Assessing the Notch Sensitivity of High Strength Wires

Abstract

High strength wires, which have a poor notch sensitivity performance, are currently been used on many offshore applications where high stresses without yielding are demanded. To assess these wires notch sensitivity, an integrated approach was implemented. An experimental program was conducted, through the realization of fatigue tests to obtain the fatigue limit for notched and notched free specimens to assess the fatigue stress concentration factor. A numerical approach using Finite Element Method, and an analytical model, available in technical literature, were used to assess the stress concentration factor. With both results, the notch sensitivity could be obtained.

Keywords:
Fatigue; notch sensitivity; staircase method

1 INTRODUCTION

The notch sensitivity (q) is a very important design parameter, since its estimation directly influences the design against fatigue failure of mechanical parts. Also notch sensitivity is associated with many other mechanical design concepts such as: stress concentration factor (SCF) or K _t, fatigue SCF or K _f and short cracks propagation. Indeed, the SCF is a well-known parameter used in mechanics of solids to estimate the stress amplification caused by a mechanical part discontinuity, like a notch. Its estimation depends entirely on the loading type and the geometry of the discontinuity. It is also well-known that for variable load the stress amplification, for ductile materials, is usually overestimated by K _t. To reduce the conservatism in the design of mechanical parts that are subjected to variable loading, the fatigue SCF is used. This variable is also a function of notch sensitivity factor (q) that takes into account, for notches, both: notch radius (r) and material ultimate strength (S_ut), recognizing that material influences on the stress amplification near notch discontinuity.

Research has been done in this area by Castro and Meggiolaro (2013), which associated the notch sensitivity with the relatively fast generation of tiny non-propagating cracks at notch root. According to the authors it indicates that the crack initiation is controlled by the stresses acting at notch tip and the fatigue crack growth behavior of short cracks emanating from notch root could be affected by the generated stress gradients. So, a crack could start at a notch tip and then stop after a short growth, due to the decreasing of the driving force in spite of its growing size. Thus, q should depend not only on the notch tip radius but also on the notch depth. Castro et al. (2014) addresses semi-empirical q factors that consider the notch tip stress gradient influencing on the fatigue behavior of short cracks. According to the authors, properly calculation of q values can be done from its fatigue limit (Se), and crack propagation threshold (ΔK_th), considering all the notch geometry and loading characteristics, without the need of any adjustable parameter.

Hu et al. (2012) made a review of various concepts that are related to q as fracture process zone, damage process zone and theory of critical distance (TCD), suggesting an exponent m to estimate q. The results indicate that there is an optimal m value for each material. Also, Arola and Williams (2002) evaluated the apparent K _t of surface texture on the fatigue life of high-strength low-alloy steels (HSLAS). It was found that the fatigue life of the used HSLAS was surface-texture-dependent, with the fatigue strength decreasing with the increase of the surface roughness.

Chapetti and Gerrero (2013) proposed the integration of fracture mechanics concepts to account for both: the fatigue notch sensitivity and the notch size effect. In fact, for components tested under cyclic loading containing notches or holes of a given K_t, with their fatigue strengths measured, the smaller are the notch or hole sizes, smaller is the decrement of K_f value.

In this article, an integrated approach was implemented to estimate the notch sensitivity of high strength wires (HSW). To accomplish it, K _f was obtained from experimental results of notched and notched free specimens. The estimation of K _t was implemented through the use of finite element commercial software, double-checked by an analytic approach as in Young (1989). Thus, the estimation of q was obtained through the utilization of classical relationships between K _t and K _f.

2 EXPERIMENTAL APPROACHES

The experimental approaches were divided in: material characterization, fatigue apparatus and fatigue procedure. The material characterization was divided in chemical analysis, tensile tests, optical microscopy, hardness and roughness tests. The fatigue apparatus describes the specimen dimensions, servo-hydraulic machine setup and test accessories. The fatigue procedure explains the staircase method used to determine the fatigue limits. The material characterization is addressed in sequence.

2.1 Material Characterization

The material characterization was done through the implementation of chemical analysis, tensile tests, optical microscopy, hardness and roughness tests of the HSW specimens. Table 1 shows the results of chemical analysis done by the use of optical emission spectroscopy technique. Table 2 shows the tensile tests results performed to determine the material main monotonic mechanical properties, such as: Yield Strength (S_y); Ultimate Strength (S_ut) and Elongation (EL). For tensile tests, three specimens of 200 mm length were used with 50 mm gage length for elongation measurements. It can be seen from Tables 1 and 2 that high values of S _y and S _ut are consistent with high strength steels (HSS) and compatible with a SAE 1065 steel material.

Table 1:
Chemical analysis results.

Chemical composition in weight
element	C	Si	Mn	P	S	Cr	Mo	Ni	Al
(%)	0.64	0.22	0.74	0.019	0.007	0.037	0.009	0.023	0.028

Table 2:
Tensile tests results.

Specimen	Sy (MPa)	Sut (MPa)	EL (%)
1	1150	1260	15.3
2	1180	1270	15.0
3	1150	1250	14.6
average	1160	1260	14.9

The Young modulus and Poison ratio were estimated, respectively, as E = 200 GPa and ν = 0.29. Also, it is important to observe that a high S _ut is directly related to high fatigue resistance (S_f).

To implement the hardness tests an Instron Wolpert machine was used with a Rockwell C indenter. To obtain the surface roughness it was used a Tesa-Rugosurf 10 equipment. Tables 3 and 4 show the hardness and the roughness results, respectively.

Table 3:
Hardness results.

Test	HRC
1	34.8
2	36.0
3	35.5
average	35.4

Table 4:
Roughness results.

Measurement	Ra longitudinal (μm)	Ra transversal (μm)
1	0.22	0.58
2	0.14	0.65
3	0.22	0.45
average	0.19	0.56

Note that the average hardness of the HSS, of Table 3, resulted in a quite high value for steel without the use of any thermomechanical process, as quenching. Also, note that the average roughness measurement, in Table 4, revealed a quite different roughness depending on the test direction. Optical microscopy was used to assess the microstructure wires aspect. The observed transversal and longitudinal (reference to the rolling direction) cross sections are shown in Fig. 1.

Figure 1:
Microstructural aspect observed by optical microscopy. (a) Transversal and (b) longitudinal cross sections. Etching: nital 2%. Magnification: 1000 X. Bandeira et al. (2014).

It can be observed that the microstructure is composed of elongated grains, in the rolling direction, of ferrite and pearlite. The volumetric fraction of pearlite is consistent with an eutectoid carbon steel composition. It can be also observed fine elongated white areas between pearlite grains which correspond to the primary ferrite. Such microstructural aspect suggests a severe cold working, compatible with the last rolling pass that could be applied under the critical temperature. Such procedure is in line with materials aiming to attain high yield strength and ultimate tensile strength levels. The fatigue apparatus is addressed in sequence.

2.2 Fatigue Apparatus

To experimentally assess K _f value, it was necessary to obtain the notched and notched free specimens fatigue limits. To accomplish this objective notches and notched free specimens were tested in a servo-hydraulic test machine, equipped with a four points bending fixture.

The specimens were submitted to different loading levels, maintaining the same loading ratio R = σ_min / σ_max. All specimens were manufactured in house by cutting 200 mm length bars. Concerning the specimen’s surface finishing, they were far from highly polished; indeed all surface finishing was maintained as received, with arithmetic average of absolute values of roughness (R_a) shown in Table 4. In this way, it was considered that the fatigue curves were related to real parts rather than the usual high polished specimens. Fig. 2 shows both specimens types.

Figure 2:
Specimen technical drawing (dimensions in mm). (a) notched free and (b) notched.

The dimensions were identical for both specimens’ types, notched and notched free, unless by a 0.4 mm shallow notch for the notched specimens generated (at transversal direction) by a broaching process in half its longitudinal length. Figure 3 shows the servo-hydraulic test machine used to implement the experimental fatigue tests, where Fig. 3.a shows the servo-hydraulic test machine general view and Fig. 3.b shows a specimen positioned on the inferior part of the four points bending fixture.

Figure 3:
Servo-hydraulic test machine: (a) general view and (b) four points bending fixture (only the bottom part is shown).

Fig. 4 shows the four points bending fixture schematic drawing that is used to show some important geometric and loading characteristics.

Figure 4:
The four points bending fixture schematic drawing.

The distances between rollers were defined in function of the specimen length. The bending moment is considered uniform between the upper rollers. The experimental tests were conducted using pulsating loads, to guarantee the upper rollers contact with specimen during the tests. The fatigue loading levels were defined as a ratio between the specimen maximum stress (σ_max) and the S _ut, always maintaining the same loading ratio R.

The maximum force (F_max) applied by the test machine was calculated as in Crandall et al. (1978):

${\text{F}}_{max}=\left(\frac{2\cdot \text{I}}{\text{a}\cdot \text{c}}\right){\sigma }_{max}$ (1)

Where, I is the specimen second moment of area, a is the distance between lower and upper rollers (see Fig. 4) and c is the specimen semi-height (note that for notched specimen, the notch depth is deducted).

The four points bending apparatus was used, as shown schematically in Fig. 4, to apply the pulsating load. The ratio was maintained at R = 0.1. As the pulsating sine load has nonzero mean stress it was necessary to transform both, mean stress (σ_m) and alternating stress (σ_a), on equivalent alternating stress (σ _{a_eq}), as in Budynas and Nisbett (2014) and Castro and Meggiolaro (2016):

$\frac{{\text{σ}}_{\text{a}\_\text{eq}}}{S_{ut}}=\frac{{\text{σ}}_{\text{a}}}{S_{ut}}\frac{1}{\left(1-\left(\frac{1+\text{R}}{1-\text{R}}\right)\frac{{\text{σ}}_{\text{a}}}{S_{ut}}\right)}\begin{array}{c}\end{array}\text{or}\begin{array}{c}\end{array}\frac{{\text{σ}}_{\text{a}\_\text{eq}}}{S_{ut}}=\frac{\left(1-R\right)\left(\frac{{\text{σ}}_{\text{max}}}{S_{ut}}\right)}{\left(2-\left(1+R\right)\left(\frac{{\text{σ}}_{\text{max}}}{S_{ut}}\right)\right)}$ (2)

It is also possible to rewrite equation 2.b to be a function of σ _{a_eq}:

$\frac{{\text{σ}}_{\text{max}}}{S_{ut}}=\frac{2\left(\frac{{\text{σ}}_{\text{a}\_\text{eq}}}{S_{ut}}\right)}{\left(\left(1-R\right)+\left(1+R\right)\left(\frac{{\text{σ}}_{\text{a}\_\text{eq}}}{S_{ut}}\right)\right)}$ (3)

The fatigue procedure is addressed in sequence.

2.3 Fatigue Procedure

One of the main objectives of this article is focused in obtaining, with maximum possible accuracy, fatigue limits of both notched and notched free HSS specimens. To accomplish this objective the staircase method was used, as in Dixon (1965) and Dixon (1948). This method uses a simple idea: a specimen is submitted to a certain stress level, after a certain number of cycles if this specimen breaks, the next specimen has the stress level decreased by a pre-defined stress decrement. However, if the specimen doesn’t break, then the stress level is increased by a pre-defined stress increment. This process continues until all specimens are used or reaches a significant number of specimens that are statistically representative according to Dixon and Mood (1948). The staircase method flowchart is presented in Fig. 5. This simple method can produce a much better estimative of the notched and notched free specimen fatigue limits than the traditional Wohler approach.

Figure 5:
Staircase method flowchart - specimen test sequence. Pollack et al. (2006)

Where C ₁ is a positive constant smaller than one that multiplies S _ut to estimate the first maximum stress σ_max1, C ₂ is a positive constant bigger than one that divides the constant C ₁ to generate the fraction of S _ut called stress increment. s is the increment or the decrement of stress and n is the number of specimens utilized. i is a counter that varies from 1 to n+1. ${\sigma }_{ma{x}_i}$ is the i ^th term of maximum stress applied to specimen. CP_i is an output variable that has two values: B or NB, which means that a specimen has broken or has not broken.

The numerical approach is addressed at the next section.

3 NUMERICAL APPROACH

It is well known that the SCF produced by a given notch depends on the mode of loading and on the notch geometry. There are many ways to estimate it: by theory of elasticity, as in Timoshenko and Goodier (1951); by experimental measurements as in Pilkey and Pilkey (2008); using, for example, photoelasticity method, as in Dally and Riley (1991), or by using a numerical method like finite element method, as in Fish (2007). In this section a numerical approach, using finite element method, is used to estimate the stress concentration factor of the shallow notch.

3.1 Numerical Model

In this article it was used the commercial software ANSYS WORKBENCH v14.0 to evaluate SCF produced by a shallow notch broached on HSS specimen. For numerical model purposes the specimen material was considered isotropic and linear elastic. The mesh was generated with hexahedrons elements PLANE 186 with plane stress option, with one node at each vertex, as shown in Fig. 6.a. The finite element model was created in 2-D dimension (in the X-Y plane) to reduce the computational effort, as shown in Fig. 6.b.

Figure 6:
Finite element model: (a) element PLANE 186 and (b) 2-D geometry.

The 2D model with plane stress option was considered based on E399 ASTM standard (2009). In item 7.1.3 of this standard, the minimum specimen width to develop plane strain condition is related to the material S_y/E ratio. Using the HSS material properties, this ratio was calculated as 0.0058, which corresponds in this standard to a minimum recommended width of 64 mm to develop plain strain condition. However, as the HSW specimen has 9 mm of width, it is quite reasonable to suppose that the state of stress is much closer, even at half specimen width, to plane stress than to plane strain condition.

Due to the notch depth is much smaller than the specimen height, in fact it is a shallow notch, and to ensure good elements aspect ratio, mainly around the notch, a refined region around it was provided as shown in Fig. 7.a. Figure 7.b shows a photo of the real notch machined by a manual broaching machine.

Figure 7:
(a) Specimen mesh details (δ = 0.075 mm) and (b) optical microscopy photo of the notch.

To guarantee the finite element model implementation consistency, a mesh convergence analysis was implemented, refining the element size, (δ) around the notch radius. Different δ were evaluated: 0.6, 0.5, 0.4, 0.3, 0.2, 0.1, and 0.075 mm. The mesh convergence was studied in function of the maximum normal stresses in the x-direction (see Fig. 6.b). Fig. 8 shows a graphical representation of the mesh convergence study.

Figure 8:
Mesh convergence study.

The mesh refinement of δ = 0.075 mm was selected for this analysis because the notch boundary can be described with a reasonable accuracy. Both, experimental and numerical results are presented at the next section.

4 RESULTS

The results are divided in two parts: experimental and numerical. At experimental part, the fatigue limit results obtained from the experimental tests are shown and, at numerical part, the SCF result obtained from the finite element method is shown.

4.1 Experimental Results

Fig. 9 shows a representation of the test sequence, for both notched and notched free specimens, applying the staircase method, as in Pollack et al. (2006), which algorithm can be seen in Fig. 5.

Figure 9:
Up-and-down sequence of staircase method: (a) notched free (b) notched specimens.

Note that all stresses are divided by S _ut, generating a ratio (σ _{a_eq} / S _ut)·100, which varies from 0 to 100%. Fig. 10 presents all fatigue results, with common points that were obtained by usual fatigue approach and up-and-down points by using staircase method. The common points are represented by black squares and the up-and-down points are represented by blue circles. Note that an arrow represent that specimen didn’t fail, for all figures. There is one arrow per specimen, unless in Fig. 10.b, where the not broken specimens were so near each other, that just one arrow was used.

Figure 10:
Fatigue results: both common points and up-and-down points for (a) notched free, (b) notched specimens.

The fatigue results which are graphically shown in Fig. 10, correspond to actual fatigue results values that are shown at ^Appendix, in Tables 6 and 7. Also in Fig. 14, at the same ^Appendix, the staircase method flowchart explains, in a graphical way, the two S _e estimation, which are represented by blue lines in Fig. 10. In Figs. 11.a and 11.b show a detailed view of up-and down points.

Figure 11:
Fatigue results, in details, for: (a) notched free and (b) notched specimens.

The fatigue limit results shown on Table 5 were obtained through the utilization of staircase method flowchart - estimation of S _e range, shown in Fig. 14 at ^Appendix. The experimental fatigue results are available at Tables 6 and 7, also at ^Appendix, or graphically in Fig. 10.

Table 5:
Fatigue limits, mean μ and the standard deviation σ.

	Specimen	μ	σ	Fatigue Limit (%)
Common points	notched free	35.5	$\{\begin{array}{c}-4.5\%\\ +4.5\%\end{array}$	33.9 ≤ (S e / S ut ) · 100 ≤ 37.1
	notched	15.5	$\{\begin{array}{c}-4.5\%\\ +4.5\%\end{array}$	14.8 ≤(S e / S ut ) · 100 ≤ 16.2
Up-and-down points	notched free	32.7	$\{\begin{array}{c}-1.1\%\\ +1.0\%\end{array}$	32.3 ≤(S e / S ut ) · 100 ≤ 33.0
	notched	12.7	$\{\begin{array}{c}-1.1\%\\ +1.0\%\end{array}$	12.6 ≤(S e / S ut ) · 100 ≤ 12.8

• Note: μ and σ were maintained from the notation adopted in et al).

The mean and the standard deviation of fatigue limit, respectively, μ and σ, of Table 5 were assessed for two cases: if the failures were the majority event, the lower stress level of survival occurrence was estimated or if the survivals were the majority event, the lower stress level of failure occurrence was estimated. Note in Table 5 that fatigue limit for both notched and notched free specimens were estimated with less dispersion when it was used the up-and-down approach, based in the staircase method when compared with the common points, obtained with usual approach.

The numerical results were assessed in sequence.

4.2 Numerical Results

To calculate the SCF, the specimen model was loaded in pure bending, to simulate the four points bending test. The bending moment value was imposed to generate a unity normal stress on longitudinal fiber at the same height of the notch root but far from it. Using this approach, the maximum stress value at the notch root turns out to be exactly the value of the SCF. Fig. 12.a shows the finite element results in a usual representation and in Fig. 12.b it was used a path approach, at the same height of the notch root, to explicitly show the stress concentration distribution.

Figure 12:
Finite element longitudinal stresses (x-axis): (a) usual presentation and (b) path approach (only left half is shown).

As expected, the stresses form a high gradient curve in the neighborhood of the shallow notch root. The ratio between maximum stresses at notch root and nominal stresses at a region far from notch, was used to estimate K _t:

${\text{K}}_t=\frac{{\text{σ}}_{\text{max}\_\text{notched}}}{{\text{σ}}_{nominalfarfromnotch}}=\frac{2.84}{1}=2.84$ (4)

Note that using the analytical approach shown at ^Appendix the K _t was estimated as 2.79, which is quite close to the finite element estimative of 2.84. So, the K _t value was estimated inside the following range: 2.79 ≤ K _t ≤ 2.84.

At next section, the material notch sensitivity factor is assessed.

5 DISCUSION

In this section the results obtained by experimental and numerical approaches are used to estimate the HSW notch sensitivity factor.

The fatigue limit range for each specimen condition can be obtained from Table 5: 32.3 ≤ (S _e _/S _ut )_{notched free} ∙ 100 ≤ 33.0 and 12.6 ≤(S _e /S _ut )_notched ∙ 100 ≤ 12.8. The fatigue stress concentration factor can be stated, as Budynas and Nisbett (2014):

${\text{K}}_f=\frac{{\left(S_{e\_}/S_{ut}\right)}_{notchedfree}}{{\left(S_e/S_{ut}\right)}_{notched}}$ (5)

So the fatigue stress concentration factor K _f can be estimated, within the following range: 2.56 ≤ K _f ≤ 2.58. In sequence, the notch sensitivity can be estimated through the utilization of a classic Peterson’s equation, as Budynas and Nisbett (2014):

$\text{q}=\frac{{\text{K}}_{\text{f}}-1}{{\text{K}}_{\text{t}}-1}$ (6)

Finally, applying the ranges calculated, respectively SCF and fatigue SCF ranges in equation (06), the range within the notch sensitivity can be estimated as: 0.86 ≤ q ≤ 0.87.

Analyzing the range for notch sensitivity factor, it can be said that the notch sensitivity narrow range obtained by the application of the proposed integrated approach revealed to be quite effective, manly due the use of the staircase method in the assessment of fatigue limits of the notched and the notched free specimens. On the other hand, the notch sensitivity range revealed to be high, indicating a probable brittle behavior, which is compatible to high strength materials. In fact, although the high ultimate strength is a desirable mechanical property to increase the fatigue resistance, the high notch sensitivity can induce deleterious effects to mechanical structures submitted to fatigue loading.

6 CONCLUSIONS

An integrated approach was used to assess the notch sensitivity of HSW. Material characterization was obtained through the implementation of chemical analysis, tension tests, hardness tests, roughness tests and optical microscopy of the HSW. Fatigue tests were accomplished with two types of wire specimens, the notched and the notched free, resulting in very distinct fatigue limits, which were used to estimate the fatigue SCF. Finite element method and analytical approaches were used to estimate the SCF with good matches between them. Finally, the notch sensitivity factor was obtained through the utilization of a well know Peterson’s equation.

In fact the utilization of the experimental/numerical integrated approach for this research was revealed quite promising in generating an estimative of HSW notch sensitivity value. In particular, the utilization of staircase method at experimental approach, really improves the fatigue limit estimation, which taking into account the natural tendency of fatigue results dispersion, contributed, in a very significant way, to obtain such a reasonable estimative of notch sensitivity.

References

• Arola, D., Williams, C.R. (2002). Estimating the fatigue stress concentration factor of machined surfaces. Int. Journal of Fatigue, 24: 923-930.
• Bandeira, C.F.C., Kenedi, P.P. and Souza, L.F.G. (2014). Analysis of Notch Sensitivity of High Strength Wires. VIII Congresso Nacional de Engenharia Mecânica - CONEM 2014, Uberlândia, Brazil.
• Budynas, R. G. and Nisbett, J. K. (2014). Shigley's Mechanical Engineering Design. 10th Edition. McGraw Hill Education.
• Castro, J.T.P. and Meggiolaro, M.A. (2016). Fatigue Design Techniques under Real Service Loads - Volume I - High-Cycle Fatigue, Amazon Books
• Castro, J.T.P., Landim, R.V., Leite, J.C.C., Meggiolaro, M.A. (2014). Prediction of notch sensitivity effects in fatigue and in environmentally assisted cracking. Fatigue Fract Engng Mater Struct, 38:161-179, doi: 10.1111/ffe.12156.
  » https://doi.org/10.1111/ffe.12156
• Castro, J.T.P. and Meggiolaro, M.A. (2013). Is notch sensitivity a stress analysis problem? Frattura ed Integrità Strutturale, 25: 79-86, DOI: 10.3221/IGF-ESIS 25.12.
  » https://doi.org/10.3221/IGF-ESIS 25.12
• Chapetti, M.D., Guerrero, A.O. (2013). Estimation of notch sensitivity and size effect on fatigue resistance. Procedia Engineering, 66:323-333.
• Crandall, S.H., Dahl, N.C., Lardner, T.J. (1978). An Introduction to the Mechanics of Solids. Second Edition with SI units, McGraw Hill International Editions.
• Dally, J.W. and Riley, W.F. (1991). Experimental Stress Analysis. McGraw-Hill. ISBN-10: 0070152187.
• Dixon, W.J. (1965). The up-and-down method for small samples. J. Am. Stat. Assoc. 60: 967-978.
• Dixon, W.J., Mood, A.M. (1948). A method for obtaining and analysing sensitivity data. J. Am. Stat. Assoc. 43: 109-126.
• E399_09 ASTM standard (2009). Linear Elastic Plane Strain Fracture Toughness KIC of Metallic Materials.
• Fish, J. (2007). A First Course in Finite Elements. Wiley. ISBN-10: 0470035803.
• Hu, X. A., Yang, X. G., Wang, J. K., Shi, D. Q., Huang, J. (2012). A simple method to analyze the notch sensitivity of specimens in fatigue tests. Fatigue Fract Engng Mater Struct , 36:1009-1016, doi: 10.1111/ffe.12053.
  » https://doi.org/10.1111/ffe.12053
• Pilkey, W.D. and Pilkey, D.F. (2008). Peterson's Stress Concentration Factors. 3rd Edition, Wiley.
• Pollak, R., Palazotto, A., Nicholas, T. (2006). A simulation-based investigation of the staircasemethod for fatigue strength testing. Mechanics of Materials, 38:1170-1181.
• Thimoshenko, S. and Goodier, S.N. (1951). Theory of Elasticity. McGraw-Hill.
• Yang, Z., Kim Kim, C.B., Cho, C., Beom, H.G. (2008).The concentration of stress and strain in finite thickness elastic plate containing a circular hole. International Journal of Solids and Structures, 45:713-731.
• Young, W.C., (1989) Roark’s Formulas for Stress and Strain. Sixth Edition with SI units, McGraw Hill International Editions.

APPENDIX

A.1. Expressions for SCFs:

Fig. 13 shows the geometry of the notches used by analytic approach:

Figure 13:
SCFs for rectangular cross-section beam submitted to pure moment: (a) U notch and (b) V notch. Young (1989).

The estimative of SCFs shown in Fig.13.a is, Young (1989):

${\text{k}}_U={\text{K}}_1+K_2\left(\frac{h}{D}\right)+K_3{\left(\frac{h}{D}\right)}^2+K_4{\left(\frac{h}{D}\right)}^3\begin{array}{c}\end{array}\text{for}\begin{array}{c}\end{array}0.5\le h/r\le 4.0$

where,

$\begin{array}{l}{K}_1=0.721+2.394\cdot \sqrt{h/r}-0.127\cdot h/r\begin{array}{cc}& \end{array}\begin{array}{c}\end{array}{K}_2=-0.426-8.827\cdot \sqrt{h/r}+1.518\cdot h/r\\ K_3=2.161+10.968\cdot \sqrt{h/r}-2.455\cdot h/r\begin{array}{cc}& \end{array}{K}_4=-1.456-4.535\cdot \sqrt{h/r}+1.064\cdot h/r\\ {\text{K}}_{t\_\text{U}}={\text{k}}_U\end{array}$

The estimative of SCFs shown in Fig. 13.b is, Young (1989):

${\text{K}}_{t\_\text{V}}=1.11\cdot {\text{k}}_U-\left[0.0275+0.1125\cdot {\left(\frac{\theta }{150}\right)}^4\right]\cdot k_U^2\begin{array}{cc}& \end{array}\text{for}\begin{array}{cc}& \end{array}\theta \le {150}^{°}$

According to Young (1989) the SCFs of a V-notch is estimated as the smaller value between K _{t_U} and K _{t_V.}. For this particular case where h = 0.4 mm, r = 0.3 mm, h/r = 1.33 mm, D = 6 mm and ϑ = 45º, the results are K _{t_U} = 2.79 and K _{t_V.} = 2.88, which results in an estimative of K _t = 2.79.

A.2. Flowchart:

Fig. 14 shows a staircase method flowchart to estimate of S _e range, as shown in Fig. 10:

Figure 14:
Staircase method flowchart - Estimation of S _e range. Pollack et al. (2006).

Where A, B and C are constants defined in the flowchart, i_max is number of specimens that have survived if the failures was the majority event (FME), S ₀ is the lower stress level of survival occurrence and m _i corresponds to the number of specimens which have survived at each stress level or i_max is number of specimens that have failed if the survival was the majority event (SME), S ₀ is the lower stress level of failure occurrence and m _i corresponds to the number of specimens which have failed at each stress level. S _e is the fatigue limit; μ and σ are, respectively, the fatigue limit mean and the standard deviation.

A.3. Tables:

Several tests were performed with two types of specimen. Tables 6 and 7 summarize the results.

Table 6:
Fatigue test results - notched free specimens.

$\left(\frac{{\text{σ}}_{\text{max}}}{{\text{S}}_{\text{ut}}}\right)$ · 100 (%)	$\left(\frac{{\text{σ}}_{\text{a}\_\text{eq}}}{{\text{S}}_{\text{ut}}}\right)$ · 100 (%)	number of cycles
		common set 0	up-and-down set 0	up-and-down set 1
50	31	1866774	1012461	1017371
52	32.8	-	174463	185197
54	34.6	-	1021397	166963
56	36.4	-	205270	-
60	40.3	138934	-	-
70	51.2	75026	-	-
80	64.3	44790	-	-
90	80.2	36380	-	-

Table 7:
Fatigue test results - notched specimens.

$\left(\frac{{\text{σ}}_{\text{max}}}{{\text{S}}_{\text{ut}}}\right)$ · 100 (%)	$\left(\frac{{\text{σ}}_{\text{a}\_\text{eq}}}{{\text{S}}_{\text{ut}}}\right)$ · 100 (%)	number of cycles
		common set 0	common set 1	common set 2	up-and-down set 0	up-and-down set 1	up-and-down set 2
18	9	-	-	-	1011280	-	-
21.5	11	1163500	-	-	1093159	1001769	-
24.9	13	-	-	-	1042841	344703	788188
28.2	15	-	-	-	178635	-	-
35.7	20	105162	76117	90535	-	-	-
46.4	28	47501	32698	28350	-	-	-
55.6	36	24117	20234	20420	-	-
66.3	47	16000	13501	12040	-	-	-
91	82	6141	-	-	-	-	-

The Tables 6 and 7 first and the second columns were calculated with the use of (03) and (02.b) equations, respectively. Note that the specimens with number of cycles values marked with a grey rectangle represents the spent cycles until the test suspension of an unbroken specimen.

Publication Dates

• Publication in this collection
  Dec 2017

History

• Received
  26 Jan 2017
• Reviewed
  26 July 2017
• Accepted
  05 Sept 2017