Experimental and numerical analysis of elasto-plastic behaviour of notched sp...IJERA Editor
The objective of the work was to estimate the elasto-plastic stress and strain behaviour at the root of the notch of
an Al 6061 plate undergoing tensile and compressive cyclic loading by both experimental and numerical
methods. This attempt to measured initial elasto-plastic stresses experimentally then verified by numerically.
The various Kt values such as 2, 4 and 6 specimens were subjected to tensile test using a computerised universal
testing machine. Numerical approach associated with body discretization and developed finite element model
with sufficient degree of freedom to analyses elasto-plastic analysis of notched specimen. Experimental results
show that analysis of three Kt notched specimens had similar behaviour of elasto-plastic behaviour but different
magnitude. The experimental results compare well with the numerical results which are obtained during finite
element analysis of notched specimens.
Experimental and numerical analysis of elasto-plastic behaviour of notched sp...IJERA Editor
The objective of the work was to estimate the elasto-plastic stress and strain behaviour at the root of the notch of
an Al 6061 plate undergoing tensile and compressive cyclic loading by both experimental and numerical
methods. This attempt to measured initial elasto-plastic stresses experimentally then verified by numerically.
The various Kt values such as 2, 4 and 6 specimens were subjected to tensile test using a computerised universal
testing machine. Numerical approach associated with body discretization and developed finite element model
with sufficient degree of freedom to analyses elasto-plastic analysis of notched specimen. Experimental results
show that analysis of three Kt notched specimens had similar behaviour of elasto-plastic behaviour but different
magnitude. The experimental results compare well with the numerical results which are obtained during finite
element analysis of notched specimens.
EGME 306A The Beam Page 1 of 18 Group 2 EXPER.docxSALU18
EGME 306A The Beam
Page 1 of 18
Group 2
EXPERIMENT 3:The Beam
Group 2 Members:
Ahmed Shehab
Marvin Penaranda
Edwin Estrada
Chris May
Bader Alrwili
Paola Barcenas
Deadline Date: 10/23/2015
Submission Date: 10/23/2015
EGME 306A – UNIFIED LABORATORY
EGME 306A The Beam
Page 2 of 18
Group 2
Abstract (Bader):
The main objective for this experiment was to determine the stress, deflection, and strain of a supported beam
under loading, and to experimentally verify the beam stress and flexure formulas. Additionally, maximum
bending stress and maximum deflection were determined. To accomplish this, a 1018 steel I-beam with a strain
gage bonded to the underside was utilized in conjunction with a dial indicator to monitor beam deflection. In
order to determine the values for strain and deflection, the beam underwent testing utilizing the MTS Tensile
Testing machine, which applied a controlled, incrementally increasing load to the beam. This data was then
utilized along with calculations for the beams neutral axis, moment of inertia, and section modulus to determine
the required objective values. Final values of 12,150 psi for the maximum actual stress (vs. 12,784.8 psi for
theoretical stress), and 0.0138 in for the maximum actual deflection (vs. .0130 in for theoretical deflection)
correlated closely with each other, and successfully verify established beam stress and flexure formulas.
EGME 306A The Beam
Page 3 of 18
Group 2
Table of Contents:
List of Symbols and Units 4
Theory 5
Procedure and Experimental Set-up 8
Results 9
Sample Calculations and Error Analysis 12
Discussion and Conclusion 15
Bibliography 16
Appendix 17
EGME 306A The Beam
Page 4 of 18
Group 2
List of Symbols and Units (Chris):
List of Symbols and Units Name of variables (units) Units
𝜎 Stress psi
𝑃 Applied load lbf
𝐼 Moment of Inertia in.4
𝜀 Strain in/in
𝐿 Length of the bar in
Z Section Modulus of Beam in3
𝑐 Distance to Beam Neutral Axis in
𝐸 Modulus of Elasticity psi
EGME 306A The Beam
Page 5 of 18
Group 2
Theory (Edwin):
There are two main objectives for this experiment: to determine maximum bending stress values in
the beam and to determine the deflection in the beam. To help visualize this phenomena, imagine
cutting a section of a symmetrically loaded beam:
Now, examine diagrams of this section before (Fig. A) and after bending (Fig. B):
(Fig. A)
(Fig. B)
The main points to take away from the above diagrams are as follows: When the moment, M is applied
as shown in Fig. A, forces will be in compression near the top (positive moment) and in tension near
the bottom (negative moment). The effects from this moment are seen in Fig. B.
For determining max stress values, one concept to note is that our bending moment M can help
calculate bending stress. First, we rec
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Stress analysis plays an important role in the design of structures like crane hook under loading conditions.
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Twice yield method for assessment of fatigue life assesment of pressure swing adsorber (psa) vessel by fea.
1. 1
TWICE-YIELD METHOD FOR ASSESSMENT OF FATIGUE LIFE
PRESSURE SWING ADSORBER (PSA) VESSEL BY FEA.
Kingston Rivington
ASME Authorized Inspector
ASNT Level 3 RT, PT, MT, UT, VT, ET, LT
ISO 9712 Level 3 PAUT/TOFD, API 510,570,653
rivington24@gmail.com Ref: # 9-2-2020
“A tribute to Late Dr. Arthur Kalnins (1931-2020) Lehigh University, who contributed his excellent work for local
strain-based fatigue approaches “
-------------------------------------------------------------------------------------------------------------------------------------------
1. OVERVIEW:
The objective of the example is to determine the number of design cycles of PSA’s at Nozzle to Elliptical
head & Knuckle portions as per Section VIII, Division 2³, of ASME Boiler and Arthur Kalnins² local strain
approach. In this example, the methodology of the twice yield fatigue analysis is used for finding out of
allowable design cycles. The PSA vessel is operated at cyclic pressure range during its service. The
Nonlinear Elastic plastic fatigue analysis is performed for a PSA that subjected to a repeated cycle of pressure
inside the vessel. No Temperatures are cycled. The Finite element analysis was performed to find out
Equivalent stress and Plastic Stain range, then values are substitute into Div,2 formulae to obtain maximum
allowable cycles.
2. ORGINAL DESIGN AND MATERIAL DATA FOR PSA
Shell material: SA516 Gr70
Ellipsoidal Head material 2:1: SA516 Gr70
Nozzle Pipe: SA350LF2 Cl 1
Nozzle Flange: SA 350 LF2 Cl.1
Table 1. Cyclic Parameters
PARAMETER UNIT PSA
Pressure Range Bar.g 4 –70 (7.0 Mpa)
Temperature Range ºC 25-45
Total Cycle time (design) Sec 540
Total cycle time (Operation) Sec 1100
Figure 1: Pressure Sequence for adsorption and regeneration cycle.
2. 2
Figure-2 Design drawing details for PSA
3.0 NOMENCLATURE
nc s s = material parameter for the cyclic stress–strain curve model
σa = total stress amplitude.
σr = total stress range
Kc s s = material parameter for the cyclic stress–strain curve model
Δεpeq, k = equivalent plastic strain range for the kth loading condition or cycle.
Δεeff , k = Effective Strain Range for the kth cycle.
ΔSp k = equivalent stress Range
Eya,k = value of modulus of elasticity of the material at the point under consideration
ɛtr = total true strain range.
ɛ pr = Plastic strain range.
Salt =effective alternating equivalent stress amplitude
4.0 MATERIAL PROPERTIES FOR STRESS ANALYSIS
According to 2019 Div. 2, paragraph 5.5.4.1(c ), a stabilized cyclic stress-strain curve shall be used. In this example, the
cyclic curves provided in 2019 Div. 2, Part 3, Annex 3.D, paragraph 3.D.4, will be used. The cyclic curve is defined by
equation (1).
3. 3
The ɛta , total true strain amplitude to be cycled, The above equation is Ramberg-Osgood (R-O) format of the cyclic
curve of equation (1) is not of the form that used in typical finite element programs that require a separation of elastic
and elastic-plastic behaviour at a specified yield stress. Equation (1) gives no such yield stress separation.
To find out the yield stress the following two methods are followed as described Arthur Kalnins²
1. Method A : To approximate this yield stress and modify the form of the curve, an offset of plastic strain,
offset, (2.0e-5) is assumed and a line is drawn along the elastic slope of Ramberg-Osgood (R-O). The
intersection of this line and the cyclic stress-strain curve is taken as the yield stress
Figure-3 Ramberg-Osgood yield stress by curve shift method
2.Method B: The yield stress is calculated also from formula approach equation (2)
For this example, the Method B formula approach has been chosen to find out yield stress.
ncss = 0.126 Table 3-D.2M Cyclic Stress–Strain Curve Data
Kcss = 693 Mpa Table 3-D.2M Cyclic Stress–Strain Curve Data
offset= 2.0e-5 Table 3-D.1M Cyclic Stress–Strain Curve Data
σy Yield stress = 177.25 Mpa
4. 4
For the Twice-Yield Method, the curves are then converted to the hysteresis loop stress and strain curve form
(strain range versus stress range). The plastic strain range is related to the stress range by the following equation (3)
Table 2: Stress range versus plastic strain range
Stress range
(Mpa)
Ey ncss Kcss εoffset
Plastic Strain
Range
355 1.98E+05 0.126 693 2.00E-05 0.00E+00
370 1.98E+05 0.126 693 2.00E-05 1.61E-05
380 1.98E+05 0.126 693 2.00E-05 2.93E-05
390 1.98E+05 0.126 693 2.00E-05 4.52E-05
400 1.98E+05 0.126 693 2.00E-05 6.42E-05
410 1.98E+05 0.126 693 2.00E-05 8.67E-05
420 1.98E+05 0.126 693 2.00E-05 1.13E-04
430 1.98E+05 0.126 693 2.00E-05 1.45E-04
440 1.98E+05 0.126 693 2.00E-05 1.82E-04
450 1.98E+05 0.126 693 2.00E-05 2.25E-04
460 1.98E+05 0.126 693 2.00E-05 2.76E-04
470 1.98E+05 0.126 693 2.00E-05 3.35E-04
480 1.98E+05 0.126 693 2.00E-05 4.03E-04
490 1.98E+05 0.126 693 2.00E-05 4.81E-04
500 1.98E+05 0.126 693 2.00E-05 5.72E-04
510 1.98E+05 0.126 693 2.00E-05 6.76E-04
520 1.98E+05 0.126 693 2.00E-05 7.96E-04
530 1.98E+05 0.126 693 2.00E-05 9.32E-04
540 1.98E+05 0.126 693 2.00E-05 1.09E-03
550 1.98E+05 0.126 693 2.00E-05 1.26E-03
560 1.98E+05 0.126 693 2.00E-05 1.46E-03
The Table 2 Stress range versus plastic strain range values are taken into material model.
5.0 MODEL AND LOADING
The axisymmetric model 2D was taken from Example as 3D models are time consumed and complicated. The pressure
load was modified to 7 Mpa (load at the cycle end point) and the nozzle thrust load(14 Mpa) was adjusted accordingly.
The boundary conditions are X=0 ,Y=0.The multilinear Kinematic hardening Ansys workbench¹ model has been chosen.
Figure 4.PSA model Figure 5. 2D model
5. 5
Figure 6. Boundary condition
6.0 DETERMINATION OF EFFECTIVE STRAIN RANGE BY TWICE-YIELD METHOD
The method is explained well by A. Kalnins² in his paper that if in the input the loading is specified as the loading
range, and the cyclic stress range-strain range curve is used for the material model, then in the output the stress
components are the stress component ranges and the strain components are the strain component ranges. Thus,
in one FEA load step, for which the loading is specified from zero to that of the loading range, the output provides
the stress and strain ranges that are needed for fatigue analysis
Figure 4 : Twice Yield method with single load step
7.0 DETERMINATION OF DESIGN CYCLES
6. 6
Figure 7. Von mises Equivalent stress range
Figure 8. Equivalent plastic strain range
a). To find out Effective Strain Ranges
ΔSp k = equivalent stress (values obtained from Ansys output)
Δεpeq, k = equivalent plastic strain range (values obtained from Ansys output)
Eya,k = value of modulus of elasticity of the material
Table-3
Component Location Eya,k ΔSp k Δεpeq, k Δεeff , k
Nozzle Inside Radius 1.98E+05 515.84 8.34E-04 3.44E-03
Knuckle inside radius 1.98E+05 363.69 1.00E-05 1.85E-03
7. 7
b. Determine the effective alternating equivalent stress for the cycle.
Table- 4
Component Location Eya,k Δεeff , k Salt,K
Nozzle Inside Radius 1.98E+05 3.44E-03 3.41E+02
Knuckle inside radius 1.98E+05 1.85E-03 1.83E+02
C. Determine the permissible number of cycles, Nk , for the alternating equivalent stress computed in Step b. Fatigue
curves based on the materials of construction are provided in ASME Division VIII Div 2 Annex 3-F, 3-F.1,
For Carbon, Low Alloy, Series 4XX, High Alloy, and High Tensile Strength Steels for temperatures not exceeding
371°C (700°F). The fatigue curve values may be interpolated for intermediate values of the ultimate tensile strength.
ET = the material modulus of elasticity at the cycle temperature
(1) For σuts ≤ 552 MPa (80 ksi) (see Figures 3-F.1M and 3-F.1) and for 48 MPa (7 ksi) ≤ Sa ≤ 3 999 MPa (580 ksi)
10ᵞ = 32.24 The above equation can be used.
The design number of design cycles, N, can be computed from eq. (3-F.21) based on the parameter X calculated for
the applicable material
Table- 5
Component Location ET Sa Y X N cycles
Nozzle Inside Radius 1.98E+05 3.41E+02 1.68E+00 3.70E+00 5032
Knuckle inside radius 1.98E+05 1.83E+02 1.41E+00 4.53E+00 33800
8.0 CONCLUSION
Refer from table -5, nozzle to ellipsoidal head junction, would limit the design cycle life of PSA is 5032 cycles.
References
1.ANSYS workbench (version 19.2) [FEA software]
2.Twice-Yield Method for Assessment of Fatigue Caused by Fast Thermal Transient According To 2007 Section Viii-Division 2 by Arthur Kalnins.
3.ASME Boiler & Pressure Vessel Code, Section VIII Div.2 2019 edition.
4.ASME PTB-3-2013