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Chinese Journal of Mechanical Engineering

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Open Access 01-12-2020 | Original Article

Structural Stress–Fatigue Life Curve Improvement of Spot Welding Based on Quasi-Newton Method

Authors: Yahang Qin, Shoune Xiao, Liantao Lu, Bing Yang, Xiangjie Li, Guangwu Yang

Published in: Chinese Journal of Mechanical Engineering | Issue 1/2020

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Abstract

∆F-N curves are usually used to predict the fatigue life of spot welding in engineering, but they are time-consuming and laborious and not universal. For the purpose of predicting the fatigue life of spot welding accurately and efficiently, tensile–shear fatigue tests were conducted to obtain the fatigue life of spot-welded specimens with different sheet thicknesses combinations. These specimens were simulated by using the finite element method, and the structural stress was theoretically calculated. In the double logarithmic coordinate system, the structural stress–fatigue life (S–N) curve of spot welding was fitted by the least-squares method, based on the quasi-Newton method. The square of the correlation coefficient of the S-N curve was taken as the optimization objective, with the correction coefficients of force, bending moment, spot welding diameter, and sheet thickness as the variables. During the optimization process, three different ways were utilized to get three optimized spot welding S–N curves, which are suitable for different situations. The results show that the fitting effect of the S–N curve is improved, the data points are more compact, and the optimization effect is significant. These S–N curves can be used to predict the fatigue life, which provide the basis for practical engineering application.

1 Introduction

Fatigue and fracture are the main causes of failure of engineering structures and specimens. Fatigue fracture failure involves many aspects, such as cyclic loads or disturbed loads, the formation and expansion of material defects, and the influence of the service environment, etc. Spot welding is commonly used in stainless-steel car bodies and has been widely applied in to automotive, aerospace, and railway vehicles, making it necessary to study the anti-fatigue performance of spot-welded structures. Because there are various forms of welding, it is not easy to determine the load parameters under different loading conditions, and research methods for welding fatigue strength are also different.

Using equivalent structural stresses at the spot-welded edges, Kang et al. [1, 2] proposed a fatigue prediction method for spot-welded joints in automotive body structures by substituting the stress components in the von Mises formula for the local structural stresses near the spot welding. Radaj [3] indicated that the fatigue durability of welded joints with different structures and different load forms could be evaluated by numerical calculation and analysis of local stresses on the plate around the welded joint. After that, Rupp [4] reported how to calculate these structural stresses and perform fatigue life calculations on welded joints based on maximum and minimum stresses and the load spectrum. Kang et al. [5, 6] proposed a data processing procedure to optimize the empirical factors in Rupp’s structural stress calculation, the optimized results demonstrated that the degree of scatter is less than that of previous calculations with initial empirical factors, and the fatigue life prediction using this procedure is well correlated with test results. The performance of spot welding has been analyzed by means of simulation, and the model was modified by combining it with the results of modal and component tests [7‐13]. By changing the spot-welding parameters through numerous component tests, the influence of different welding parameters on the fatigue performance of the solder joint was investigated [14‐18].

Adib [19] studied the mechanical behavior of spot welding under the tensile–shear load for one, three, and five spot welds in detail, and the volumetric approach was applied to find fatigue life duration of welded spots. Through experimental examination, Choi et al. [20] studied the fatigue behavior of spot-welded triple plates and proposed a fatigue life prediction by using the crack opening angle (COA) around the spot welding. Referring to the studies of Kan [21] and Oh [22], Pan and Sheppard [23] discussed the nature of the stresses and strains around the welded joint and studied the relationship between strain and fatigue life. Finally, they developed a fatigue life prediction method based on strain. Dong et al. [24‐26] presented a structural stress definition that is insensitive to mesh size. The definition is consistent with elementary structural mechanics theory and provides an effective measure of the stress state associated with the fatigue behavior of welded joints in the form of both membrane and bending components. Wang et al. [27] developed an empirical three-stage initiation–propagation (TSIP) model that can predict the anti-fatigue performance of spot welding under a constant amplitude tensile–shear load. They discussed the improvements of the anti-fatigue performance caused by changes in the welding geometry, residual stress, and material property with the aid of the model. Lee et al. [28] expressed the ultimate loads in terms of the base metal yield strength and specimen geometries and then presented a master overload failure curve for a single spot-welded specimen in a mixed-mode load domain. Recasting the load vs. fatigue life relations experimentally obtained, they finally succeeded in predicting the fatigue life of various spot-welded specimens with a single parameter.

Research on the fatigue characteristics of spot welding is mainly based on modal analysis, fracture mechanics, or the structural stress method. Fatigue analysis using modal analysis requires numerous experiments, entailing high costs, and the modal frequency of the structure is not easy to obtain [29, 30]. Fatigue analysis based on fracture mechanics requires establishing a detailed finite element model to analyze crack growth and deduce the stress intensity factor [31‐33]. The above process is complicated and not suitable for the simple life prediction in engineering practice. By contrast, the structural stress method is relatively simple and effective, greatly reducing the workload in engineering application.

In this paper, a finite element model of spot welding based on the structural stress method is established. The relation between the structural stress and the fatigue life of spot-welded specimens is described. For the fitted fatigue performance curve, the influence of each parameter on the fitting effect of the curve is analyzed, thereby obtaining a curve with guiding significance to engineering practice.

2 Fatigue Analysis Theory

Figure 1 shows a typical spot-welded structure, with the shaded portion being the weld nugget. In the finite element analysis, two sheets are simulated by the shell elements and the weld nugget is simulated by the CBAR beam element, which is perpendicular to the neutral layer and connects point 1 to point 2. To obtain more accurate force values and moment values for the beam element nodes, a spot-welding model should be established in the calculation. As shown in Figure 1, the axial direction of the beam element is taken as the Z direction in the FE (finite element) fatigue, but it is worth noting that, in MSC NASTRAN, the axial direction of the beam element is the X direction. Therefore, before performing the fatigue analysis, it is necessary to transform the results of the beam element’s forces and moments between the coordinate systems. The specific conversion process is given in Table 1.

Table 1

Transformation of nodal forces in FE fatigue

Point 1		Point 2		Point 3
FE fatigue	NASTRAN CBAR	FE fatigue	NASTRAN CBAR	FE-fatigue
FX1	− Z force	FX2	Z force	FX1
FY1	Y force	FY2	− Y force	FY1
FZ1	X force	FZ2	− X force	FZ1
MX1	− Z moment1	MX2	Z moment2	(MX1t2 + MX2t1)/(t+ t2)
MY1	− Y moment1	MY2	Y moment2	(MY1t2 + MY2t1)/(t1+t2)
MZ1	X moment	MZ2	− X moment	(MZ1t2 + MZ2t1)/(t1 + t2)

The structural stresses on the inner surfaces of the two sheets are calculated by using the transformed beam element nodal forces and moments (except M_Z). When considering the fatigue strength of the base metal around the weld nugget, the radial stress on the contact surface of the two sheets around the weld nugget is taken as the structural stress. However, when considering the fatigue strength of the weld nugget, the principal stress of the weld nugget at the joint cross section is taken as the structural stress, and the principal stress is determined by the shear stress and normal stress at the weld nugget. Figure 2 shows the calculation model of the equivalent structural stress of the base metal and the weld nuggets. The equations for calculating the specific equivalent structure of the base metal are as follows.

Taking sheet 1 as an example, the structural stress of the base material can be expressed by

$$\begin{aligned} \sigma_{v1} = & - \sigma_{\text{max} } \left( {F_{x1} } \right)\cos \theta - \sigma_{\text{max} } \left( {F_{y1} } \right)\sin \theta + \sigma_{\text{max} } \left( {F_{z1} } \right) \\ + \sigma_{ \text{max} } \left( {M_{x1} } \right)\sin \theta - \sigma_{\text{max} } \left( {M_{y1} } \right)\cos \theta , \\ \end{aligned}$$

(1)

where

$$\sigma_{{\text{max}}} \left( {F_{x1} } \right) = \frac{{F_{x1} }}{{\pi ds_{1} }},$$

(2)

$$\sigma_{\text{max} } \left( {F_{y1} } \right) = \frac{{F_{y1} }}{{\pi ds_{1} }},$$

(3)

$$\sigma_{\text{max} } \left( {M_{x1} } \right) = K_{1} \left( {\frac{{1.872M_{x1} }}{{ds_{1}^{2} }}} \right),$$

(4)

$$\sigma_{\text{max} } \left( {M_{y1} } \right) = K_{1} \left( {\frac{{1.872M_{y1} }}{{ds_{1}^{2} }}} \right),$$

(5)

where $d$ is the diameter of the weld nugget, $s_{1}$ is the thickness of sheet 1, $K_{1} = 0.6\sqrt {s_{1} }$ is the empirical correction coefficient, and $\theta$ is the angle of the calculated stress.

When $F_{z1} > 0$, the axial force of the weld nugget is a tensile force, which will cause fatigue damage. Consequently, the influence of the axial force should be considered:

$$\sigma \left( {F_{z1} } \right) = K_{1} \left( {\frac{{1.744F_{z1} }}{{s_{1}^{2} }}} \right).$$

(6)

When $F_{z1} \le 0$, the axial force of the weld nugget is a compressive force, hence no fatigue will occur. Therefore, the influence of the axial force can be ignored:

$$\sigma \left( {F_{z1} } \right) = 0.$$

(7)

For the fatigue strength of the base metal, the equations for calculating the structural stress are given above. By solving for the structural stress and using probability and statistics methods, the stress–life distribution can be obtained. These data can be fitted to establish the structural stress–fatigue life (S–N) curves of the base metal, which are suitable for the fatigue design and life prediction of the spot-welded structures.

3 Experimental Procedures and Finite Element Simulation

3.1 Fatigue Tests

Austenitic stainless steel was used in this study because of its good weldability and corrosion resistance. The base metals (BMs) used for comparison were stainless steels of spot-welded bodies in railway vehicles. They were 1.4318 and 1.4318 + C850 austenitic stainless steels in EN10088-2 [34], the chemical compositions and physical mechanical properties of which are listed in Tables 2 and 3.

Table 2

Chemical compositions of 1.4318 austenitic stainless steel

Base metal	Chemical composition (wt%)
X2CrNiN18-7	C	Si	Mn	P_max.	S	Ni	Cr	N
X2CrNiN18-7	< 0.03	≤ 1	≤ 2	≤ 0.045	≤ 0.015	6–8	16.5–18.5	0.1–0.2

Table 3

Physical mechanical properties of 1.4318 and 1.4318+C850 austenitic stainless steels

Base metal	Number	Density (kg/m³)	Poisson’s ratio	Yield strength (MPa)	Tensile strength (MPa)
X2CrNiN18-7	1.4318	7850	0.3	330	630
X2CrNiN18-7	1.4318 + C850	7850	0.3	500	1010

Tensile–shear fatigue tests of spot-welded specimens with different sheet thicknesses were conducted under two load ratios (r = 0.1 and 0.5). The commonly used sheet thickness combinations were 0.8 + 1.2, 0.8 + 2.5, 1.5 + 1.5, 1.5 + 2.0, and 2.0 + 2.0. Except for the sheet thickness and welding nugget diameter, other main parameters such as shape and length remained constant. The shape and dimensions of spot-welded specimens are shown in Figure 3. The welding nugget diameters and chamfer circle radii of different sheet thicknesses are given in Table 4. As shown in Figure 4, the tensile-shear tests were performed using a RUMUL TESTRONIC high-frequency testing machine (Switzerland).

Table 4

Welding nugget diameters and chamfer circle radius of specimens

Specimen thicknesses t (mm)		Welding nugget diameter Φd (mm)	Chamfer circle radius R (mm)
t₁	t₂	Welding nugget diameter Φd (mm)	R₁	R₂
0.8	1.2	4.5	4.0	4.0
0.8	2.5	4.5	4.0	5.0
1.5	1.5	6.0	4.0	4.0
1.5	2.0	6.0	4.0	5.0
2.0	2.0	6.0	5.0	5.0

Five kinds of spot-welded specimens were tested on a high-frequency fatigue testing machine. The fatigue data of the specimens with 1.5 + 1.5 mm thickness combination under two load ratios (r = 0.1 and 0.5) were obtained from the tensile–shear fatigue testing, and the other specimens were only loaded under one load ratio (r =0.5). All fatigue test results are distinguished according to the different load ratios and sheet thickness combinations to draw a $\Delta F_{a} {-}N$ (load range–life) scatter plot (Figures 5 and 6).

As can be seen from Figure 6, for the spot-welded specimen with 1.5 + 1.5 mm thickness combination, the data under the load ratio r = 0.1 are more dispersed than those under r = 0.5 because of the influence of the average load. When the load range is constant, as the load ratio r increases, the average load value also increases, which causes the increase of tensile load in the cyclic load. This is very favorable for the initiation and propagation of fatigue cracks and can reduce fatigue life. Therefore, the effect of the load ratio on fatigue strength needs to be considered.

3.2 Finite Element Simulation

The finite element model of the spot-welded structure was established according to the actual structural dimension of the specimen, as shown in Figure 7. Neutral shell elements were used to simulate the two connected sheets, and a single rigid CBAR beam element was used to simulate the weld nugget. The sheet thickness of the specimens was defined as t₁ + t₂, and the diameter of the weld nugget was assumed to be $\varPhi d$ in the finite element model.

For each loading case under the load ratio r and load range $\Delta F_{a}$, the maximum load F_max and the minimum load F_min were loaded into the finite element model.

The loaded model was imported into NASTRAN for calculation, and the forces and moments of the beam element nodes under F_max and F_min were obtained. Then, the results were substituted into Eqs. (1)–(7) to obtain the structural stress of the spot-welded specimens based on the tensile–shear force calculation. In Figure 8, A and B represent the nodes at the two ends of the beam element.

3.3 Fitting the S–N Curve

The fatigue life values of spot-welded specimens were obtained in actual fatigue tests, and the structural stress range ∆σ_s was calculated according to the structural stress equations based on the finite element simulation under the tensile–shear load. By taking the structural stress range ∆σ_s as the ordinate and the fatigue life N as the abscissa, the double logarithmic model and the least-squares method were used to fit the fatigue data by linear regression analyses under different loading ratios (r = 0.1 and 0.5). Consequently, the S–N curves of spot-welded specimens were obtained (Figures 9 and 10). The governing equations from the regression analyses are shown in each figure.

The values of the correlation coefficient squared (R²) under two load ratios (r = 0.1 and 0.5) and one load ratio (r=0.5) were 0.6582 and 0.8445, respectively. There is a significant change in R² under different loading ratios. Therefore, the influence of the load ratio on the fatigue performance should be distinguished in the research process.

According to the linear regression results under the load ratio r = 0.5, the equation for fatigue life evaluation of the spot-welded specimens was obtained by fitting as

$$y = - 0.1694x + 3.2506,$$

(8)

where $y = \lg \Delta \sigma_{\text{s}}$ (the equivalent structural stress range) and $x = \lg N$ (the fatigue life).

According to the fitted S–N curve equation and the test data of spot welding, the residual standard deviation σ=0.05097 was calculated. The results prove that the predicted life of the curve deviates little from the test life and that the predicted result of the regression model is good.

According to the fitted S–N curve of the spot-welded specimen obtained by linear regression, with the life obtained by the test as the abscissa and the predicted life as the ordinate, the five lifespans used to predict the fatigue life are plotted, as shown in Figures 11 and 12.

Figure 11 shows that most data points fall within five lifespans with the exception of a few points. Figure 12 shows that all the data points fall within five lifespans, and the prediction result is better than that of Figure 11. It can be seen that the load ratio has a great influence on the fatigue characteristics of the base metal of the spot-welded specimen and so the fatigue data under different load ratios should be considered separately.

4 Results and Discussion

4.1 Structural Stress Calculation with Correction Coefficients

As shown in Figure 2, by taking sheet 1 as an example, the structural stress equation after introducing the correction coefficient can be expressed by

$$\begin{aligned} \sigma_{v1} = - \sigma_{\text{max} } \left( {F_{x1} } \right)\cos \theta - \sigma_{\text{max} } \left( {F_{y1} } \right)\sin \theta + \sigma_{\text{max} } \left( {F_{z1} } \right) \hfill \\ + \sigma_{\text{max} } \left( {M_{x1} } \right)\sin \theta - \sigma_{\text{max} } \left( {M_{y1} } \right)\cos \theta , \hfill \\ \end{aligned}$$

(9)

where

$$\sigma_{\text{max} } \left( {F_{x1} } \right) = \frac{{F_{x1} }}{{\pi ds_{1} }} \times SFFXY \times d^{DEFXY} \times s_{1}^{TEFXY} ,$$

(10)

$$\sigma_{\text{max} } \left( {F_{y1} } \right) = \frac{{F_{y1} }}{{\pi ds_{1} }} \times SFFXY \times d^{DEFXY} \times s_{1}^{TEFXY} ,$$

(11)

$$\sigma_{\text{max} } \left( {M_{x1} } \right) = \left( {\frac{{1.872M_{x1} }}{{ds_{1}^{2} }}} \right) \times SFMXY \times d^{DEMXY} \times s_{1}^{TEMXY} ,$$

(12)

$$\sigma_{\text{max} } \left( {M_{y1} } \right) = \left( {\frac{{1.872M_{y1} }}{{ds_{1}^{2} }}} \right) \times SFMXY \times d^{DEMXY} \times s_{1}^{TEMXY} ,$$

(13)

$$\sigma_{\text{max} } \left( {F_{z1} } \right) = \left( {\frac{{1.744F_{z1} }}{{s_{1}^{2} }}} \right) \times SFFZ \times d^{DEFZ} \times s_{1}^{TEFZ} .$$

(14)

In the structural stress solution equations for spot welding, nine parameters were introduced to modify the stress results obtained by the shear force, axial force, and bending moment. At present, the default initial values are mainly used in the project to solve for the spot-welding structural stress in steel. The default values of these parameters are given in Table 5.

Table 5

Initial correction parameters (C1)

SFFXY	SFFZ	SFMXY
1	0.6	0.6
DEFXY	DEFZ	DEMXY
0	0	0
TEFXY	TEFZ	TEMXY
0	0.5	0.5

The structural stress calculated after introducing the correction coefficient and the fatigue life obtained by the test were plotted and the result is shown in Figure 13. The regression analysis was performed on the spot-welding test data by using the least-squares method.

In fact, spot welding is widely used in structures of railroad vehicles and the bodies and main components of automobiles. Automobiles are mainly made of thin-walled, high-strength steel and railroad vehicles are made of austenitic stainless steel. The fatigue properties of these two kinds of spot-welding structures in the two conditions are different. The initial S–N curve is not accurate and cannot meet the requirements of the railroad vehicles. Therefore, the correction parameters should be considered, and the initial S–N curve should be optimized to obtain a new S–N curve that is more relevant and suitable for the spot-welding structures of railroad vehicles.

4.2 Correction Coefficient Optimization

According to the structural stress solution Eqs. (1)–(6), the correlation coefficient R² of the fitted S-N curve is taken as an objective function, and the variables are the nine parameters in the structural stress solution equations, the range of which is between 0 and 1. The parameter optimization program was compiled in MATLAB. In the program, the correction coefficients for the sheet thickness and welding nugget diameter are used as variables ranging from 0 to 1, whereby the structural stress S can be calculated. Then, in combination with the test fatigue life N, the correlation coefficient squared, R², can be maximized. Figure 14 shows the specific optimization flowchart.

The fmincon function of the nonlinear constrained optimization tool in MATLAB was used to control the maximum objective function. The quasi-Newton method (BFGS) [35] algorithm was used to optimize the obtained S–N curve. The S–N curve was optimized under the load ratio r = 0.5, and the optimized results are listed in Table 6.

Table 6

Optimized parameters

	Force and bending moment coefficients	Diameter coefficients	Sheet thickness coefficients
FX,FY	3.81 × 10⁻⁵	0.21	0.36
FZ	2.34 × 10⁻⁵	0.29	0.38
MX,MY	0.75	1.44 × 10⁻⁵	0.34
R²	0.8784

The initial input values of the nine parameters were modified. Then the corrected parameter values and correlation coefficient values were calculated. The results are listed in Table 7.

Table 7

Optimization results under different initial inputs

	First results	Second results	Third results
SFFXY	3.24 × 10⁻⁵	3.37 × 10⁻⁵	3.79 × 10⁻⁵
SFFZ	2.14 × 10⁻⁵	2.10 × 10⁻⁵	2.28 × 10⁻⁵
SFMXY	0.75	0.72	0.75
DEFXY	0.26	0.23	0.21
DEFZ	0.32	0.32	0.29
DEMXY	1.44 × 10⁻⁵	1.44 × 10⁻⁵	1.44 × 10⁻⁵
TEFXY	0.41	0.39	0.4
TEFZ	0.41	0.39	0.39
TEMXY	0.34	0.34	0.34
R²	0.8784	0.8784	0.8784

It can be seen from Table 7 that, in the case of different initial values, the nine corrected parameters have little difference, and the correlation coefficient has no change, which indicates that the optimization procedure is correct and the obtained results are the optimal solutions in this interval.

The first two rows of the optimization results were shear force and axial force parameters. The values are close to zero. When these values are put into the formulas of the structural stress solution, the obtained $\sigma_{\text{max} } \left( {F_{x} } \right)$ and $\sigma_{\text{max} } \left( {F_{y} } \right)$ are also close to zero. This means that the influence of the shear force and the axial force on structural stress has been ignored, which is incorrect. In response to this problem, three specific optimization methods were performed.

4.2.1 Force and Moment Correction (C2)

In reference to Eqs. (9)–(14) for the correction of the welding nugget diameter and sheet thickness, the correction of the force and moment can be expressed as

$$\sigma_{\text{max} } \left( {F_{x1} } \right) = \frac{{F_{x1} }}{{\pi ds_{1} }} \times \left| {F_{x1} } \right|^{SFFXY} \times d^{DEFXY} \times s_{1}^{TEFXY} ,$$

(15)

$$\sigma_{\text{max} } \left( {F_{y1} } \right) = \frac{{F_{y1} }}{{\pi ds_{1} }} \times \left| {F_{y1} } \right|^{SFFXY} \times d^{DEFXY} \times s_{1}^{TEFXY} ,$$

(16)

$$\sigma_{\text{max} } \left( {M_{x1} } \right) = \left( {\frac{{1.872M_{x1} }}{{ds_{1}^{2} }}} \right) \times \left| {M_{x1} } \right|^{SFMXY} \times d^{DEMXY} \times s_{1}^{TEMXY} ,$$

(17)

$$\sigma_{\text{max} } \left( {M_{y1} } \right) = \left( {\frac{{1.872M_{y1} }}{{ds_{1}^{2} }}} \right) \times \left| {M_{y1} } \right|^{SFMXY} \times d^{DEMXY} \times s_{1}^{TEMXY} ,$$

(18)

$$\sigma_{\text{max} } \left( {F_{z1} } \right) = \left( {\frac{{1.744F_{z1} }}{{s_{1}^{2} }}} \right) \times \left| {F_{z1} } \right|^{SFFZ} \times d^{DEFZ} \times s_{1}^{TEFZ} .$$

(19)

According to Eqs. (15)–(19), the S–N curve of spot welding under load ratio r = 0.5 was re-optimized. The results of parameter optimization are listed in Table 8.

Table 8

Parameter optimization results (C2)

SFFXY	SFFZ	SFMXY
0.0456	1.07 × 10⁻⁵	0.023
DEFXY	DEFZ	DEMXY
2.77 × 10⁻⁵	2.65 × 10⁻⁵	1.44×10⁻⁵
TEFXY	TEFZ	TEMXY
4.58 × 10⁻⁵	7.95 × 10⁻⁵	4 × 10⁻⁴

The optimized results were brought into the structural stress equations to re-solve for the structural stress. The S–N curve equation of the spot-welded specimen under tensile–shear load is $y = 0.17493x + 3.4901,$ with R² = 0.8906.

4.2.2 Force and Moment Correction with Initial Empirical Coefficient K₁ (C3)

Based on Eqs. (9)–(11), the initial empirical correction coefficient K₁ was introduced, and the structural stress equations are as follows:

$$\sigma_{\text{max} } \left( {F_{x1} } \right) = \frac{{F_{x1} }}{{\pi ds_{1} }} \times \left| {F_{x1} } \right|^{SFFXY} \times d^{DEFXY} \times s_{1}^{TEFXY} ,$$

(20)

$$\sigma_{\text{max} } \left( {F_{y1} } \right) = \frac{{F_{y1} }}{{\pi ds_{1} }} \times \left| {F_{y1} } \right|^{SFFXY} \times d^{DEFXY} \times s_{1}^{TEFXY} ,$$

(21)

$$\sigma_{\text{max} } \left( {M_{x1} } \right) = K_{1} \times \left( {\frac{{1.872M_{x1} }}{{ds_{1}^{2} }}} \right) \times \left| {M_{x1} } \right|^{SFMXY} \times d^{DEMXY} \times s_{1}^{TEMXY} ,$$

(22)

$$\sigma_{\text{max} } \left( {M_{y1} } \right) = K_{1} \times \left( {\frac{{1.872M_{y1} }}{{ds_{1}^{2} }}} \right) \times \left| {M_{y1} } \right|^{SFMXY} \times d^{DEMXY} \times s_{1}^{TEMXY} ,$$

(23)

$$\sigma_{\text{max} } \left( {F_{z1} } \right) = K_{1} \times \left( {\frac{{1.744F_{z1} }}{{s_{1}^{2} }}} \right) \times \left| {F_{z1} } \right|^{SFFZ} \times d^{DEFZ} \times s_{1}^{TEFZ} .$$

(24)

According to Eqs. (20)–(24), the S–N curve of spot welding under load ratio r = 0.5 was re-optimized. The parameter optimization results are listed in Table 9.

Table 9

Parameter optimization results (C3)

SFFXY	SFFZ	SFMXY
0.02	5.95 × 10⁻⁷	4.11 × 10⁻⁷
DEFXY	DEFZ	DEMXY
2.46 × 10⁻⁶	1.92 × 10⁻⁶	1.04 × 10⁻⁶
TEFXY	TEFZ	TEMXY
1.17 × 10⁻⁶	3.28 × 10⁻⁶	7.06 × 10⁻⁷

The optimized results were brought into the structural stress equations to re-solve for the structural stress. The S–N curve equation of the spot-welded specimen under tensile-shear load is $y = 0.16948x + 3.2811,$ with R² = 0.8573.

4.2.3 Welding Nugget Diameter and Sheet Thickness Correction (C4)

The coefficients for the force and moment in Table 4 were used to change the other six parameters, such as the welding nugget diameter and sheet thickness in the equations, and the structural stress equations are as follows:

$$\sigma_{\text{max} } \left( {F_{x1} } \right) = \frac{{F_{x1} }}{{\pi ds_{1} }} \times d^{DEFXY} \times s_{1}^{TEFXY} ,$$

(25)

$$\sigma_{\text{max} } \left( {F_{y1} } \right) = \frac{{F_{y1} }}{{\pi ds_{1} }} \times d^{DEFXY} \times s_{1}^{TEFXY} ,$$

(26)

$$\sigma_{\text{max} } \left( {M_{x1} } \right) = \left( {\frac{{1.872M_{x1} }}{{ds_{1}^{2} }}} \right) \times d^{DEMXY} \times s_{1}^{TEMXY} ,$$

(27)

$$\sigma_{\text{max} } \left( {M_{y1} } \right) = \left( {\frac{{1.872M_{y1} }}{{ds_{1}^{2} }}} \right) \times d^{DEMXY} \times s_{1}^{TEMXY} ,$$

(28)

$$\sigma_{\text{max} } \left( {F_{z1} } \right) = \left( {\frac{{1.744F_{z1} }}{{s_{1}^{2} }}} \right) \times d^{DEFZ} \times s_{1}^{TEFZ} .$$

(29)

According to the structural stress Eqs. (25)–(29), the S–N curve of spot welding under load ratio r = 0.5 was re-optimized. The parameter optimization results are listed in Table 10.

Table 10

Parameter optimization results (C4)

DEFXY	DEFZ	DEMXY
1.84 × 10⁻⁵	3.49 × 10⁻⁵	0.13
TEFXY	TEFZ	TEMXY
2.3 × 10⁻⁴	1.5 × 10⁻⁴	2 × 10⁻⁴

Comparing Figure 13 with Figures 15, 16, 17, it can be found that, after three types of corrections, the correlation coefficients of the spot-welding S–N curves increased, and all the test data points fall within five lifespans.

The results of the four optimization methods and the optimization parameters are listed in Table 11 and Table 12, respectively. C1 has no optimization. C2 has the removal of the initial empirical coefficient K₁ and the introduction of the force and moment correction. C3 has the retention of the initial empirical coefficient K₁ and the introduction of the force and moment correction. C4 has the correction of the welding nugget diameter and sheet thickness.

Table 11

Results of four optimization methods

Optimization methods	S–N curve	R²
C1	lg S = − 0.1694 lg N + 3.2506	0.8445
C2	lg S = − 0.17493 lg N + 3.4901	0.8906
C3	lg S = − 0.16948 lg N + 3.2811	0.8573
C4	lg S = − 0.1704 lg N + 3.26216	0.8874

Table 12

Optimization parameters of four optimization methods

Optimization method	C1	C2	C3	C4
SFFXY	1	0.0456	0.02	‒
SFFZ	0.6	1.07 × 10⁻⁵	5.95 × 10⁻⁷	‒
SFMXY	0.6	0.023	4.11 × 10⁻⁷	‒
DEFXY	0	2.77 × 10⁻⁵	2.46 × 10⁻⁶	1.84 × 10⁻⁵
DEFZ	0	2.65 × 10⁻⁵	1.92 × 10⁻⁶	3.49 × 10⁻⁵
DEMXY	0	1.44 × 10⁻⁵	1.04 × 10⁻⁶	0.13
TEFXY	0	4.58 × 10⁻⁵	1.17 × 10⁻⁶	2.30 × 10⁻⁴
TEFZ	0.5	7.95 × 10⁻⁵	3.28 × 10⁻⁶	1.50 × 10⁻⁴
TEMXY	0.5	4.00 × 10⁻⁴	7.06 × 10⁻⁷	2.00 × 10⁻⁴

The S–N curves of the four optimization methods were compared, as shown in Figure 18. It can be seen that C3 and C4 are close to the original curve, whereas C2 exhibits an obvious difference.

5 Conclusions

According to the fatigue test results, the following conclusions can be drawn by analyzing the fatigue failure characteristics of spot-welded specimens.

With the value of the correlation coefficient squared, R², as the objective function, three optimization methods are proposed to optimize the S–N curves under the load ratio r = 0.5. After three corrections, the S–N curve correlation coefficient of the spot-welding structure is increased. The data points are compact and all of them fall within five lifespans. The optimization effect is remarkable, and the obtained S–N curves can be used to predict the fatigue life.

The S–N curves obtained in this study are applicable to the fatigue lives of spot-welded structures under the load ratio r = 0.5, a base metal of EN1.4318, and sheet thicknesses of 0.8‒2.5 mm.

When the types of loads, diameters and sheet thicknesses are various in the test, using C2 optimization is recommended; if the load type is relatively limited, C4 is recommended for optimization; if the test data are relatively limited, using C3 optimization is recommended.

Acknowledgements

Not applicable.

Competing interests

The authors declare no competing financial interests.

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Title: Structural Stress–Fatigue Life Curve Improvement of Spot Welding Based on Quasi-Newton Method
Authors: Yahang Qin
Shoune Xiao
Liantao Lu
Bing Yang
Xiangjie Li
Guangwu Yang
Publication date: 01-12-2020
Publisher: Springer Singapore
Published in: Chinese Journal of Mechanical Engineering / Issue 1/2020
Print ISSN: 1000-9345
Electronic ISSN: 2192-8258
DOI: https://doi.org/10.1186/s10033-020-00453-3

Springer Professional

Structural Stress–Fatigue Life Curve Improvement of Spot Welding Based on Quasi-Newton Method

Abstract

1 Introduction

2 Fatigue Analysis Theory

3 Experimental Procedures and Finite Element Simulation

3.1 Fatigue Tests

3.2 Finite Element Simulation

3.3 Fitting the S–N Curve

4 Results and Discussion

4.1 Structural Stress Calculation with Correction Coefficients

4.2 Correction Coefficient Optimization

4.2.1 Force and Moment Correction (C2)

4.2.2 Force and Moment Correction with Initial Empirical Coefficient K₁ (C3)

4.2.3 Welding Nugget Diameter and Sheet Thickness Correction (C4)

5 Conclusions

Acknowledgements

Competing interests

Premium Partners

Springer Professional

Abstract

1 Introduction

2 Fatigue Analysis Theory

3 Experimental Procedures and Finite Element Simulation

3.1 Fatigue Tests

3.2 Finite Element Simulation

3.3 Fitting the S–N Curve

4 Results and Discussion

4.1 Structural Stress Calculation with Correction Coefficients

4.2 Correction Coefficient Optimization

4.2.1 Force and Moment Correction (C2)

4.2.2 Force and Moment Correction with Initial Empirical Coefficient K1 (C3)

4.2.3 Welding Nugget Diameter and Sheet Thickness Correction (C4)

5 Conclusions

Acknowledgements

Competing interests

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4.2.2 Force and Moment Correction with Initial Empirical Coefficient K₁ (C3)