ASME BPVC VIII Example E E PTB
|
|
- Gervais Timothy Elliott
- 5 years ago
- Views:
Transcription
1 Table of contents Comparison - Form for equations... 2 Example E Integral Type... 3 E Bolted flanges ASME BPVC VIII DIVISION 1 APP. 2, 2017 Edition... 5 Example E Loose Type... 7 E Bolted flanges ASME BPVC VIII DIVISION 1 APP. 2, 2017 Edition... 9 Appendix: Material documentation Layout Input values: or Calculated values: or Critical values: or Estimated values: or Lauterbach Verfahrenstechnik GmbH
2 Comparison - Form for equations Equation form Comment Results for example E acc. ASME and Lauterbach Verfahrenstechnik GmbH (LV) The LV-program uses formulas for Bolted flanges acc. VIII-1, App.2. Equations Conversion factor mm2 = N2lbf = 'Results Ex. E LV and ASME Required load W acc. LV W1 = #23(1)*N2lbf Required load W ASME W1Asme = Difference % Diff1 = (W1Asme-W1)/W1Asme*100 'Results Ex. E LV and ASME Required load W acc. LV W2 = #23(2)*N2lbf Required load W ASME W2Asme = Difference % Diff2 = (W2Asme-W2)/W2Asme*100 'Maximum difference between LV and ASME Dmax = Max( Diff1 ; Diff2 ) Value Lauterbach Verfahrenstechnik GmbH
3 Example E Integral Type Determe if the stresses the heat exchanger girth flange are with acceptable limits, considerg the followg design conditions. The flange is of an tegral type and is attached to a cyldrical shell with a Category C, Type 1 butt weld and has been 100% radiographically examed. See Figure E General Data: Cylder Material = SA-516, Grade 70 Design Conditions = 135 F Allowable Stress at Design Temperature = psi Allowable Stress at Ambient Temperature = psi Corrosion Allowance = Flange Data: Material = SA-105 Allowable Stress at Design Temperature = psi Allowable Stress at Ambient Temperature = psi Modulus of Elasticity at Design Temperature = 26.0E + 06 psi Modulus of Elasticity at Ambient Temperature = 29.4E +06 psi Bolt Data: Material = SA-193, Grade B7 Allowable Stress at Design Temperature = psi Allowable Stress at Ambient Temperature = psi Diameter = 0.75 Number of Bolts = 44 Root area = Gasket Data: Material = Flat Metal Jacketed (Iron/Soft Steel) Gasket Factor = 3.75 Seatg Stress = 7600 psi Inside Diameter = 29.0 Outside Diameter = 30.0 Lauterbach Verfahrenstechnik GmbH
4 Design rules for bolted flange connections with rg type gaskets are provided Vlll-1 Mandatory Appendix 2. The rules this paragraph are the same as those provided Vlll-2, paragraph However, there are differences to be noted, cludg; a step-by-step design procedure, nomenclature with regard to operatg and gasket seatg bolt loads, the clusion of a flange moment due to externally applied axial forces and bendg moment, and mor differences bolt pacg criteria. Therefore, while the example problem will be presented for use with Vlll-1, Appendix 2, references to Vlll-2 paragraphs will be provided, as applicable. Evaluate the girth flange accordance with Vlll-1, Appendix 2. Establish the design conditions and gasket reaction diameter, (VIII-2, paragraph ). Lauterbach Verfahrenstechnik GmbH
5 E Bolted flanges ASME BPVC VIII DIVISION 1 APP. 2, 2017 Edition Integral Type Flange Design data Design pressure Hydrostatic head Calculation pressure Calculation temperature Flange P D D P P MPa 0 MPa MPa = p D = D p = p T 0 bar psi psi F Outside diameter A Inside diameter B Bolt circle diameter C Pipe size Hub length h Flange thickness t B n Large hub thickness g Small hub thick. g Material K03504-SA-105--Class:-Size: Allowable operatg stress Allowable stallation stress Corrosion allowance Modulus of elasticity at operation Modulus of elasticity at test (20 C) S fb S fa c 2 E T E MPa MPa Gasket Gasket diameter Effective gasket width Gasket factor Gasket seatg load [Table: 2-5.2] [Table: 2-5.1] [Table: 2-5.1] G b m y Lauterbach Verfahrenstechnik GmbH
6 Bolts Number Root diameter Nomal diameter Material G41400-SA-193-B7-Class:-Size:<=64 Allowable operatg stress Allowable stallation stress Consider bolt factor B SC 2-6(7)? n d K a S b S a (N=No) Y (Y/N) Required operation bolt load Mimum itial bolt load Available cross section of bolts Required cross section Required cross section Eq.(1) Eq.(2) W m1 /S b W m2 /S a W m1 W m2 A b A m1 A m lbf lbf ² ² ² Req. bolt load for gasket seatg Allowable bolt load (A m +A b ) S a /2 A b S a W W all lbf lbf (5) Design (gasket seatg =1; max. allowable=2) 1 (1,2) Moment M D = H D h D M G = H G h G M T = H T h T = = = Force Lever arm = Result lbf = lbf ft lbf = 1389 lbf ft lbf = 2700 lbf ft Total operatg moment = M D + M G + M T = Total gasket seatg moment, Eq. (6) = W (C-G)/2 = M 01 M lbf ft lbf ft Stress Operation Installation Allowable Longitudal S H S f (8) Ratio S H /S f S f Allowable stress Radial S R S f (9) Tangential S T S f (10) Combation (S H +S R )/2 = S f Combation (S H +S T )/2 = S f B S B Smax Bolt pitch = (3) Remark Lauterbach Verfahrenstechnik GmbH
7 Auxiliary values (Fig ) (Fig ) (Fig ) (Fig ) (Fig ) (Fig ) (Fig ) Eq.(1) Eq.(2) Bolt pitch Lauterbach Verfahrenstechnik GmbH
8 (3) For (7) KI (=0.3 acc. Table 2-14) = 0.3 J = V [M 01 or M 02 ]/L/[E or E 20C ]/(g 0 -c 2 )²/K L /h 0 = [ 2.333e+7 or 2.344e+7 ]/ /[ or ]/( )²/ 0.3 / Rigidity criterion: J Lauterbach Verfahrenstechnik GmbH
9 Example E Loose Type Determe if the stresses the ASME B16.5, Class 300, NPS 20 Slip-on Flange are with acceptable limits, considerg the followg design conditions. The flange is of a loose type with hub and is attached to a cyldrical shell with Category C fillet welds, see Vlll-1 Appendix 2, Figure 2-4 Sketch 3. General Data Cylder Material = SA-516, Grade 70 Design Conditions = 450 psig@650 F Allowable Stress at Design Temperature = psi Allowable Stress at Ambient Temperature = psi Corrosion Allowance = 0.0 Flange Data: Material = SA-105 Allowable Stress at Design Temperature = psi Allowable Stress at Ambient Temperature = psi Modulus of Elasticity at Design Temperature = 26.0E + 06 psi Modulus of Elasticity at Ambient Temperature = 29.4E +06 psi Bolt Data: Material = SA -193, Grade B7 Allowable Stress at Design Temperature = psi Allowable Stress at Ambient Temperature = psi Diameter = 1.25 Number of Bolts = 24 Root area = Gasket Data Material = Kammprofile Gasket Factor = 2.0 Seatg Stress = 2500 psi Inside Diameter = Outside Diameter = Lauterbach Verfahrenstechnik GmbH
10 Design rules for bolted flange connections with rg type gaskets are provided Vlll-1 Mandatory Appendix 2. The rules this paragraph are the same as those provided Vlll-2, paragraph However, there are differences to be noted, cludg; a step-by-step design procedure, nomenclature with regard to operatg and gasket seatg bolt loads, the clusion of a flange moment due to externally applied axial forces and bendg moment, and mor differences bolt spacg criteria. Therefore, while the example problem will be presented for use with Vlll-1, Appendix 2, references to Vlll-2 paragraphs will be provided, as applicable. Evaluate the flange accordance with Vlll-1, Appendix 2. Establish the design conditions and gasket seatg reaction diameter, (VIII-2, paragraph ). Lauterbach Verfahrenstechnik GmbH
11 E Bolted flanges ASME BPVC VIII DIVISION 1 APP. 2, 2017 Edition Loose Type Flange With Full Neck Design data Design pressure Hydrostatic head Calculation pressure Calculation temperature Flange P D MPa = p D D P 0 MPa = D p 0 P MPa = p T 0 bar bar bar C Outside diameter A mm Inside diameter B Bolt circle diameter C mm Pipe size B n 20.2 Hub length h mm Flange thickness t mm mm Large hub thickness g mm Small hub g thickness mm Material K03504-SA-105--Class:-Size: Allowable operatg stress Allowable stallation stress Corrosion allowance Modulus of elasticity at operation Modulus of elasticity at test (20 C) S fb S fa c 2 E T E mm MPa MPa Gasket Gasket diameter Effective gasket width Gasket factor Gasket seatg load [Table: 2-5.2] [Table: 2-5.1] [Table: 2-5.1] G b m y mm mm Lauterbach Verfahrenstechnik GmbH
12 Bolts Number Root diameter Nomal diameter Material G41400-SA-193-B7-Class:-Size:<=64 Allowable operatg stress Allowable stallation stress Consider bolt factor B SC 2-6(7)? Required operation bolt load Eq.(1) Mimum itial bolt load Eq.(2) Available cross section of bolts Required cross section W m1 /S b Required cross section W m2 /S a n d K a S b S a (N=No) W m1 W m2 A b A m1 A m2 Y mm mm (Y/N) N N mm² mm² mm² Req. bolt load for gasket seatg Allowable bolt load (A m +A b ) S a /2 A b S a W W all N N (5) Design (gasket seatg =1; max. allowable=2) 1 (1,2) Moment M D = H D h D M G = H G h G M T = H T h T = = = Force Lever arm = Result N mm = 5.537e+7 Nmm N mm = 1.209e+7 Nmm N mm = Nmm Total operatg moment = M D + M G + M T = Total gasket seatg moment, Eq. (6) = W (C-G)/2 = M 01 M e e+8 Nmm Nmm Stress Operation Installation Allowable Longitudal S H S f (8) Ratio S H /S f S f Allowable stress Radial S R S f (9) Tangential S T S f (10) Combation (S H +S R )/2 = S f Combation (S H +S T )/2 = S f B S B Smax Bolt pitch mm mm = (3) Remark Lauterbach Verfahrenstechnik GmbH
13 Auxiliary values (Fig ) (Fig ) (Fig ) (Fig ) (Fig ) (Fig ) Eq.(1) Eq.(2) Bolt pitch (3) Lauterbach Verfahrenstechnik GmbH
14 For (7) KL (=0.2 acc. Table 2-14) = 0.2 J = V [M 01 or M 02 ]/L/[E or E 20C ]/(g 0 -c 2 )²/K L /h 0 = [ 7.714e+7 or 1.046e+8 ]/ / /[ or ]/( )²/ 0.2 / Rigidity criterion: J Lauterbach Verfahrenstechnik GmbH
15 Appendix: Material documentation Section 2: Flansch/AFL Section 3: Flansch/AFL Material specification: Regulation: ASMET1A:2015Spec. No.: SA-105 Product: Forggs Material code: K03504-SA-105--Class:-Size: Short name: Carbon steel Design conditions and dimensions: Temperature [ C]: 343,3333 Pressure [bar]: 9,31 Thickness [mm]: 2 Outside diameter [mm]: 0 Material values for test and design conditions: Test condition Operatg condition Nomal design strength []: 138,00 122,80 Safety factor: 1,00 1,00 Allowable stress []: 138,00 122,80 Modulus of elasticity [k]: ,6667 Notes: G10 General Requirements Upon prolonged exposure to temperatures above 425 C, the carbide phase of carbon steel may be converted to graphite. See Nonmandatory Appendix A, A 201 and A 202. S1 Size Requirements For Section I applications, stress values at temperatures of 450 C and above are permissible but, except for tubular products 75 mm O.D. or less enclosed with the boiler settg, use of these materials at these temperatures is not current practice. T2 Time-Dependent Properties Allowable stresses for temperatures of 400 C and above are values obtaed from time dependent properties. -- Creep rupture strength for h [MPa]: Tensile strength and yield stress at ambient temperature: Diam./ Tensile str. ReH Rupture Rupture Thick. Rm m Rm max elong. elong <= mm MPa MPa MPa längs % quer % K-values as function of the temperature Diam./ Thickn. 50 C 100 C 150 C 200 C 250 C 300 C 350 C 400 C <= mm MPa MPa MPa MPa MPa MPa MPa MPa K-values as function of the temperature Diam./ Thickn. 450 C 500 C 550 C 600 C 650 C 700 C 800 C <= mm MPa MPa MPa MPa MPa MPa MPa Lauterbach Verfahrenstechnik GmbH
16 Modulus of elasticity dependence of the temperature: Static modulus of elasticity [k] at the temperature of Coefficient of lear expansion: Thermal coefficient of expansion between 20 C and Density 100 C 200 C 300 C 400 C 500 C 600 C 700 C 800 C Heat Heat (20 C) cond. capac. kg/dm³ 10E-6/K 10E-6/K 10E-6/K 10E-6/K 10E-6/K 10E-6/K 10E-6/K 10E-6/K W/Km J/kgK ,85 12,1 12,7 13,3 13,8 14, Section 2: Schraube/AFL Section 3: Schraube/AFL Material specification: Regulation: ASMET3:2010Spec. No.: SA-193 Product: Boltg Material code: G41400-SA-193-B7-Class:-Size:<=64 Short name: 1Cr-0.2Mo Design conditions and dimensions: Temperature [ C]: 343,3333 Pressure [bar]: 9,30798 Thickness [mm]: 2 Outside diameter [mm]: 0 Material values for test and design conditions: Test condition Operatg condition Nomal design strength []: 172,00 172,00 Safety factor: 1,00 1,00 Allowable stress []: 172,00 172,00 Modulus of elasticity [k]: ,4 Notes: -- Creep rupture strength for h [MPa]: Tensile strength and yield stress at ambient temperature: Diam./ Tensile str. ReH Rupture Rupture Thick. Rm m Rm max elong. elong <= mm MPa MPa MPa längs % quer % K-values as function of the temperature Diam./ Thickn. 50 C 100 C 150 C 200 C 250 C 300 C 350 C 400 C <= mm MPa MPa MPa MPa MPa MPa MPa MPa K-values as function of the temperature Diam./ Thickn. 450 C 500 C 550 C 600 C 650 C 700 C 800 C <= mm MPa MPa MPa MPa MPa MPa MPa Lauterbach Verfahrenstechnik GmbH
17 Modulus of elasticity dependence of the temperature: Static modulus of elasticity [k] at the temperature of Static modulus of elasticity [k] at the temperature of Coefficient of lear expansion: Thermal coefficient of expansion between 20 C and Density 100 C 200 C 300 C 400 C 500 C 600 C 700 C 800 C Heat Heat (20 C) cond. capac. kg/dm³ 10E-6/K 10E-6/K 10E-6/K 10E-6/K 10E-6/K 10E-6/K 10E-6/K 10E-6/K W/Km J/kgK ,85 12,1 12,7 13,3 13,8 14, Lauterbach Verfahrenstechnik GmbH
ASME BPVC VIII Example E E4.3.8 PTB
ASME BPVC VIII-1 217 Example E4.3.7 - E4.3.8 PTB-4-213 Table of contents Comparison - Form for equations... 2 Example E4.3.7- Conical Transitions Without a Knuckle... 3 E4.3.7 Large End - Dished heads
More informationNote to reviewers: See next page for basis for the change shown on this page. L-3160 TANGENTIAL CONTACT BETWEEN FLANGES OUTSIDE THE BOLT CIRCLE
ASME BPVC.III.A-2017 ð17þ L-3160 TANGENTIAL CONTACT BETWEEN FLANGES OUTSIDE THE BOLT CIRCLE The design procedure is based on the assumption that the flanges are in tangential contact at their outside diameter
More informationItem No.: Sample Doc. No.: DESIGN METHOD - 0
ITEGRAL TYPE FLAGES UDER ITERAL PRESSURE internal design pressure P 0.590 MPa W m2 3.14bGy + b r r l y 470225.861 design temperature 82.000 C H p 2P(3.14bGm + b r r l m ) 115117.535 ambient temperature
More informationN = Shear stress / Shear strain
UNIT - I 1. What is meant by factor of safety? [A/M-15] It is the ratio between ultimate stress to the working stress. Factor of safety = Ultimate stress Permissible stress 2. Define Resilience. [A/M-15]
More informationLCLS-II 2K Cold Box Transfer Line Nozzle. Analysis and Allowable Loads
Author(s): Connor Kaufmann Page 1 of 12 LCLS-II 2K Cold Box Transfer Line Nozzle Analysis and Allowable Loads Revision History: Revision Date Released Description of Change - 01/03/2018 Original release,
More informationWTS Table of contents. Layout
Table of contents Thermal and hydraulic design of shell and tube heat exchangers... 2 Tube sheet data... 4 Properties of Water and Steam... 6 Properties of Water and Steam... 7 Heat transfer in pipe flow...
More informationSimplified Method for Mechanical Analysis of Safety Class 1 Piping
Simplified Method for Mechanical Analysis of Safety Class 1 Piping ZHANG Zheng-ming *, WANG Min-zhi, HE Shu-yan Division of Reactor Structure & Mechanics, Institute of Nuclear Energy Technology, Tsinghua
More informationC100 Cryomodule Vacuum Vessel Structural Analysis Gary G. Cheng, William R. Hicks, and Edward F. Daly
Introduction C100 Cryomodule Vacuum Vessel Structural Analysis Gary G. Cheng, William R. Hicks, and Edward F. Daly Cryomodule (CM) prototypes for CEBAF 12GeV upgrade project have been built in the past
More information3) Aft bolted connection analysis: (See Figure 1.0)
Given: Both static and dynamic (fatigue) failure criteria will be used. A mimum factor of safety =2 will be adhered to. For fatigue analysis the ASME elliptic model with Von Mises equivalent stress will
More informationMANDATORY APPENDIX 41 ELECTRIC IMMERSION HEATER ELEMENT SUPPORT PLATES
41-1 41-5 Page 1 of 5 No changes, age is included for reference. MANDATORY APPENDIX 41 ELECTRIC IMMERSION HEATER ELEMENT SUPPORT PLATES 41-1 SCOPE 41-3 41-1.1 The rules in this Mandatory Aendix cover the
More informationPart :Fill the following blanks (20 points)
Part :Fill the following blanks (20 points) 1. Among the impurity elements in carbon steel, ( ) are useful elements, ( ) are harmful elements. 2. The plastic properties of metal materials are ( ) and 3.
More informationDownloaded from Downloaded from / 1
PURWANCHAL UNIVERSITY III SEMESTER FINAL EXAMINATION-2002 LEVEL : B. E. (Civil) SUBJECT: BEG256CI, Strength of Material Full Marks: 80 TIME: 03:00 hrs Pass marks: 32 Candidates are required to give their
More informationMandatory Appendices
Mandatory Appendices MANDATORY APPENDICES A99 Appendix 1 Supplementary Design Formulas... 315 Appendix 2 Rules for Bolted Flange Connections With Ring Type Gaskets... 331 Appendix 3 Definitions... 351
More information90/10 COPPER NICKEL ALLOY EUCARO 10 OFFSHORE APPLICATIONS
0/ COPPER NICKEL ALLOY EUCARO OFFSHORE APPLICATIONS 2 W O R L D O F COPPER N I CK E L Eucaro TABLE OF CONTENTS Technical Information Page - Pipes Page Inner Flanges Page - Outer Flanges Page Solid Slip-On
More informationSafety Analysis of a Class 3 Component by ANSYS
Safety Analysis of a Class 3 Component by ANSYS D. L. Wang Department of Aerospace Engineering, Texas A & M Z. X. Tian Key Laboratory for Power Machinery and Engineering of Ministry Education Shanghai
More informationR13. II B. Tech I Semester Regular Examinations, Jan MECHANICS OF SOLIDS (Com. to ME, AME, AE, MTE) PART-A
SET - 1 II B. Tech I Semester Regular Examinations, Jan - 2015 MECHANICS OF SOLIDS (Com. to ME, AME, AE, MTE) Time: 3 hours Max. Marks: 70 Note: 1. Question Paper consists of two parts (Part-A and Part-B)
More informationName :. Roll No. :... Invigilator s Signature :.. CS/B.TECH (CE-NEW)/SEM-3/CE-301/ SOLID MECHANICS
Name :. Roll No. :..... Invigilator s Signature :.. 2011 SOLID MECHANICS Time Allotted : 3 Hours Full Marks : 70 The figures in the margin indicate full marks. Candidates are required to give their answers
More informationExample 4: Design of a Rigid Column Bracket (Bolted)
Worked Example 4: Design of a Rigid Column Bracket (Bolted) Example 4: Design of a Rigid Column Bracket (Bolted) Page : 1 Example 4: Design of a Rigid Column Bracket (Bolted) Determine the size of the
More information2012 MECHANICS OF SOLIDS
R10 SET - 1 II B.Tech II Semester, Regular Examinations, April 2012 MECHANICS OF SOLIDS (Com. to ME, AME, MM) Time: 3 hours Max. Marks: 75 Answer any FIVE Questions All Questions carry Equal Marks ~~~~~~~~~~~~~~~~~~~~~~
More informationStress Analysis Lecture 3 ME 276 Spring Dr./ Ahmed Mohamed Nagib Elmekawy
Stress Analysis Lecture 3 ME 276 Spring 2017-2018 Dr./ Ahmed Mohamed Nagib Elmekawy Axial Stress 2 Beam under the action of two tensile forces 3 Beam under the action of two tensile forces 4 Shear Stress
More informationPlease review the following statement: I certify that I have not given unauthorized aid nor have I received aid in the completion of this exam.
Please review the followg statement: I certify that I have not given unauthorized aid nor have I received aid the completion of this eam. Signature: INSTRUCTIONS Beg each problem the space provided on
More informationASTRA EVANGELISTA S.A.
(1) STR EVNGELIST S.. PLNT CNNING COMPRESS Pressure Vessel Design Calculations Vessel No: Customer: FIUB Contract: Designer: HRI/SEG Date: lunes, agosto 09, 2004 1 / 33 Table Of Contents1) Table Of Contents
More informationUNIT I SIMPLE STRESSES AND STRAINS
Subject with Code : SM-1(15A01303) Year & Sem: II-B.Tech & I-Sem SIDDHARTH GROUP OF INSTITUTIONS :: PUTTUR Siddharth Nagar, Narayanavanam Road 517583 QUESTION BANK (DESCRIPTIVE) UNIT I SIMPLE STRESSES
More informationReview of the Master SN Neuber Rule in the ASME Division 2 Rewrite Project
Review of the Master SN Neuber Rule in the ASME Division 2 Rewrite Project ASME BPVC Code Week Atlanta, GA February 2007 Chris Hinnant Paulin Research Group Houston, TX Table of Contents 1.0 Introduction
More informationCOLUMNS: BUCKLING (DIFFERENT ENDS)
COLUMNS: BUCKLING (DIFFERENT ENDS) Buckling of Long Straight Columns Example 4 Slide No. 1 A simple pin-connected truss is loaded and supported as shown in Fig. 1. All members of the truss are WT10 43
More informationDesign Calculations. CTC My Address My City. Revision : 16/02/10. Example B102
Revision : 16/2/1 2 16/2/1 1 6/11/9 Rev. Date Description Aut. Chk. App. QA Job Tag : Description : Job Name : Drawing No : Vessel Tag : Bentley AutoPIPE Vessel (Microprotol) procal V33.3..2 1 prodia2
More informationCIV 207 Winter For practice
CIV 07 Winter 009 Assignment #10 Friday, March 0 th Complete the first three questions. Submit your work to Box #5 on the th floor of the MacDonald building by 1 noon on Tuesday March 31 st. No late submissions
More informationAPPENDIX 2 RULES FOR BOLTED FLANGE CONNECTIONS WITH RING TYPE GASKETS
APPEDIX RULES FOR BOLTED FLAGE COECTIOS WITH RIG TYPE GASKETS -1 SCOPE GEERAL (a) The rules in Appendix apply specifically to the design of bolted flange connections with gaskets that are entirely within
More informationYour Company Name Here
Your Company Name Here Your Address Here COMPRESS Pressure Vessel Calculations Rev 1 Contact: Engineer's Name Here Item: Example Amine Absorber Drawing No: 12345-1 Rev 3 Customer: Size: 114"ID x 57'-0"
More information2.1 Background of Piping Stresses
2 Research Review One of the major additions to Tmin was the inclusion of analysis of a 2-Dimensional vertical piping span. The original plan from Dupont was to include several types of 2-D and 3-D vertical
More informationMechanical Engineering Ph.D. Preliminary Qualifying Examination Solid Mechanics February 25, 2002
student personal identification (ID) number on each sheet. Do not write your name on any sheet. #1. A homogeneous, isotropic, linear elastic bar has rectangular cross sectional area A, modulus of elasticity
More informationPressure Vessel Engineering Ltd. ASME Calculation CRN Services Finite Element Analysis Solid Modeling & Drafting
Pressure Vessel Engineering Ltd. ASME Calculation CRN Services Finite Element Analysis Solid Modeling & Drafting Design Conditions: Cust: Pressure Vessel Engineering Ltd. Code: ASME VIII-2 File: PVEfea-9128-1.0
More informationFEA A Guide to Good Practice. What to expect when you re expecting FEA A guide to good practice
FEA A Guide to Good Practice What to expect when you re expecting FEA A guide to good practice 1. Background Finite Element Analysis (FEA) has transformed design procedures for engineers. Allowing more
More informationTuesday, February 11, Chapter 3. Load and Stress Analysis. Dr. Mohammad Suliman Abuhaiba, PE
1 Chapter 3 Load and Stress Analysis 2 Chapter Outline Equilibrium & Free-Body Diagrams Shear Force and Bending Moments in Beams Singularity Functions Stress Cartesian Stress Components Mohr s Circle for
More informationFor more Stuffs Visit Owner: N.Rajeev. R07
Code.No: 43034 R07 SET-1 JAWAHARLAL NEHRU TECHNOLOGICAL UNIVERSITY HYDERABAD II.B.TECH - I SEMESTER REGULAR EXAMINATIONS NOVEMBER, 2009 FOUNDATION OF SOLID MECHANICS (AERONAUTICAL ENGINEERING) Time: 3hours
More informationIBV Series C Carbon Steel Inverted Bucket Vertical Steam Trap
Local regulations may restrict the use of this product to below the conditions quoted. In the interests of development and improvement of the product, we reserve the right to change the specification without
More informationIBV Series Z Alloy Steel Inverted Bucket Vertical Steam Trap
Local regulations may restrict the use of this product to below the conditions quoted. In the interests of development and improvement of the product, we reserve the right to change the specification without
More informationmy!wind Ltd 5 kw wind turbine Static Stability Specification
my!wind Ltd 5 kw wind turbine Static Stability Specification 1 P a g e 0 3 / 0 4 / 2 0 1 4 Contents Contents... 2 List of Changes... 2 Appendixes... 2 General remarks... 3 1. Introduction... 4 2. Geometry...
More informationTension zone applications, i.e., cable trays and strut, pipe supports, fire sprinklers Seismic and wind loading
General Information Mechanical Anchors General Information Power-Stud + SD1 Wedge Expansion Anchor Product Description The Power-Stud+ SD1 anchor is a fully threaded, torque-controlled, wedge expansion
More informationSteel Post Load Analysis
Steel Post Load Analysis Scope The steel posts in 73019022, 73019024, and 73019025, are considered to be traditional building products. According to the 2015 International Building Code, this type of product
More informationRODS: THERMAL STRESS AND STRESS CONCENTRATION
RODS: HERML SRESS ND SRESS CONCENRION Example 5 rod of length L, cross-sectional area, and modulus of elasticity E, has been placed inside a tube of the same length L, but of cross-sectional area and modulus
More informationApplication nr. 7 (Connections) Strength of bolted connections to EN (Eurocode 3, Part 1.8)
Application nr. 7 (Connections) Strength of bolted connections to EN 1993-1-8 (Eurocode 3, Part 1.8) PART 1: Bolted shear connection (Category A bearing type, to EN1993-1-8) Structural element Tension
More informationPES Institute of Technology
PES Institute of Technology Bangalore south campus, Bangalore-5460100 Department of Mechanical Engineering Faculty name : Madhu M Date: 29/06/2012 SEM : 3 rd A SEC Subject : MECHANICS OF MATERIALS Subject
More informationCIVIL DEPARTMENT MECHANICS OF STRUCTURES- ASSIGNMENT NO 1. Brach: CE YEAR:
MECHANICS OF STRUCTURES- ASSIGNMENT NO 1 SEMESTER: V 1) Find the least moment of Inertia about the centroidal axes X-X and Y-Y of an unequal angle section 125 mm 75 mm 10 mm as shown in figure 2) Determine
More informationMechanics of Materials Primer
Mechanics of Materials rimer Notation: A = area (net = with holes, bearing = in contact, etc...) b = total width of material at a horizontal section d = diameter of a hole D = symbol for diameter E = modulus
More informationC100 Cryomodule Vacuum Vessel Structural Analysis An Addendum to JLAB-TN
Introduction C100 Cryomodule Vacuum Vessel Structural Analysis An Addendum to JLAB-TN-07-081 Gary G. Cheng and Edward F. Daly The C100 cryomodule (CM) vacuum vessel structural analysis per ASME Boiler
More informationKey Design Engineering
Key Design Engineering 194-55 Northfield Dr. East Waterloo, ON N2K 3T6 COMPRESS Pressure Vessel Design Calculations Item: Sample Calculation: 36" ir Receiver Customer: BC Industries Job: KEY-Design-ir
More information3 Hours/100 Marks Seat No.
*17304* 17304 14115 3 Hours/100 Marks Seat No. Instructions : (1) All questions are compulsory. (2) Illustrate your answers with neat sketches wherever necessary. (3) Figures to the right indicate full
More informationStrength of Material. Shear Strain. Dr. Attaullah Shah
Strength of Material Shear Strain Dr. Attaullah Shah Shear Strain TRIAXIAL DEFORMATION Poisson's Ratio Relationship Between E, G, and ν BIAXIAL DEFORMATION Bulk Modulus of Elasticity or Modulus of Volume
More informationISHIK UNIVERSITY DEPARTMENT OF MECHATRONICS ENGINEERING
ISHIK UNIVERSITY DEPARTMENT OF MECHATRONICS ENGINEERING QUESTION BANK FOR THE MECHANICS OF MATERIALS-I 1. A rod 150 cm long and of diameter 2.0 cm is subjected to an axial pull of 20 kn. If the modulus
More informationSolid Mechanics Homework Answers
Name: Date: Solid Mechanics Homework nswers Please show all of your work, including which equations you are using, and circle your final answer. Be sure to include the units in your answers. 1. The yield
More informationStress Analysis of Radial and Non- Radial Nozzle Connections in Ellipsoidal Head Pressure Vessel
Journal of Mechanical Engineering Vol. 10, No. 1, 67-83, 2013 Stress Analysis of Radial and Non- Radial Nozzle Connections in Ellipsoidal Head Pressure Vessel Haszeme Abu Kasim 1, a Professor Dr. Ir. Wahyu
More informationPERIYAR CENTENARY POLYTECHNIC COLLEGE PERIYAR NAGAR - VALLAM THANJAVUR. DEPARTMENT OF MECHANICAL ENGINEERING QUESTION BANK
PERIYAR CENTENARY POLYTECHNIC COLLEGE PERIYAR NAGAR - VALLAM - 613 403 - THANJAVUR. DEPARTMENT OF MECHANICAL ENGINEERING QUESTION BANK Sub : Strength of Materials Year / Sem: II / III Sub Code : MEB 310
More informationPVP BUTANE STORAGE BULLET CALCULATION AND FEA VERIFICATION
Proceedings of PVP2005 2005 ASME Pressure Vessels and Piping Division Conference July 17-21, 2005, Denver, Colorado USA PVP2005-71123 BUTANE STORAGE BULLET CALCULATION AND FEA VERIFICATION Zhanghai Wang
More informationImpact and Fracture Mechanics Assessment of a Fused Silica Window
Arnold AFB Wind Tunnel Impact and Fracture Mechanics Analysis Rev-0 1 of 41 Impact and Fracture Mechanics Assessment of a Fused Silica Window Objective: Determine the survival probability of a fused silica
More informationDESIGN OF A SHELL AND TUBE HEAT EXCHANGER
DESIGN OF A SHELL AND TUBE HEAT EXCHANGER Swarnotpal Kashyap Department of Chemical Engineering, IIT Guwahati, Assam, India 781039 ABSTRACT Often, in process industries the feed stream has to be preheated
More informationEMA 3702 Mechanics & Materials Science (Mechanics of Materials) Chapter 3 Torsion
EMA 3702 Mechanics & Materials Science (Mechanics of Materials) Chapter 3 Torsion Introduction Stress and strain in components subjected to torque T Circular Cross-section shape Material Shaft design Non-circular
More informationQUESTION BANK SEMESTER: III SUBJECT NAME: MECHANICS OF SOLIDS
QUESTION BANK SEMESTER: III SUBJECT NAME: MECHANICS OF SOLIDS UNIT 1- STRESS AND STRAIN PART A (2 Marks) 1. Define longitudinal strain and lateral strain. 2. State Hooke s law. 3. Define modular ratio,
More informationCHAPTER 6: ULTIMATE LIMIT STATE
CHAPTER 6: ULTIMATE LIMIT STATE 6.1 GENERAL It shall be in accordance with JSCE Standard Specification (Design), 6.1. The collapse mechanism in statically indeterminate structures shall not be considered.
More informationAluminum shell. Brass core. 40 in
PROBLEM #1 (22 points) A solid brass core is connected to a hollow rod made of aluminum. Both are attached at each end to a rigid plate as shown in Fig. 1. The moduli of aluminum and brass are EA=11,000
More informationInitial Stress Calculations
Initial Stress Calculations The following are the initial hand stress calculations conducted during the early stages of the design process. Therefore, some of the material properties as well as dimensions
More informationdb = 23.7 in B C D 96 k bf = 8.97 in tf = in k = 1.09 in 13 Fy = 50 ksi Fu = 65 ksi Member A-B, Interior column: A E
le B1, second floor. t = thickness of connected part Pu = factored load to be resisted d = diameter of the bolt eb = one-half the depth of the beam, ec = one-half the depth of the column, Hub = factored
More informationMathematical Modeling of Families of Charts 12/18/02
Mathematical Modelg of Families of Charts /8/0 K Solver is used to computerize stress calculations volvg spherical shells with radial loads on nozzle connections. Bullet 07 from the Weldg Research Council
More informationCO~RSEOUTL..INE. revisedjune 1981 by G. Frech. of..a.pqij~t(..~ttsa.fidteconol.q.gy. Sault ",Ste'...:M~ri,e.: SAUl. ir.ft\,nl~t';~l' G ". E b:.
-/ 1/ /.. SAUl. ir.ft\,nl~t';~l' G ". E b:.~~~~~, of..a.pqij~t(..~ttsa.fidteconol.q.gy. Sault ",Ste'...:M~ri,e.: ',' -.\'~. ~ ;:T.., CO~RSEOUTL..INE ARCHITECTURAL ENGINEERING II ARC 200-4 revisedjune 1981
More informationCritical Load columns buckling critical load
Buckling of Columns Buckling of Columns Critical Load Some member may be subjected to compressive loadings, and if these members are long enough to cause the member to deflect laterally or sideway. To
More informationFree Body Diagram: Solution: The maximum load which can be safely supported by EACH of the support members is: ANS: A =0.217 in 2
Problem 10.9 The angle β of the system in Problem 10.8 is 60. The bars are made of a material that will safely support a tensile normal stress of 8 ksi. Based on this criterion, if you want to design the
More informationChapter 4 Pure Bending
Chapter Pure endg INTRODUCTION endg tress W W L endg of embers made of everal aterials 0 5 lumum 0.5 TYP rass teel rass 2.5 2 lumum 2.5 1.5 12 Cross-section, Cross-section, tress Concentrations r r D d
More informationTheory at a Glance (for IES, GATE, PSU)
1. Stress and Strain Theory at a Glance (for IES, GATE, PSU) 1.1 Stress () When a material is subjected to an external force, a resisting force is set up within the component. The internal resistance force
More informationNonlinear Finite Element Analysis of Gasketed Flange Joints under Combined Internal Pressure and Different Thermal Loading Conditions
Failure of Engineering Materials & Structures Code 50 UET TAXILA MECHNICAL ENGINEERING DEPARTMENT Nonlinear Finite Element Analysis of Gasketed Flange Joints under Combined Internal Pressure and Different
More informationStresses Analysis of Petroleum Pipe Finite Element under Internal Pressure
ISSN : 48-96, Vol. 6, Issue 8, ( Part -4 August 06, pp.3-38 RESEARCH ARTICLE Stresses Analysis of Petroleum Pipe Finite Element under Internal Pressure Dr.Ragbe.M.Abdusslam Eng. Khaled.S.Bagar ABSTRACT
More informationPVP2006-ICPVT
Proceedings of PVP26-ICPVT-11 26 ASME Pressure Vessels and Piping Division Conference July 23-27, 26, Vancouver, BC, Canada PVP26-ICPVT-11-93731 REINVESTIGATION OF A HEAT EXCHANGE FLANGE LEAK Mike Porter
More informationUnbraced Column Verification Example. AISC Design Examples AISC 13 th Edition. ASDIP Steel is available for purchase online at
Unbraced Column Verification Example AISC Design Examples AISC 3 th Edition IP Steel is available for purchase onle at www.asdipsoft.com H-9 Example H.4 W-Shape Subject to Combed Axial Compression and
More informationD e s i g n o f R i v e t e d J o i n t s, C o t t e r & K n u c k l e J o i n t s
D e s i g n o f R i v e t e d J o i n t s, C o t t e r & K n u c k l e J o i n t s 1. Design of various types of riveted joints under different static loading conditions, eccentrically loaded riveted joints.
More informationJUT!SI I I I TO BE RETURNED AT THE END OF EXAMINATION. THIS PAPER MUST NOT BE REMOVED FROM THE EXAM CENTRE. SURNAME: FIRST NAME: STUDENT NUMBER:
JUT!SI I I I TO BE RETURNED AT THE END OF EXAMINATION. THIS PAPER MUST NOT BE REMOVED FROM THE EXAM CENTRE. SURNAME: FIRST NAME: STUDENT NUMBER: COURSE: Tutor's name: Tutorial class day & time: SPRING
More information1. ARRANGEMENT. a. Frame A1-P3. L 1 = 20 m H = 5.23 m L 2 = 20 m H 1 = 8.29 m L 3 = 20 m H 2 = 8.29 m H 3 = 8.39 m. b. Frame P3-P6
Page 3 Page 4 Substructure Design. ARRANGEMENT a. Frame A-P3 L = 20 m H = 5.23 m L 2 = 20 m H = 8.29 m L 3 = 20 m H 2 = 8.29 m H 3 = 8.39 m b. Frame P3-P6 L = 25 m H 3 = 8.39 m L 2 = 3 m H 4 = 8.5 m L
More informationSamantha Ramirez, MSE. Stress. The intensity of the internal force acting on a specific plane (area) passing through a point. F 2
Samantha Ramirez, MSE Stress The intensity of the internal force acting on a specific plane (area) passing through a point. Δ ΔA Δ z Δ 1 2 ΔA Δ x Δ y ΔA is an infinitesimal size area with a uniform force
More informationDesign against fluctuating load
Design against fluctuating load In many applications, the force acting on the spring is not constants but varies in magnitude with time. The valve springs of automotive engine subjected to millions of
More informationSTRUCTURAL VERIFICATION OF A 60.7 M DOME ROOF FOR TANK FB 2110
CTS Netherlands B.V. Riga 10 2993 LW Barendrecht The Netherlands Tel.: +31 (0)180 531027 (office) Fax: +31 (0)180 531848 (office) E-mail: info@cts-netherlands.com Website: www.cts-netherlands.com Chamber
More informationEMA 3702 Mechanics & Materials Science (Mechanics of Materials) Chapter 2 Stress & Strain - Axial Loading
MA 3702 Mechanics & Materials Science (Mechanics of Materials) Chapter 2 Stress & Strain - Axial Loading MA 3702 Mechanics & Materials Science Zhe Cheng (2018) 2 Stress & Strain - Axial Loading Statics
More informationCOURSE TITLE : APPLIED MECHANICS & STRENGTH OF MATERIALS COURSE CODE : 4017 COURSE CATEGORY : A PERIODS/WEEK : 6 PERIODS/ SEMESTER : 108 CREDITS : 5
COURSE TITLE : APPLIED MECHANICS & STRENGTH OF MATERIALS COURSE CODE : 4017 COURSE CATEGORY : A PERIODS/WEEK : 6 PERIODS/ SEMESTER : 108 CREDITS : 5 TIME SCHEDULE MODULE TOPICS PERIODS 1 Simple stresses
More informationMMJ1133 FATIGUE AND FRACTURE MECHANICS A - INTRODUCTION INTRODUCTION
A - INTRODUCTION INTRODUCTION M.N.Tamin, CSMLab, UTM Course Content: A - INTRODUCTION Mechanical failure modes; Review of load and stress analysis equilibrium equations, complex stresses, stress transformation,
More informationMechanics of Materials
Mechanics of Materials Notation: a = acceleration = area (net = with holes, bearing = in contact, etc...) SD = allowable stress design d = diameter of a hole = calculus symbol for differentiation e = change
More informationFlexure: Behavior and Nominal Strength of Beam Sections
4 5000 4000 (increased d ) (increased f (increased A s or f y ) c or b) Flexure: Behavior and Nominal Strength of Beam Sections Moment (kip-in.) 3000 2000 1000 0 0 (basic) (A s 0.5A s ) 0.0005 0.001 0.0015
More informationDonald P. Shiley School of Engineering ME 328 Machine Design, Spring 2019 Assignment 1 Review Questions
Donald P. Shiley School of Engineering ME 328 Machine Design, Spring 2019 Assignment 1 Review Questions Name: This is assignment is in workbook format, meaning you may fill in the blanks (you do not need
More informationSample Question Paper
Scheme I Sample Question Paper Program Name : Mechanical Engineering Program Group Program Code : AE/ME/PG/PT/FG Semester : Third Course Title : Strength of Materials Marks : 70 Time: 3 Hrs. Instructions:
More informationMECHANICS OF MATERIALS
Third E CHAPTER 2 Stress MECHANICS OF MATERIALS Ferdinand P. Beer E. Russell Johnston, Jr. John T. DeWolf Lecture Notes: J. Walt Oler Texas Tech University and Strain Axial Loading Contents Stress & Strain:
More informationNAME: Given Formulae: Law of Cosines: Law of Sines:
NME: Given Formulae: Law of Cosines: EXM 3 PST PROBLEMS (LESSONS 21 TO 28) 100 points Thursday, November 16, 2017, 7pm to 9:30, Room 200 You are allowed to use a calculator and drawing equipment, only.
More informationInitial tension forces in guys of steel industrial chimneys at adjustment phase
American Journal of Environmental Engineering and Science 04; (5): 04-09 Published online November 30, 04 (http://www.openscienceonline.com/journal/ajees) Initial tension forces in guys of steel industrial
More informationFigure 1 Lifting Lug Geometry with Weld
Should you Perform Nonlinear Stress Analysis? Many of our clients inquire whether nonlinearity should be considered in their analyses. The answer to that question is not simple. Sometimes, as in certain
More informationInspection of Welds in Small Pipes by NDT Ultrasonic Phased-Array techniques. Detection, positioning, sizing and classification of defects.
More info about this article: http://www.ndt.net/?id=22924 Inspection of Welds in Small Pipes by NDT Ultrasonic Phased-Array techniques. Detection, positioning, sizing and classification of defects. J.
More informationCLUTCHES AND BRAKES. Square-jaw clutch
Clutches: CLUTCHES AND BRAKES A Clutch is a mechanical device which is used to connect or disconnect the source of power from the remaining parts so the power transmission system at the will of the operator.
More informationSIMPLE MODEL FOR PRYING FORCES IN T-HANGER CONNECTIONS WITH SNUG TIGHTENED BOLTS
SIMPLE MODEL FOR PRYING FORCES IN T-HANGER CONNECTIONS WITH SNUG TIGHTENED BOLTS By Fathy Abdelmoniem Abdelfattah Faculty of Engineering at Shoubra, Zagazig University, Banha Branch Mohamed Salah A. Soliman
More informationBLOCK SHEAR CONNECTION DESIGN CHECKS
REF: ASI TN013 Version 1 ASI Head Office Level 13, 99 Mount Street North Sydney NSW 2060 Tel: 02 9931 6666 Email: enquiries@steel.org.au (ABN)/ACN (94) 000973 839 www.steel.org.au ASI TECHNICAL NOTE TN013
More informationBeam Bending Stresses and Shear Stress
Beam Bending Stresses and Shear Stress Notation: A = name or area Aweb = area o the web o a wide lange section b = width o a rectangle = total width o material at a horizontal section c = largest distance
More informationFatigue Problems Solution
Fatigue Problems Solution Problem 1. (a) Given the values of σ m (7 MPa) and σ a (1 MPa) we are asked t o compute σ max and σ min. From Equation 1 Or, σ m σ max + σ min 7 MPa σ max + σ min 14 MPa Furthermore,
More informationSOLUTION (17.3) Known: A simply supported steel shaft is connected to an electric motor with a flexible coupling.
SOLUTION (17.3) Known: A simply supported steel shaft is connected to an electric motor with a flexible coupling. Find: Determine the value of the critical speed of rotation for the shaft. Schematic and
More information1. Given the shown built-up tee-shape, determine the following for both strong- and weak-axis bending:
1. Given the shown built-up tee-shape, determe the followg for both strong- and weak-ais bendg: a. Location of the neutral ais b. Moment of ertia c. Section Moduli d. Radius of gration Solution: (a) Location
More informationFinite Element Modeling for Transient Thermal- Structural Coupled Field Analysis of a Pipe Joint
International Conference on Challenges and Opportunities in Mechanical Engineering, Industrial Engineering and Management Studies 88 Finite Element Modeling for Transient Thermal- Structural Coupled Field
More informationASME VIII div.1 verification document
ASME VIII div. verification document August July, a AutoPIPE Vessel... No changes 5 Mar July, a Microprotol..7.6 Feb Same as Rev 9 including Bentley Inc. 4 Oct 9 July, a Microprotol..7.5 Oct Including
More informationMECHANICS OF MATERIALS
2009 The McGraw-Hill Companies, Inc. All rights reserved. Fifth SI Edition CHAPTER 3 MECHANICS OF MATERIALS Ferdinand P. Beer E. Russell Johnston, Jr. John T. DeWolf David F. Mazurek Torsion Lecture Notes:
More information