ASME B31.3 CODE REQUIREMENTS Introduction to Pipe Stress Analysis and CAESAR II SCOPE OF ASME B31.3 • The scope of this code includes all fluids. This scope specifically excludes the following: • Piping with an internal design pressure between 0 and 15 psi (105 kPa) • Power boilers and BEP which is required to be in accordance with B31.1 • Tubes inside fired heaters • Pressure vessels, heat exchangers, pumps, or compressors. Credits: Piping Systems Manual, Brian Silowash, McGraw-Hill ASME B31.3 FOR PIPE STRESS ANALYSIS • CHAPTER II : Design • All about minimum requirements of piping design philosophy including flexibility analysis can be found in this chapter • APPENDIX A : Allowable Stresses and Quality Factors for Metallic Piping • Table A-1 Basic Allowable Stresses in Tension for Metals • Appendix C Physical Properties of Piping Materials • Appendix D Flexibility and Stress Intensification Factors • Appendix H Sample Calculations for Branch Reinforcement • Appendix P Alternative Rules for Evaluating Stress Range • Appendix S Piping System Stress Analysis Examples LOADING TO BE CONSIDERED IN PIPE STRESS ANALYSIS • Pressure • The design pressure (internal or external) is generally set at the most severe condition of concurrent pressure and temperature expected during service [1] • The most severe condition is that which results in the greatest required component thickness and the highest component rating. [2] • For internal pressure (from most of engineering textbooks): β’ Longitudinal Pressure Stress : πππ = ππ· 4π‘ β’ Circumferential Pressure Stress (Hoop Stress): πβπ = ππ· 2π‘ βͺ π = internal pressure βͺ π· = Pipe outside diameter βͺ π‘ = pipe wall thickness [1] Credits: Pipe Stress Engineering, L.C. Peng, ASME Press [2] Credits: ASME B31.3 2012 para.301.2.1(b) LOADING TO BE CONSIDERED IN PIPE STRESS ANALYSIS • Test pressure generally is not design parameter. It is quality control measure used to find out the poor quality welding and flange joints. The test pressure at testing temperature is calculated as 1.5πππ ππ = π • ππ is the allowable stress of the pipe material at test temperature • π is the allowable stress of the pipe material at design temperature • π is the design temperature Credits: Pipe Stress Engineering, L.C. Peng, ASME Press LOADING TO BE CONSIDERED IN PIPE STRESS ANALYSIS • Test pressure (continued) • The test stress shall not exceed 100% yield strength (some code uses 90% yield strength) • When the test hoop stress at test temperature exceeds the above limit, the test pressure shall be reduced to the maximum pressure that meets this test stress limit. Credits: Pipe Stress Engineering, L.C. Peng, ASME Press LOADING TO BE CONSIDERED IN PIPE STRESS ANALYSIS • Temperature • The temperature at the most severe condition of concurrent temperature and pressure expected during service is generally selected as the design temperature [1] • Ambient temperature is used as referent temperature of pipe thermal expansion (sometimes called Installation temperature) • Steam-out temperature is the steam temperature when process equipment is being cleaned and purged by steam. [1] Credits: Pipe Stress Engineering, L.C. Peng, ASME Press LOADING TO BE CONSIDERED IN PIPE STRESS ANALYSIS • Temperature Guided Cantilever method is one of the approximated approaches for calculating bending stress from thermal expansion/contraction. ππ,π = • • • • • • • • π 6πΈπΌ 3πΈπ· = 2 β= 2 β π ππΏ πΏ ππ,π = bending stress due to thermal expansion π = bending moment π = pipe section modulus πΈ = modulus of elasticity πΌ = area moment of inertia π· = pipe outside diameter πΏ = displacement absorb leg Δ = thermal displacement Credits: Pipe Stress Engineering, L.C. Peng, ASME Press LOADING TO BE CONSIDERED IN PIPE STRESS ANALYSIS • Weight o All of these weights shall be considered β’ Pipe and piping components β’ Working and test fluid β’ Insulation β’ Refractory lining β’ Pipe attachment weight β’ Etc. LOADING TO BE CONSIDERED IN PIPE STRESS ANALYSIS Basic Beam Formula for Weight stress approximation: ππ,π = βπππ₯ = π€πΏ2 8π (at center) 5π€πΏ4 384πΈπΌ (at center) Simple Beam ππ,π = Fixed Beam βπππ₯ = π€πΏ2 12π π€πΏ4 384πΈπΌ (at end) (at center) Credits: Pipe Stress Engineering, L.C. Peng, ASME Press LOADING TO BE CONSIDERED IN PIPE STRESS ANALYSIS • Wind • Calculate wind force : πΉ = πππ πA • • • • πΉ = the total wind force on the element πππ = the equivalent wind pressure (dynamic pressure) π = the pipe element wind shape factor π΄ = the pipe element exposed area as shown • If wind velocity versus elevation is provided, dynamic pressure can be calculated from πππ = 1 2 ο²π 2 • π = the wind velocity • ο² = the air velocity Credits: CAESAR II User Guide, Technical Discussion LOADING TO BE CONSIDERED IN PIPE STRESS ANALYSIS • Earthquake • Calculate the static horizontal seismic design force using equation 13.3-1 from ASCE #7 : πΉπ = [(0.4 ππ ππ·π ππ ) / (π π/πΌπ )] (1 + 2 z / h) since ππ is "component operating weight“ Define calculated (horizontal) acceleration πΉπ ππ» = π π Credits: CAESAR II User Guide, Technical Discussion LOADING TO BE CONSIDERED IN PIPE STRESS ANALYSIS • Earthquake (continued) ππ» = [(0.4 ππ ππ·π ) / (π π /πΌπ )] (1 + 2 z / h) additionally; ππ» ≤ 1.6 ππ·π πΌπ and ππ» ≥ 0.3 ππ·π πΌπ • ππ = Component amplification factor, from Table 13.6-1 = [2.5 for "Piping"] • ππ·π = Design elastic response acceleration at short period (0.2 sec), from Section 11.4.4 • π π = Component response modification factor, from Table 13.6-1 = 12.0 for "Piping in accordance with ASME B31... with joints made by welding or brazing"; v alues range as low as 3.0 for other joints and for less ductile materials. • πΌπ = Component importance factor, from Section 13.1.3 = 1.5 for life-safety components, components containing hazardous material, or components that are required for continuous operation; 1.0 for all others • π§ = Height in structure at point of attachment • β = Average roof height of structure Credits: CAESAR II User Guide, Technical Discussion LOADING TO BE CONSIDERED IN PIPE STRESS ANALYSIS • PSV Reaction force (Open system for gas and vapor) • πΉ = reaction force at point of • • • • • • discharge to atmosphere π = flow of any gas π = ratio of specific heat π = temperature at inlet π = molecular weight of process gas π΄ = area of the outlet at the point of discharge π = static pressure within the outlet at the point of discharge Credits: API RP 520 part 2 LOADING TO BE CONSIDERED IN PIPE STRESS ANALYSIS • Slug flow • • • • 2 πΉπ₯ = ππ΄π (1 − πππ π) πΉπ¦ = ππ΄π 2 π πππ πΉπ¦ πΉπ₯ π = liquid density π΄ = pipe inside projected area π = fluid velocity π = bending angle LOADING TO BE CONSIDERED IN PIPE STRESS ANALYSIS • Other adv ance dynamic loads • Acoustic Pulsation • Pressure wav e / Water hammer / Steam hammer • Friction force between pipe or pipe attachment and support structure • Harmonic excitation v ibration induced by support structure Credits: Pipe Stress Engineering, L.C. Peng, ASME Press Stress Analysis of Piping System : Stress Categories • Primary stresses (Sustained • Secondary stresses are stresses) which are developed by the imposed loading. • Primary stresses are not selflimiting • Following lists are the loads which induced primary stresses: • Pressure • Weight developed by the constraint of displacements • These displacements can be caused either by thermal expansion or by imposed restraint and anchor point movements • Secondary stresses are selflimiting Credits: Piping Handbook, Mohinder L. Nayyar, McGraw-Hill Stress Analysis of Piping System : Stress Categories Credits: Pipe Stress Engineering, L.C. Peng, ASME Press Stress Analysis of Piping System : ASME B31.3 Basic Allowable Stresses • Basis for establishing allowable stresses in ASME B31.3 (2012) can be found in paragraph 302.3 • Appendix A table A-1 • Hot allowable stress, πβ • Cold allowable stress, ππ Credits: ASME B31.3 2012 Appendix-A Stress Analysis of Piping System : Weld Strength Reduction Factor, W • The material at weld-effect zone is weaker then the unaffected zone. • At elevated temperatures, the long-term strength of weld joints may be lower than the long-term strength of the base material. For longitudinal or spiral (helical seam) welded piping components, the product of the allowable stress and the applicable weld quality factor, SE, shall be multiplied by the weld joint strength reduction factor, W, when determining the required wall thickness for internal pressure • The weld joint strength reduction factor, W, is equal to 1.0 when evaluating occasional loads such as wind and earthquake. • It is also not required when calculating the allowable stress range for displacement stresses, SA. Credits: Pipe Stress Engineering, L.C. Peng, ASME Press Stress Analysis of Piping System : Stress Intensification Factor (SIF) • A piping system consists of many different components. However, in the analysis we normally idealize these various components into two types of elements: β’ the straight pipe beam element o When a straight pipe is subject to bending, it behaves like any straight beam: its cross-section remains circular and the maximum stress occurs at the extreme outer fiber. β’ the curved pipe beam element o When subject to a bending moment, the circular cross-section of the bend becomes oval. Credits: Pipe Stress Engineering, L.C. Peng, ASME Press Stress Analysis of Piping System : Stress Intensification Factor (SIF) Credits: Pipe Stress Engineering, L.C. Peng, ASME Press Stress Analysis of Piping System : Stress Intensification Factor (SIF) • The ovalization tendency of the curved pipe has resulted in the following peculiar phenomena: o Increase of flexibility. Ovalization is caused by the relaxation of the extreme outer fiber of the bend. o Increase of longitudinal bending stress. The relaxation of the extreme outer fiber reduced in the moment resisting arm. o Creation of circumferential shell bending stress. Squeezing the circular cross-section into an oval shape generates bending on the pipe wall. Credits: Pipe Stress Engineering, L.C. Peng, ASME Press Stress Analysis of Piping System : Stress Intensification Factor (SIF) • Code SIFs o Stress intensification factors (SIF) in ASME B31.3 Appendix-D are intended for use only on self-limiting stresses. [1] o For sustained loads, a separate set of SIFs is required. ASME B31.3 2012 provides these factor as “Moment Index”. o The stress intensification and flexibility factors at elbows and bends are sensitive to flanged ends and internal pressure. [1] [1] Credits: Pipe Stress Engineering, L.C. Peng, ASME Press Stress Analysis of Piping System : Stress Intensification Factor (SIF) Credits: ASME B31.3 2012 Appendix-D ASME B31.3 2012 Fig. 319.4.4A and Fig. 319.4.4B Stress Analysis of Piping System : Limits of Calculated Stresses due to Sustain Loads, ππΏ • Stress Due to Sustained Loads • See Appendix S, Example 2 for guidance on loading conditions and support scenarios that result in the greatest ππΏ for each operating condition being considered. • The loads due to weight should be based on the nominal thickness • Section moduli used to compute the stresses shall be based on nominal pipe dimensions less allowances • Areas used to compute the stresses in this paragraph assume nominal pipe dimensions less allowances affecting the inside diameter of the pipe • the stress due to sustained loads, ππΏ such as pressure and weight ππΏ = ππ + ππ 2+ 2ππ‘ 2 Credits: ASME B31.3 2012 para. 320.2 Stress Analysis of Piping System : Limits of Calculated Stresses due to Sustain Loads, ππΏ • The Stress due to sustained bending moment: ππ = πΌπ ππ 2+ πΌπ ππ 2 π • πΌπ = sustained in-plane moment index. In the absence of more applicable data, πΌπ is taken as the greater of 0.75ππ or 1.00. • πΌπ = sustained out-plane moment index. In the absence of more applicable data, πΌπ is taken as the greater of 0.75ππ or 1.00. • ππ = in-plane moment due to sustained loads, e.g., pressure and weight • ππ = out-plane moment due to sustained load s, e.g., pressure and weight • π = sustained section modulus using nominal pipe dimensions less allowances Credits: ASME B31.3 2012 para. 320.2 Stress Analysis of Piping System : Limits of Calculated Stresses due to Sustain Loads, ππΏ • The Stress due to sustained torsional moment: πΌπ‘ ππ‘ ππ‘ = 2π • πΌπ‘ = sustained torsional moment index. In the absence of more applicable data, It is taken as 1.00. • ππ‘ = torsional moment due to sustained loads, e.g., pressure and weight Credits: ASME B31.3 2012 para. 320.2 Stress Analysis of Piping System : Limits of Calculated Stresses due to Sustain Loads, ππΏ • The Stress due to sustained longitudinal force: πΌπ πΉπ ππ = π΄π • π΄π = cross-sectional area of the pipe, considering nominal pipe dimensions less allowances • πΉπ = longitudinal force due to sustained loads, e.g., pressure and weight • πΌπ = sustained longitudinal force index. In the absence of more applicable data, πΌπ is taken as 1.00. Credits: ASME B31.3 2012 para. 320.2 Stress Analysis of Piping System : Limits of Calculated Stresses due to Sustain Loads, ππΏ Stresses Due to Sustained Loads, πΊπ³ . “The sum of the longitudinal stresses due to sustained loads, ππΏ , such as pressure and weight in any component in a piping system shall not exceed πβ , where πβ is taken from ASME B31.3 Table A-1 at the metal temperature of the operating condition being considered.” ππΏ ≤ πβ • πβ = basic allowable stress at maximum metal temperature expected during the displacement cycle under analysis • For castings, the basic allowable stress shall be multiplied by the applicable casting quality factor, πΈπ . For longitudinal welds, the basic allowable stress need not be multiplied by the weld quality factor, πΈπ Credits: ASME B31.3 2012 para. 302.3.5(c) Stress Analysis of Piping System : Limits of Calculated Stresses due to Displacement Stress Range, ππΈ • Flexibility Analysis • Piping systems shall have sufficient flexibility to prevent thermal expansion or contraction or movements of piping supports and terminals from causing [1] o failure of piping or supports from overstress or fatigue o leakage at joints o distortion in piping and valves or in connected equipment (pumps and turbines, for example), resulting from excessive thrusts and moments in the piping • the computed displacement stress range ππΈ = ππ + ππ [2] 2 + 2ππ‘ 2 [1] Credits: ASME B31.3 2012 para. 319.1.1 [2] Credits: ASME B31.3 2012 para. 319.4.4 Stress Analysis of Piping System : Limits of Calculated Stresses due to Displacement Stress Range, ππΈ • πΊπ = axial stress range due to displacement strains • = ππ πΉπ/π΄π • ππ = axial stress intensification factor. In the absence of more applicable data ππ = 1.0 for elbows, pipe bends, and miter bends (single, closely spaced, and widely spaced), and ππ = π0 (or π when listed) in Appendix D for other components • πΉπ = range of axial forces due to displacement strains between any two conditions being evaluated • π΄π = cross-sectional area of pipe Credits: ASME B31.3 2012 para. 319.4.4 Stress Analysis of Piping System : Limits of Calculated Stresses due to Displacement Stress Range, ππΈ • The resultant bending stresses, πΊπ • for elbows, miter bends, and full size outlet branch connections (Legs 1, 2, and 3) shall be calculated from following equation: ππ = ππ ππ 2+ ππ ππ 2 π • for reducing outlet branch connections shall be calculated from following equation: o For Header (Leg 1 and Leg 2) ππ = ππ ππ ππ ππ 2 π o For Branch (Leg 3) ππ = 2+ ππ ππ 2+ ππ ππ 2 ππ Credits: ASME B31.3 2012 para. 319.4.4 Stress Analysis of Piping System : Limits of Calculated Stresses due to Displacement Stress Range, ππΈ Stress Analysis of Piping System : Limits of Calculated Stresses due to Displacement Stress Range, ππΈ • ππ = in-plane stress intensification factor (Appendix D) • ππ = out-plane stress intensification factor (Appendix D) • ππ = effective section modulus for branch • • • • • = ππ22 ππ ππ = effective branch wall thickness, lesser of πΰ΄€β and ππ πΰ΄€π π2 = mean branch cross-sectional radius πΰ΄€β = thickness of pipe matching run of tee or header exclusive of reinforcing elements πΰ΄€π = thickness of pipe matching branch π = section modulus of pipe • Torsional stress, ππ‘ = ππ‘ ππ‘ /2π • ππ‘ = torsional stress intensification factor. In the absence of more applicable data, ππ‘ p 1.0 • ππ‘ = torsional moment Credits: ASME B31.3 2012 para. 319.4.4 Stress Analysis of Piping System : Limits of Calculated Stresses due to Displacement Stress Range, ππΈ Allowable Displacement Stress Range, SA. “The computed displacement stress range, SE, in a piping system shall not exceed the allowable displacement stress range, SA” ππΈ ≤ ππ΄ ππ΄ = π 1.25ππΆ + 0.25πβ • (1a) When πβ is greater than ππΏ , the difference between them may be added to the term 0.25πβ in eq. (1a). In that case, the allowable stress range is calculated by eq. (1b): ππ΄ = π 1.25 ππΆ + πβ + ππΏ (1b) Stress Analysis of Piping System : Limits of Calculated Stresses due to Displacement Stress Range, ππΈ Credits: ASME B31.3 2012 para. 302.3.5 Stress Analysis of Piping System : Limits of Calculated Stresses due to Occasional Loads • The sum of the longitudinal stresses, ππΏ , due to sustained loads, such as pressure and weight, and of the stresses produced by occasional loads, such as wind or earthquake, may be as much as 1.33 times the basic allowable stress given in Appendix A. Wind and earthquake forces need not be considered as acting concurrently. ππΏ πππ + πππΆπΆ ≤ 1.33πβ • Stresses due to test conditions are not subject to the limitations in para. 302.3. It is not necessary to consider other occasional loads, such as wind and earthquake, as occurring concurrently with test loads. Credits: ASME B31.3 2012 para. 302.3.6 Stress Analysis of Piping System : Limits of Calculated Stresses due to Test Loads • Refer to ASME B31.3 2012 para 345.4.2(c) • ππ Minimum test gage pressure, ππ = π π • if the test pressure as defined above would produce a nominal pressure stress or longitudinal stress in excess of the yield strength at test temperature or a pressure more than 1.5 times the component rating at test temperature, the test pressure may be reduced to the maximum pressure that will not exceed the lesser of the yield strength or 1.5 times the component ratings at test temperature. • CAESAR II has implement this paragraph in to their recommended load case setup as ππ»ππ· ≤ ππ¦ References • ASME B31.3 Process Piping edition 2012 • Pipe Stress Engineering, L.C. Peng, ASME Press • Piping Systems Manual, Brian Silowash, McGraw-Hill • Piping Handbook, Mohinder L. Nayyar, McGraw-Hill • CAESAR II 2013 User Guide, Technical Discussion • API RP 520 part 2 : Installation