 * 65.000 * max( 1.906/4, 1 )

= 422.500 mm^2


= tn * LH

= 6.679 * 26.944

= 179.953 mm^2


= 0.5 * Leg412

= 0.5 * 7.0002

= 24.500 mm^2



= min( 95.463 * 8.000 , 65.000 * 8.000 )

= 520.000 mm^2


= A1 + frn( A2 + A3 ) + A41 + A42 + A43 + frp( A5 )

= 422.500+1.000(179.953+0.000)+24.500+0.000+0.000+1.000(520.000)

= 1146.953 mm^2


= 1.5 * S * E

= 1.5 * 137.900 * 1.000

= 206.9 MPa


= P * Rn( LH - t )

= 0.050 * 102.859 ( 26.944 - 6.500 )

= 105.1 N


= P * Reff * ( LR + tn )

= 0.050 * 951.500 * ( 65.000 + 6.679 )

= 3409.8 N






= P * Reff * Rnc

= 0.050 * 951.500 * 102.859

= 4893.1 N



= 102.859 ( 26.944 - 6.500 ) + 951.500 ( 65.000 + 6.679 + 102.859 )

= 168175.3 mm^2



= 206.850/( 2 * 168175.281/1146.953 - 951.500/6.500 )

= 1.4 MPa


= S[t/Reff]

= 137.900 [6.500/951.500 ]= 0.9 MPa



= min( 1.408 , 0.942 )

= 0.942 MPa


= ( fN + fS + fY ) / AT

= ( 105.133 + 3409.829 + 4893.087 )/1146.953

= 7.331 MPa


= P * Reff / teff

= 0.050 * 951.500/6.500

= 7.3 MPa



= max( 2 * 7.331 - 7.319 , 7.319 )

= 7.3 MPa








= ( 102.859 + 6.679 )/102.859



= pi/2 * ( Rn + tn )

= pi/2 * ( 102.859 + 6.679 )





= 172.061 mm


= pi/2 * ( Rn + tn + W )

= pi/2 * ( 102.859 + 6.679 + 95.463 )

= 322.013 mm


= 4.950, 4.243, 0.000, mm



= min(4893*1.06,1.5*117.9(179.953+0.000),pi/4*0.1*102.86^2*1.06^2)

= 471.139 N


= fwelds * t * S/( t * S + te * Sp )

= 471.1*6.50*137/(6.500*137+8.000*137)

= 211.200 N



= 471.1*8.00*137/(6.500*137+8.000*137)

= 259.939 N


= fws / ( Ltau * ( 0.6 * tw1 + 0.49 * L43T ) )

= 211.200/( 172.061 * ( 0.6 * 6.500 + 0.49 * 0.000 ) )

= 0.315 MPa


= fwp / ( Ltau * ( 0.6 * tw2 + 0.49 * L41T ) )

= 259.939/( 172.061 * ( 0.6 * 6.000 + 0.49 * 4.950 ) )

= 0.251 MPa


= fwp / ( Ltau * ( 0.49 * L42T ) )

= 259.939/( 322.013 * ( 0.49 * 4.243 ) )

= 0.388 MPa



= max( 0.315 , 0.251 , 0.388 )














I8P0T VAL0E", 8o99le Description: 8-* 'rom : ()















Material SA-106 B







Diameter 2.0000 in.




Flange Type Slip on


















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Insert Nozzle No Pad, with Inside projection

#einforcement CALC0LATI78, Description: 8-*






= (P*R)/(S*E-0.6*P) per UG-27 (c)(1)

= (0.05*951.5001)/(137*1.00-0.6*0.05)

= 0.3451 mm


= (P*R)/(S*E-0.6*P) per UG-27 (c)(1)

= (0.05*26.13)/(117*1.00-0.6*0.05)

= 0.0111 mm





Normal to Vessel Wall (Thickness Limit), no pad Tlnp 10.0930 mm


Note:




















= min[ tb3, max( tb1,tb2) ]= min[ 4.920 , max( 3.000 , 3.000 ) ]

= 3.0000 mm


= max( ta, tb )

= max( 1.8175 , 3.0000 )

= 3.0000 mm



MDMT of the Nozzle Neck to Flange Weld, Curve: B ----------------------------------------------------------------------






----------------------------------------------------------------------


























The Drop for this Nozzle is : 0.4789 mm The Cut Length for this Nozzle is, Drop + Ho + H + T : 2708.0002 mm





Nozzle Calcs. : M Nozl: 20 1:26p Aug 15,2014

I8P0T VAL0E", 8o99le Description: % 'rom : ()















Material SA-516 70











Flange Type Slip on






















This is a Manway or Access Opening.

Class of attached Flange 150Grade of attached Flange GR 1.1



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#einforcement CALC0LATI78, Description: %






= (P*R)/(S*E-0.6*P) per UG-27 (c)(1)

= (0.05*951.5001)/(137*1.00-0.6*0.05)

= 0.3451 mm



= (0.05*304.8000)/(137*1.00+0.4*0.05)

= 0.1105 mm







= min( 1, Sn/S )

= min( 1, 137.9/137.9 )

= 1.000


= min( 1, Sn/S )





= min( 1, 137.9/137.9 )

= 1.000


= min( 1, Sp/S )

= min( 1, 137.9/137.9 )= 1.000


= min( fr2, fr4 )

= min( 1.0 , 1.0 )

= 1.000






Area in Inward Nozzle A3 NA 0.000 NA mm^2Area in Welds A41+A42+A43 NA 85.000 NA mm^2

Area in Element A5 NA 1682.400 NA mm^2









"rea Required "!:


= 0.5(596.6000*4.9539*1+2*6.5000*4.9539*1*(1-1.00))

= 1477.754 mm^2




= 596.600 ( 1.00 * 6.5000 - 1.0 * 4.954 ) - 2 * 6.500

( 1.00 * 6.5000 - 1.0 * 4.9539 ) * ( 1 - 1.000 )

= 922.392 mm^2


= ( 2 * Tlwp ) * ( tn - trn ) * fr2

= ( 2 * 16.25 ) * ( 6.50 - 1.24 ) * 1.0000

= 170.899 mm^2



= 7.0000² *1.00 + (0.0000 )² *1.00 + 6.0000² * 1.00

= 85.000 mm^2







= ( 890.0000 - 609.6000 ) * 8.0000 * 1.0000

= 1682.400 mm^2




----------------------------------------------------------------------











----------------------------------------------------------------------






----------------------------------------------------------------------






----------------------------------------------------------------------























= 8.000 - 1.500

= 6.500 mm


= Di/2 + corrosion allowance= 1900.000/2 + 1.500

= 951.500 mm


Note : Pad Thk >= 0.5T and Pad Width >= 8(Shell Thk + Pad Thk)

= 8( t + te )

= 8( 6.500 + 8.000 )

= 116.000 mm


= t + 0.78 * sqrt( Rn * tn )

= 6.500 + 0.78 * sqrt( 298.300 * 6.500 )

= 40.846 mm


= Lpr1 + T

= 800.000 + 6.500

= 806.500 mm


= 8( t + te )

= 8( 6.500 + 8.000 )

= 116.000 mm



= min[ 40.846 , 806.500 , 116.000 )

= 40.846 mm


= t + te

= 6.500 + 8.000

= 14.500 mm



= min( 10, (596.60 + 6.500 )/( sqrt((1903.00 + 14.500 ) * 14.500 )) )





= 3.617



= t * LR * max( Lamda/4, 1 )= 6.500 * 116.000 * max( 3.617/4, 1 )

= 754.000 mm^2


= tn * LH

= 6.500 * 40.846

= 265.500 mm^2


= 0.5 * Leg412

= 0.5 * 7.0002

= 24.500 mm^2



= min( 140.200 * 8.000 , 116.000 * 8.000 )

= 928.000 mm^2


= A1 + frn( A2 + A3 ) + A41 + A42 + A43 + frp( A5 )

= 754.000+1.000(265.500+0.000)+24.500+0.000+0.000+1.000(928.000)

= 1972.000 mm^2


= 1.5 * S * E

= 1.5 * 137.900 * 1.000

= 206.9 MPa


= P * Rn( LH - t )

= 0.050 * 298.300 ( 40.846 - 6.500 )

= 512.2 N


= P * Reff * ( LR + tn )

= 0.050 * 951.500 * ( 116.000 + 6.500 )

= 5827.4 N


= P * Reff * Rnc

= 0.050 * 951.500 * 298.300

= 14190.4 N



= 298.300 ( 40.846 - 6.500 ) + 951.500 ( 116.000 + 6.500 + 298.300 )

= 410636.7 mm^2







= 206.850/( 2 * 410636.688/1972.000 - 951.500/14.500 )

= 0.6 MPa


= S[t/Reff]

= 137.900 [6.500/951.500 ]= 0.9 MPa



= min( 0.590 , 0.942 )

= 0.590 MPa


= ( fN + fS + fY ) / AT

= ( 512.229 + 5827.442 + 14190.418 )/1972.000

= 10.412 MPa

General Primary Membrane Stress [SigmaCirc]: = P * Reff / teff

= 0.050 * 951.500/14.500

= 3.3 MPa



= max( 2 * 10.412 - 3.281 , 3.281 )

= 17.5 MPa








= ( 298.300 + 6.500 )/298.300



= pi/2 * ( Rn + tn )

= pi/2 * ( 298.300 + 6.500 )

= 478.779 mm


= pi/2 * ( Rn + tn + W )

= pi/2 * ( 298.300 + 6.500 + 140.200 )

= 699.004 mm


= 4.950, 4.243, 0.000, mm



= min(14190*1.02,1.5*137.9(265.500+0.000),pi/4*0.1*298.30^2*1.02^2)





= 3647.984 N


= fwelds * t * S/( t * S + te * Sp )

= 3648.0*6.50*137/(6.500*137+8.000*137)

= 1635.303 N



= 3648.0*8.00*137/(6.500*137+8.000*137)

= 2012.681 N


= fws / ( Ltau * ( 0.6 * tw1 + 0.49 * L43T ) )

= 1635.303/( 478.779 * ( 0.6 * 6.500 + 0.49 * 0.000 ) )

= 0.876 MPa


= fwp / ( Ltau * ( 0.6 * tw2 + 0.49 * L41T ) )= 2012.681/( 478.779 * ( 0.6 * 8.000 + 0.49 * 4.950 ) )

= 0.582 MPa


= fwp / ( Ltau * ( 0.49 * L42T ) )

= 2012.681/( 699.004 * ( 0.49 * 4.243 ) )

= 1.385 MPa



= max( 0.876 , 0.582 , 1.385 )


(eld Si*e 'alculations& 8escri%tion: M
















Nozzle Schedule : Step: 18 1:26p Aug 15,2014

8o99le "chedule:

Nominal Flange Noz. Wall Re-Pad Cut

Description Size Sch/Type O/Dia Thk ODia Thick Length

in. Cls in. mm mm mm mm------------------------------------------------------------------------------

N1 2.000 80 SlipOn 2.375 5.537 - - 2708.00

N13 2.000 80 SlipOn 2.375 5.537 - - 2708.00

N4 3.000 80 SlipOn 3.500 7.620 150.00 8.000 2708.00

N5 3.000 80 SlipOn 3.500 7.620 150.00 8.000 2708.00

N6 4.000 80 SlipOn 4.500 8.560 200.00 8.000 809.72

N11 8.000 40 SlipOn 8.625 8.179 410.00 8.000 814.34

N12 8.000 40 SlipOn 8.625 8.179 410.00 8.000 814.34

N2 20.000 150 SlipOn 20.000 8.000 700.00 8.000 842.59

N3 20.000 150 SlipOn 20.000 8.000 700.00 8.000 842.59

M 24.000 150 SlipOn 24.000 8.000 890.00 8.000 858.22

General Notes for the above table:

The Cut Length is the Outside Projection + Inside Projection + Drop +

In Plane Shell Thickness. This value does not include weld gaps,

nor does it account for shrinkage.

In the case of Oblique Nozzles, the Outside Diameter must

be increased. The Re-Pad WIDTH around the nozzle is calculated as follows:

Width of Pad = (Pad Outside Dia. (per above) - Nozzle Outside Dia.)/2

For hub nozzles, the thickness and diameter shown are those of the smaller

and thinner section.

8o99le %aterial and &eld 'illet Leg "i9e Details:

Shl Grve Noz Shl/Pad Pad OD Pad Grve Inside

Nozzle Material Weld Weld Weld Weld Weld

mm mm mm mm mm

------------------------------------------------------------------------------

N1 SA-106 B 8.000 6.000 - - -

N13 SA-106 B 8.000 6.000 - - -

N4 SA-106 B 8.000 7.000 6.000 6.000 -

N5 SA-106 B 8.000 7.000 6.000 6.000 -

N6 SA-106 B 8.000 7.000 6.000 6.000 -

N11 SA-106 B 8.000 7.000 6.000 6.000 -

N12 SA-106 B 8.000 7.000 6.000 6.000 -

N2 SA-516 70 8.000 7.000 6.000 8.000 -

N3 SA-516 70 8.000 7.000 6.000 8.000 -

M SA-516 70 8.000 7.000 6.000 8.000 -

Note: The Outside projections below do not include the flange thickness.

Nozzle Miscellaneous Data:

Elevation/Distance Layout Projection Installed In

Nozzle From Datum Angle Outside Inside Component

mm deg. mm mm

----------------------------------------------------------------------------

N1 160.000 90.00 800.00 1900.00 shell




Nozzle Schedule : Step: 18 1:26p Aug 15,2014

N13 3640.000 90.00 800.00 1900.00 shell

N4 1880.000 90.00 800.00 1900.00 shell

N5 2120.000 90.00 800.00 1900.00 shell

N6 2380.000 90.00 800.00 0.00 shell

N11 2720.000 90.00 800.00 0.00 shell

N12 3120.000 90.00 800.00 0.00 shellN2 640.000 90.00 800.00 0.00 shell

N3 1390.000 90.00 800.00 0.00 shell

M 3910.000 90.00 800.00 0.00 shell

&eld "i9es for "lip 7n 8o99le 'langes per 0&+(-:

Nozzle to Flange Fillet Weld Leg dimension [xmin]:

= min( 0.7 * Hub Thickness, Nozzle Thickness-Corrosion )/0.7 for Socket Welds

= min( 1.4 * tmin, Hub Thickness ) / 0.7 for Slip on Flanges.

The Nozzle Wall thicknesses shown below are in the corroded condition. Hubs

are considered to be straight.

Nominal Flange Noz. Wall Hub Throat xmin

Description Size Sch/Type O/Dia Thk -------- Thickness

in. Cls in. mm mm mm mm

------------------------------------------------------------------------------

N1 2.000 80 SlipOn 2.375 4.037 7.874 3.956 5.652

N13 2.000 80 SlipOn 2.375 4.037 7.874 3.956 5.652

N4 3.000 80 SlipOn 3.500 6.120 8.636 5.998 8.568

N5 3.000 80 SlipOn 3.500 6.120 8.636 5.998 8.568

N6 4.000 80 SlipOn 4.500 7.060 9.398 6.579 9.398

N11 8.000 40 SlipOn 8.625 6.679 11.938 6.545 9.350

N12 8.000 40 SlipOn 8.625 6.679 11.938 6.545 9.350

N2 20.000 150 SlipOn 20.000 6.500 22.860 6.370 9.100

N3 20.000 150 SlipOn 20.000 6.500 22.860 6.370 9.100

M 24.000 150 SlipOn 24.000 6.500 23.749 6.370 9.100




tr Corroded Roof plate thickness

h Height of liquid in tankG Density of fluid stored

Ph Pressure due to liquid head = G*g*HPi Internal PressureP q = Design pressure = Ph + Pi

End Plate aterial

Sy !ield stress of end plate

Sa "llo#a$le $ending stress = %&'' *(y

a a)& nsupported length of plateb in& unsupported length of plateE odulus of Elasticitya/b Ratio of a$ 4

α ,actor $ased on a$

β ,actor $ased on a$

σr max Maximum Radial stress in plates =β*q*b²/tr²

Ymax -ertical deflection of plate = α*q*b^4/(E*tr^3)

ya "llo#a$le plate defection = tr.

/01%% 22

/

3%&% kPa

E4D P5"6E DE(IG4

%&%'1 Pa

DE(IG4 D"6"

7&3% 22

"8I DIE,5EC6I94 9, P5"6E

0.1400

:&% 22

As σr max < σa, Provided End plate thickness is ok.

/7&': kPa

"8I R"DI"5 (6RE(( I4 P5"6E(

:;3 22/1;0''; Pa

0.7410

/&1 2

Reference : Case 1,Table 11. ,Chapter 11,!lat paltes,Roark !orm"las for #tress$#train,%th Edition

As & 'max <&a, Provided roof plate thickness is ok.

.3% Pa/'3 Pa

:&< 22

'7&': kPa

I( .%'. Gr&

/31 Pa



AS PER, IS 1893 (PART 1 ) : 2002, INDIAN STANDARD CRITERIA FOR EARTHQUAKE

RESISTANT DESIGN OF STRUCTURES.

PART 1 GENERAL PROVISION AND BUILDINGS.

SEISMIC ZONE : 3 ( AS PER FIG - 1 )

Z = ZONE FACTOR

= 0.16

I = IMPORTANCE FACTOR

= 2

R = RESPONSE REDUCTION FACTOR

= 4

Sa / g = AVERAGE RESPONSE ACCELERATION COEFFICIENT

= 2.5

Ah = DESIGN HORIZONTAL SEISMIC COEFFICIENT

= Z I Sa

2 R g

Ah = 0.10

Wo = MAX.OPERATING WEIGHT OF VESSEL

= 16200 kg

SEISMIC FORCE AT BASE

VB = Ah * Wo

= 1620 kg

SEISMIC LOAD CALCULATIONS





SHELL ID 1900 mm

SHELL LENGTH 4500 mm

SHELL THK 8 mm

HEAD THK 10 mm

BOOT SHELL OD 0 mm

BOOT SHELL LENGTH 0 mm

NUMBER OF BOOTS 1

CORRODED EMPTY WT OF VESSEL (Wv !450"0 kg

BOLT SI#E M$4

BOLT CORROSION ALLOWANCE 1"% mm

CORRODED ROOT AREA OF BOLT& A' !"01$8 cm2

NO" OF BOLTS& N 4

ENTER TENSILE STRESS OF THE OLT 15!0 kg!cm2ENTER SHEAR STRESS OF THE OLT 10$0 kg!cm2

NO##LE DATA

MARKM

N$)

N!

N4)

N5N%

N11)

N1$

N1)

N1!*TY 1 $ $ 1 $ $

OD %10 508 88"9 114"! $19"08 %0"!!

LENGTH 500 500 500 500 500 500

VOLUME(M! OF NO##LES + A 0"15 0"$0 0"01 0"01 0"04 0"00 0"40

VOLUME OF VESSEL + 14"8 M!

VOLUME OF BOOT + C 0"0 M!

TOTAL VOLUME OF VESSEL& " , A--C 15 M!

WATER FORCE& #$ , " % 1000 15$$8 KG

NET UPLIFT FORCE& &' , #$ + #( 118 KG

UPLIFT FORCE CONSIDERING 10. E/TRA&

&') 1$9%0 KG

SEISMIC SHEAR STRESS& F* 1%$0 KG

UPLIFT FORCE CALCULATION

TOTAL

Is Compliance

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