Abstract
An experimental and numerical investigation of fatigue life and crack propagation in two-dimensional perforated aluminum structures is presented. Specifically, the performance of positive Poisson’s ratio (PPR) geometries using circular holes is compared to that of auxetic stop-hole and straight-groove hole geometries. Mechanical fatigue testing shows that the considered auxetic structures have more than 20% longer life than the porous PPR structure at the same porosity and peak effective maximum stress despite having holes with larger stress concentrations. Digital image correlation is used to detect crack initiation and damage propagation much earlier than can be detected by the unaided eye. Accompanying finite element analyses reveal that auxetic structures have the advantage over their PPR counterparts by delaying crack initiation, spreading damage over a larger area, and having a stress intensity factor that decreases over a significant range of crack lengths. In addition, numerical simulations suggest that auxetic structures maintain their negative Poisson’s ratios in the presence of cracks.
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Abbreviations
- Δ J :
-
Cyclic component of the J-integral
- Δ K :
-
Nominal stress intensity factor range
- 〈𝜖xx〉,〈𝜖yy〉:
-
Local average strains in test sample finite element analysis
- 〈ux〉L, 〈ux〉R, 〈uy〉T, 〈uy〉B :
-
Average boundary displacements in test sample finite element analysis
- \(\bar {\mathbf {\varepsilon }}\) :
-
Average infinitesimal strain tensor in periodic finite element analysis
- u(x, y):
-
Displacement vector in periodic finite element analysis
- u∗(x, y):
-
Deviation in displacement vector away from average in periodic finite element analysis
- uT, uB, uL, uR :
-
Representative volume element boundary displacement vectors in periodic finite element analysis
- x :
-
Position vector in periodic finite element analysis
- xT, xB, xL, xR :
-
Representative volume element boundary positions in periodic finite element analysis
- ν e f f :
-
Effective Poisson’s ratio
- σ a :
-
Fatigue stress amplitude
- σ f :
-
Reduced fatigue endurance limit
- σ m :
-
Mean fatigue stress
- σ r :
-
Standard reference fatigue endurance limit
- σ m a x :
-
Maximum applied fatigue stress
- σ m i n :
-
Minimum applied fatigue stress
- σ T S :
-
Ultimate tensile strength
- a :
-
Crack length
- D, n :
-
Material constants used in Paris’ Law
- \(D^{\prime }, n^{\prime }\) :
-
Material constants used in Dowling and Begley’s fatigue crack growth Law
- E :
-
Young’s modulus
- f :
-
Width of void slot in stop-hole-void samples
- g :
-
Stop-hole void center-to-center distance
- G 0 :
-
Strain energy release rate
- J :
-
The value of the J-integral
- K :
-
Stress intensity factor
- K f :
-
Fatigue notch strength reduction factor
- K i :
-
Miscellaneous fatigue strength reduction factors
- K t :
-
Stress concentration factor
- Kmax,Kmin :
-
Maximum and minimum stress intensity factor values, respectively
- L :
-
Representative volume element void center-tocenter length, i.e. half the width of the representative volume element
- L m i n :
-
Minimum distance between two consecutive voids
- m :
-
Radius of stop-holes in stop-hole-void samples
- N :
-
Fatigue loading cycle number
- p :
-
Length of straight-groove void slot
- q :
-
Length of stop-hole-void slots
- q f :
-
Fatigue notch sensitivity factor
- R :
-
Fatigue stress ratio, \(\frac {\sigma _{min}}{\sigma _{max}}\)
- s :
-
Width of slot in straight-groove-void samples
- t :
-
Radius of circular voids in circular-void samples
- \(u_{x}^{Vp_{x}}, u_{y}^{Vp_{x}}, u_{x}^{Vp_{y}}, u_{y}^{Vp_{y}}\) :
-
Virtual point displacements in periodic finite element analysis
- Vpx,Vpy :
-
Finite element virtual points used in periodic finite element analysis
- x, y :
-
Position coordinates in periodic finite element analysis
- z :
-
Radius of void slot ends in straight-groove-void samples
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Acknowledgements
M.T., L.F., and G.D. acknowledge the support of internal grant and start-up funding from the School of Engineering at Santa Clara University.
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Appendix A: Approximation of Poisson’s ratio from FE Simulations
Appendix A: Approximation of Poisson’s ratio from FE Simulations
We present a brief summary of the approaches used to calculate the effective Poisson’s ratio in both the finite-sized and periodic RVE model based on the authors’ previous work [3].
A.1 Finite-size Model
In order to calculate the effective PR on the finite-size test sample geometries, we extracted the horizontal and the vertical displacement components from the boundary nodes of the porous 40 by 40 mm gauge area of the samples. These displacement are used to compute average displacements at the boundaries 〈ux〉L, 〈ux〉R, 〈uy〉T, and 〈uy〉B, where the superscripts L, R, T, and B denote the left, top, right, and bottom boundaries, respectively. From these average displacements, we compute local strain averages
where l denotes the distance between the top/bottom and left/right boundaries (i.e., l = 40 mm here). The effective Poisson’s ratio νeff is given by
A.2 Infinite Periodic Model
Consider a 2D periodic structure composed of an array of RVE’s. The displacement vector at any point (x, y) in the structure can be expressed as [50, 51]
where, in general, \(\bar {\mathbf {\varepsilon }}\) is the constant average displacement gradient, x is the position vector and u∗(x, y) is a periodic vector representing local deviation away from the average due to inhomogeneities (e.g., voids). We take \(\bar {\mathbf {\varepsilon }}\) to be symmetric so that it is equivalent to the average infinitesimal strain. Continuity of the periodic structure requires that both the top/bottom boundary pairs and left/right boundary pairs deform identically. Thus, for the top and bottom boundaries, we can write
where u∗ in equation (11) and (12) are the same. Subtracting these two equations gives us the continuity constraint
A similar process for the left and right boundaries yields
To apply these conditions in Abaqus, we utilize two virtual nodesVpx and Vpy. These are points unconnected to the RVE and whose spatial placement is arbitrary. The numerical values of the displacements of the two virtual nodes are set to be equivalent to components of the average strain we want to impose. Thus we write (13) and (14) as constraint equations (i.e., *EQUATION) for each periodic node pair as
where we set \(u_{x}^{Vp_{x}} = \bar {\varepsilon }_{xx}\), \(u_{y}^{Vp_{x}} = \bar {\varepsilon }_{yx}\), \(u_{x}^{Vp_{y}} = \bar {\varepsilon }_{xy}\), and \(u_{y}^{Vp_{y}} = \bar {\varepsilon }_{yy}\). Since the displacements of our virtual points correspond to the average strain in the structure, we can use them to compute an average (or effective) Poisson’s ratio for the entire structure
where \(u_{y}^{Vp_{y}}\) is a specified displacement (we use − 0.005 in this analysis) and \(u_{x}^{Vp_{x}}\) is computed by Abaqus as part of the FE analysis.
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Francesconi, L., Baldi, A., Dominguez, G. et al. An Investigation of the Enhanced Fatigue Performance of Low-porosity Auxetic Metamaterials. Exp Mech 60, 93–107 (2020). https://doi.org/10.1007/s11340-019-00539-7
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DOI: https://doi.org/10.1007/s11340-019-00539-7