Grips For A Linear Fracture Testing Machine And Method Of Designing Same

Abstract

Test fixture grips for testing quasibrittle materials, such as fiber-polymer composites are provided having increased mass and stiffness relative to standard test grips to provide for obtaining postpeak measurements. The design is based on static analysis (using the second law of thermodynamics), confirmed by dynamic analysis of the test setup as an open system. Dynamic analysis of the test setup as a closed system with PID controlled input further indicates that the controllability of postpeak softening under CMOD control is improved not only by increasing the grip stiffness but also by increasing the grip mass.

Claims

1. Grips for securing a quasi-brittle test specimen having a tangential (incremental) stiffness K<0- to the base and crosshead of a linear fracture testing machine having a frame stiffness Kin, the grips having a stiffness K.sub.g, such that the combined stiffness of the testing machine and grips K.sub.mg=1/(1/K.sub.m+1/K.sub.g), and the total stiffness of the test specimen, the testing machine and the grips K.sub.t=1/(1/K.sub.m+1/K.sub.g)+K.sub.s>0-.

2. Grips for securing a quasi-brittle test specimen having a tangential (incremental) stiffness K.sub.s<0- to the base and crosshead of a linear fracture testing machine having a frame stiffness K.sub.m, the total stiffness of the test specimen, the testing machine and the grips K.sub.t=1/(1/K.sub.m+1/K.sub.g)+K.sub.s>0-, such that the grips have a stiffness K.sub.g=1/(K.sub.s/K.sub.t1/K.sub.m+1/K.sub.t)>0-.

3. The grips of claim 1 wherein K.sub.m=200 MN/m, K.sub.s=0.830 MN/m, and K.sub.g=192.4 MN/m, the grips having a mass of 9.419 kg.

4. The grips of claim 2 wherein K.sub.m200 MN/m, K.sub.s=0.830 MN/m, and K.sub.g=192.4 MN/m, the grips having a mass of 9.419 kg.

5. A method for designing grips having a mass and a stiffness for a linear fracture testing machine for testing specimens having a negative incremental stiffness (K.sub.s<0) during fracture propagation comprising inputting the incremental stiffness (K.sub.s<0) of the specimen; the stiffness of the testing machine (K.sub.m>0), a mass of the specimen, a mass of the testing machine, a time delay of the testing machine, and PID parameters for the combination of the testing machine, grips and specimen, and solving $\begin{array}{cc}\left[\begin{array}{ccccc}-& 1& 0& 0& 0\\ -\frac{1}{m}.Math.\left(K_g+\frac{K_s}{x_1}\right)& -& \frac{K_g}{m}& 0& 0\\ 0& 0& -& 1& 0\\ R_1& -\frac{.Math..Math.K_M}{M}& R_2& -\frac{K_M.Math.}{M}& -\frac{\mathrm{Km}.Math..Math.}{M}-\\ 1& 0& 0& 0& -\end{array}\right]& \left(28\right)\\ R_1=\frac{K_g-.Math..Math.K_M}{M}+\frac{K_M.Math.}{M}\left[+.Math.\frac{K_s/x_1+K_g}{m}\right]& \left(29\right)\\ R_2=-\frac{K_M+K_g}{M}+\frac{.Math..Math.K_g.Math.K_M}{\mathrm{mM}}& \left(30\right)\end{array}$ so that the eigenvalues are strictly negative to determine the mass and stiffness of the grips.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0016] FIG. 1 is a simplified schematic of a universal servo-hydraulic testing machine.

[0017] FIG. 2 shows the dimensions of a 2D woven composite specimen.

[0018] FIG. 3a) depicts the experimental setup considered in the analysis, and 3b) depicts the grips designed to achieve stable post peak.

[0019] FIG. 4 is a series of four graphs of a load-point control stability analysis for various values of grip mass, m.sub.g.

[0020] FIG. 5 is a schematic of the machine and testing setup including the PI) control.

[0021] FIG. 6 is a series of graphs showing the effect of grip mass on a) an open system, b) proportional control, c) differential control, and d) integrative control.

[0022] FIG. 7 is a series of graphs showing the effect of grip stiffness on a) an open system, b) proportional control, c) differential control, and d) integrative control.

[0023] FIG. 8a) depicts a MTS standard fracture mechanics clevis grip, and FIG. 8b) depicts grips designed according to the present application and having increased stiffness and mass.

[0024] FIG. 9 are examples of typical stable load-displacement curves obtained with grips designed in accordance with the present application for carbon fiber woven composites (a) and (b) and for glass fiber textile composites (c) and (d).

[0025] FIG. 10 depicts the geometry of Single Edge Notched Tension (SENT) specimens used in the testing (units: mm).

[0026] FIG. 11 depicts a) typical load-displacement curves of [0 ].sub.8 geometrically-scaled SENT specimens of various sizes, showing decreasing nonlinearity at increasing specimen size; typical failure patterns of SENT specimens for width b) D=20 mm, c)D=40 mm, and d) D=80 mm; and e) is the magnification of the fracture surface for the large specimen showing extensive tow failure and pull-out.

[0027] FIG. 12 shows front, side, top and isometric views of a grip designed according to the present application, with dimensions in mm.

[0028] FIG. 13 comprises perspective views of grips designed using iteratively the method described herein to provide an a) an initial design, b) a second design, and c) a final design (corresponding to the grip shown in FIG. 12).

DETAILED DESCRIPTION

[0029] In the description that follows, a method for designing grips is disclosed based upon, first, a static stability analysis that identifies the minimum grip stiffness required for stability. Then a dynamic analysis of stability is presented to address issues related to the stabilization of postpeak softening of the test specimens Experiments performed to support the conclusions reached are described, and an example is presented of how the methods described herein can be used to design grips in accordance with the method.

[0030] For the purpose of static analysis, the test system can be considered as the coupling of two elements: 1) the testing machine frame of stiffness K.sub.m with the specimen grips (or fixtures) of stiffness K.sub.g forming one elastic element of stiffness K.sub.m, and 2) the test specimen, of tangential (or incremental) stiffness K.sub.s. FIG. 1 shows a schematic of the testing frame.

[0031] Based on the second law of thermodynamics, the test setup becomes unstable if the there exists a perturbing load that produces negative work W on the test setup, thus causing an increase of entropy, S (see [6, chpt. 10]). If a perturbing load P is applied, axially at the load-point of the test specimen while the system in equilibrium, the combined stiffness of the machine with the grips is K.sub.mg=1/(1/K.sub.m+1/K.sub.g) and the total stiffness K.sub.t resisting P is K.sub.mg+K.sub.s. The displacement under P in the direction of P is v=P/K.sub.t, and

[00001]$\begin{array}{cc}.Math..Math.W=-T.Math..Math..Math..Math.S=\frac{1}{2}.Math..Math..Math.P.Math..Math..Math..Math.=\frac{1}{2}.Math.{K_t\left(\right)}^2& \left(1\right)\end{array}$

where T=absolute temperature. The equilibrium of the system is stable if and only if W>0, which requires that K.sub.t>0 or

[00002]$\begin{array}{cc}{K}_t=\frac{1}{1/K_m+1/K_g}+K_s>0& \left(2\right)\end{array}$

[0032] Considering a typical 20 ton testing machine (e.g., MTS) used in the testing of composites and a typical compact tension specimen consisting of 24 layers of woven carbon fiber epoxy composites for a total thickness of 5.4 mm (see FIG. 2), the typical characteristics are: [0033] Machine frame stiffness: K.sub.m=260 MN/m; [0034] Stiffness of standard specimen grips: K.sub.g=0.768 MN/nm; [0035] The steepest slope of the measured postpeak load-deflection curve of the test specimen: K.sub.s=0.830 MN/m; [0036] Mass of machine frame: m.sub.m=500 kg; [0037] Mass of grips (or fixtire m.sub.g=0.919 kg; [0038] Characteristic halftime of machine hydraulics delay: =0.02 s (de-fined as the time to approach halfway to a suddenly changed setting of electronic control).
Using these value, from Eq. (2), it is determined that

K.sub.t=0.06426 MN/m<0(3)

i.e., the tested specimen is unstable. This would suggest that it is impossible to observe gradual postpeak softening in tensile tests of fiber composites.

[0039] However, this does not take into account the effect of grip stiffness. It has generally been assumed that the standard grips provided by the manufacturers are stiff enough. But comparison of K.sub.g with K.sub.m suggests otherwise. It was, therefore, decided to produce grips (FIG. 3), with the following stiffness and mass;

[0040] {tilde over (K)}.sub.g=192.4 MN/m(=74% K.sub.m)

[0041] {tilde over (m)}.sub.g=9.419 kg (=10 m.sub.g)

Compared to the current standard grips, they are about 10-times heavier and 250-times stiffer. Eq. (2) gives:

K.sub.t=109.6 MN/m>0(4)

By which stability is achieved.

[0042] Using these grips, the composite compact tension specimens (FIG. 3) exhibited stable progressive softening, and not only under CMOD control but also under load-point control. The grips overcame the feature that the fracture energy G.sub.f deduced from the size effect tests was much larger than the maximum possible area under a snapback curve. In fact, the area indicated by G.sub.f required a rather gradual progressive softening, and this is what is now observed with the new grips.

[0043] From Eq. (2), one can obtain the minimum grip stiffness, necessary for stability, based on the estimated steepest postpeak slope K.sub.s:

[00003]$\begin{array}{cc}{\left[K_g\right]}_{\min }=\frac{1}{1/{.Math.K_s.Math.}_{\max }-1/K_m}.Math..Math.\left(K_s<0\right)& \left(5\right)\end{array}$

Thus, using the static analysis above, and by manipulation of Equation (5), grips according to the present disclosure have a tangential (incremental) stiffness K.sub.s<0- to the base and crosshead of a linear fracture testing machine having a frame stiffness K.sub.m, the grips having a stiffness K.sub.g, such that the combined stiffness of the testing machine and grips K.sub.mg=1/(1/K.sub.m+1/K.sub.g), and the total stiffness of the test specimen, the testing machine and the grips K.sub.t=1/(1/K.sub.m+1/K.sub.g)+K.sub.s>0-, and the grips have a stiffness K.sub.g=1/(K.sub.s/K.sub.t1/K.sub.m+1/K.sub.t)>0-.

[0044] Postpeak softening has typically been stabilized by controlling the Crack Mouth (or Crack Tip) Opening Displacement (CMOD or CTOD). If w is the relative displacement across the crack mouth or across the crack-tip region, and F denotes a fictitious force working on w (although in reality F=0), the incremental (or tangential) cross compliance C.sub.sc between the load, P, and displacement w is derived by considering the relations:

du=C.sub.sdP+C.sub.scdF(6)

dw=C.sub.scdP+C.sub.ccdF(7)

[0045] where P=applied force; C.sub.s=1/K.sub.S=direct (load-point) incremental (or tangential) compliance of the specimen. According to the LEFM [7, e.g.],

[00004]$\begin{array}{cc}{C}_{\mathrm{sc}}=\frac{2}{{\mathrm{bDE}}^{}}.Math.{}_0^{}.Math.k\left({}^{}\right).Math.k_c\left({}^{}\right).Math.d.Math..Math.{}^{}& \left(8\right)\end{array}$

[0046] where =/D, =crack length, D), b=specimen dimension (or size) and width; k(),k.sub.c()=dimensionless stress intensity factors due to applied load P and to fictitious load F; k=K.sub.IbD/P where K.sub.I=actual stress intensity factor; for plane stress E=E=Young's modulus, and for plane strain E=E/(1.sup.2) where =Poisson ratio. Because F=0, Eqs. (6)-(7) reduce to du=C.sub.SdP and dw=C.sub.scdP or

[00005]$\begin{array}{cc}\mathrm{du}=r_{\mathrm{sc}}.Math.\mathrm{dw},r_{\mathrm{sc}}=\frac{C_s}{C_{\mathrm{sc}}}& \left(9\right)\end{array}$

The same equations apply to CTOD control, if w is redefined as the crack tip opening displacement.

[0047] The advantage of using CMOD or CTOD control is that, during the fracture test, w always increases. So, by controlling w, the postpeak softening can be measured even if the specimen is unstable under load-point control. But there is a caveatthe response of testing machine with its hydraulics must be fast enough. For notched concrete and rock specimens tested in the servo-controlled stiff machines introduced since 1963 it has been fast enough. But for strong and very light specimens, such as those of woven laminates, it has not been fast enough, since all the attempts to measure the postpeak by means of CMOD of CTOD control have failed. A dynamic analysis of stability (as thermodynamics applies to equilibrium states only) explains why.

[0048] The inability to obtain a stable postpeak softening under CMOD or CTOD control has been attributed to an unspecified peculiar property of composites. However, the obtaining of a stable postpeak with the grips obtained by the static analysis described above shows that there is nothing peculiar in the material behavior of composites. The most likely explanation of why CMOD alone cannot control the postpeak test is that the response of hydraulics is not fast enough (even with the optimal PID setting). A dynamic analysis of the test setup, first as an open system, confirms this.

[0049] The test setup may be idealized as shown in FIG. 1, where u(t) is the load-point displacement of the test specimen; v(t) is the displacement at the attachment of the grips (or fixture) to the loading frame, and y(t) is the input from the electronic control, representing the prescribed load-displacement history (t=time). The effective mass of the machine frame is denoted as M, and the mass of the grips as m.sub.g, including the mass of the specimen (which is, however, negligible in the case of composites). The mass and stiffness of the load cell are considered to be included in M and K.sub.M.

[0050] To control the test, the controller of the machine sends a signal to the servo-valve. The hydraulic pressure on the piston increases and the piston moves, but not immediately. The halftime, r, of the hydraulics response delay, , which is of the order of 0.02 s (and is assumed to correspond to the optimized PID setting), may be modeled by a damper of viscosity constant

=K.sub.m(10)

[0051] Because the system can be considered incrementally linear, it will suffice to analyze the response to a sudden unit change of y, i.e., y=1(t) where H denotes the Heaviside step function. Because only infinitely small increments are considered, the response may be considered to be linear and K.sub.S to be constant, characterizing the steepest postpeak slope of the postpeak load displacement curve (K.sub.S<0). We also assume that no unloading would occur (because, for unloading, K.sub.S would switch to a positive value).

[0052] The equations of motion can be derived from the Lagrange equations:

[00006]$\begin{array}{cc}\frac{}{t}.Math.\left(\frac{L}{\stackrel{.}{}}\right)-\frac{L}{}+\frac{}{\stackrel{.}{}}=0& \left(11\right)\\ \frac{}{t}.Math.\left(\frac{L}{\stackrel{.}{u}}\right)-\frac{L}{u}+\frac{}{\stackrel{.}{u}}=0& \left(12\right)\\ \mathrm{where}.Math..Math.L=T-V& \left(13\right)\\ T=\frac{1}{2}.Math.M.Math.{\stackrel{.}{}}^2+\frac{1}{2}.Math.m_g.Math.{\stackrel{.}{u}}^2& \left(14\right)\\ V=\frac{1}{2}.Math.{K_M\left(-y\right)}^2+\frac{1}{2}.Math.{K_g\left(-u\right)}^2+\frac{1}{2}.Math.K_s.Math.u^2& \left(15\right)\\ =\frac{1}{2}.Math.K_M.Math.{\left(\stackrel{.}{}-\stackrel{.}{y}\right)}^2& \left(16\right)\end{array}$

[0053] where the superior dots denote derivatives with respect to time t. Eqs. (11) and (12) yield the following equations of motion:

M{umlaut over (v)}K.sub.M(vy)+K.sub.M({dot over (v)}{dot over (y)})+K.sub.g(vu)=0(17)

m.sub.g+K.sub.g(uv)+K.sub.su=0(18)

[0054] where K.sub.M was substituted. It is convenient to rewrite the equations of motion in the phase space by introducing new variables:

x.sub.1=u, x.sub.2=, x.sub.3=v, x.sub.4={dot over (v)}(19)

[0055] Substitution into the equations of motion gives a system of first-order ordinary linear differential equations in matrix form:

[00007]$\begin{array}{cc}\left\{\begin{array}{c}{\stackrel{.}{x}}_1\\ {\stackrel{.}{x}}_2\\ {\stackrel{.}{x}}_3\\ {\stackrel{.}{x}}_4\end{array}\right\}=\left[\begin{array}{cccc}0& 1& 0& 0\\ -\frac{K_g+K_s}{m_g}& 0& -\frac{K_g}{m_g}& 0\\ 0& 0& 0& 1\\ \frac{K_g}{M}& 0& -\frac{K_M+K_g}{M}& -\frac{K_M.Math.}{M}\end{array}\right].Math.\left\{\begin{array}{c}{x}_1\\ x_2\\ x_3\\ x_4\end{array}\right\}+\left\{\begin{array}{c}0\\ 0\\ 0\\ \frac{K_M}{M}.Math.y+\frac{K_M.Math.}{M}.Math.\stackrel{.}{y}\end{array}\right\}& \left(20\right)\end{array}$

[0056] The homogeneous part of this first-order matrix differential equation is satisfied by functions of the form x.sub.n=a.sub.ne.sup.t (n=1, 2, 3, 4). Substitution into the homogeneous part of the foregoing matrix differential equation yields a homogeneous matrix algebraic equation for the column matrix of an. It has a nonzero solution if and only if is equal to the eigenvalues of the square matrix in Eq. (20). The solution is stable if and only if, for all the eigenvalues,

Re()<0(21)

[0057] For calculations, the aforementioned machine and test properties with the standard grips is considered. Then the following column matrix of eigenvalues is calculated:

[00008]$\begin{array}{cc}\left\{\right\}=\left\{\begin{array}{c}80.65\\ -1.035.Math.{10}^4\\ -77.17\\ -53.87\end{array}\right\}& \left(22\right)\end{array}$

[0058] The presence of a positive eigenvalue, .sub.1, indicates that, with the standard grips, the test of postpeak is unstable, which means that postpeak softening cannot be observed, as is known from experience. Also note that the eigenvalues are real, which means that the stability loss is a divergence rather than flutter (oscillatory instability). Thus the static stability check in Eq. (3) is sufficient.

[0059] Now, considering the new grips of mass m.sub.g=10m.sub.g0=9.419 kg and stiffness K.sub.g=10K.sub.g0=2.6.Math.10.sup.9 N/m (FIG. 3), with all the other parameters remain the same, the calculations yield the eigenvalue matrix (with i.sup.2=1):

[00009]$\begin{array}{cc}\left\{\right\}=\left\{\begin{array}{c}-15.78+4.52.Math.i.Math.{10}^3\\ -15.78-4.52.Math.i.Math.{10}^3\\ -1.032.Math.{10}^4\\ -50.129\end{array}\right\}& \left(23\right)\end{array}$

[0060] All Re()-values are negative. So the specimen is stable, even under load-point control. This confirms the previous finding by static stability analysis, Eq. (4).

[0061] CMOD or CTOD control would work with the standard grips if the response of the controls were infinitely fast. However, with a hydraulic system this is impossible. The specimen accelerates fast in dynamic motion before the hydraulics can adjust the displacement.

[0062] The way to slow down the acceleration is to increase the mass to the grips. If the grip mass m.sub.g is increased to m.sub.g=10m.sub.g, 100m.sub.g and 1000m.sub.g, without increasing the grip stiffness, the sets of eigenvalues achieved are listed under the diagrams of FIG. 4. All of these sets include an eigenvalue with Re()>0, which means the specimens are unstablebut unstable under controlled load-point displacement.

[0063] With a view of CMOD control, the response of the system for input y(t)=H(t) (Heaviside step function) is calculated under four initial conditions u={dot over (u)}=v={dot over (v)}=0. The solution is obtained as a sum of the particular solution and a linear combination of four eigenvectors. The response curves of u(t) are plotted in the four diagrams of FIG. 4. Note that, with increasing grip mass, the time at the onset of sharp exponential acceleration of displacement u(t) (briefly onset time) greatly increases.

[0064] To compare the onset time with the performance of the hydraulics, vertical lines are plotted in FIG. 4 at time of 0.1 s, which is 5-times longer than the halftime of the hydraulics delay, by which time the CMOD control should be able to enforce the specified load-point displacement u with sufficient accuracy.

[0065] In the first diagram of FIG. 4, which corresponds to the standard (light) grips, the rise of exponential acceleration of u(t) begins much before the critical time of 0.01 s. Obviously, the controls are too slow to prevent this acceleration, which inevitably leads to sudden failure. However, as seen in the third diagram, the grip mass of 100 m.sub.g postpones the acceleration well beyond 0.1 s, and here the hydraulics controlled by the CMOD should evidently be able to impose the required load-point displacement.

[0066] According to the second diagram for 10 m.sub.g, it seems the exponential acceleration could also be prevented, but better informed analysis of the hydraulic system and trial testing may be needed. The fourth diagram, for 1000 m.sub.g, is obviously overkill.

[0067] The closed-loop control of the modern testing machines is based on a Proportional-Integrative-Differential (PID) signal of the error w.sub.Dw where w.sub.D=desired Crack Mouth Opening Displacement (CMOD) and w=CMOD measured by the extensometer; see the schematic of the control loop in FIG. 5.

[0068] Combining Eqs. (6) and (7) and integrating over a small time interval with constant tangential stiffnesses, one gets w=C.sub.sc/C.sub.su where u(0)=w(0)=0 may be assumed. Accordingly, the equations of motion of the system may be written as:

[00010]$\begin{array}{cc}\{\begin{array}{c}m.Math.\stackrel{\mathrm{.Math.}}{u}+K_g\left(u-\right)+K_s\left(u\right)=0\\ M.Math.\stackrel{\mathrm{.Math.}}{}+K_M\left[\left(,u,y\right)+.Math.\stackrel{.}{}\left(,u,y\right)\right]+K_g\left(-u\right)=0\\ \left(,u,y\right)=-y+\left(\frac{C_{\mathrm{sc}}}{C_s}.Math.u-w_D\right).Math.K_p+\left(\frac{C_{\mathrm{sc}}}{C_s}.Math.\stackrel{.}{u}-{\stackrel{.}{w}}_D\right).Math.K_D+\\ K_t.Math.{}_0^t.Math.\left(\frac{C_{\mathrm{sc}}}{C_s}.Math.u-w_D\right).Math.{\mathrm{dt}}^{}\end{array}& \left(24\right)\end{array}$

where K.sub.p is the proportional gain of the PID control, and K.sub.g is the stiffness of the grips. Introducing the transformation:

x.sub.1=u, x.sub.2={dot over (u)}, x.sub.3=v, x.sub.4={dot over (v)}, x.sub.5=x.sub.1dt(25)

the system of equations becomes:

[00011]$\begin{array}{cc}.Math.\{\begin{array}{c}{\stackrel{.}{x}}_1=x_2\\ {\stackrel{.}{x}}_2=-\frac{1}{m}\left[K_g\left(x_1-x_3\right)+K_s\left(x_1\right)\right]\\ {\stackrel{.}{x}}_3=x_4\\ {\stackrel{.}{x}}_4=-\frac{1}{M}.Math.\{K_M\left[x_3+.Math..Math.x_1+.Math..Math.x_2+.Math..Math.x_5\right]+\\ K_M.Math.\left[x_4+.Math..Math.x_2-\frac{}{m}.Math.K_g\left(x_1-x_3\right)-\frac{K_g}{m}.Math..Math..Math.x_1+.Math..Math.x_1\right]+\\ K_g\left(x_3-x_1\right)\}-K_M.Math.\left(y,w_D\right)\\ {\stackrel{.}{x}}_5=x_1\end{array}& \left(26\right)\\ .Math.\mathrm{where}& \\ .Math.=\frac{C_{\mathrm{sc}}}{C_s}.Math.K_p,=\frac{C_{\mathrm{sc}}}{C_s}.Math.K_d,=\frac{C_{\mathrm{sc}}}{C_s}.Math.K_i.Math..Math.\mathrm{and}& \\ =[y-.Math..Math.w_D-.Math.{\stackrel{.}{w}}_D-.Math.w_D.Math.{\mathrm{dt}}^{}+\left(y-.Math.{\stackrel{.}{w}}_D-.Math.{\stackrel{\mathrm{.Math.}}{w}}_D-.Math..Math.w_D\right)& \left(27\right)\end{array}$

[0069] The foregoing system is stable if the linearized system is stable [6, chpt. 3]. Stability requires that all the eigenvalues of the matrix of equations (26), given below, be negative:

[00012]$\begin{array}{cc}\left[\begin{array}{ccccc}-& 1& 0& 0& 0\\ -\frac{1}{m}.Math.\left(K_g+\frac{K_s}{x_1}\right)& -& \frac{K_g}{m}& 0& 0\\ 0& 0& -& 1& 0\\ R_1& -\frac{.Math..Math.K_M}{M}& R_2& -\frac{K_M.Math.}{M}& -\frac{\mathrm{Km}.Math..Math.}{M}-\\ 1& 0& 0& 0& -\end{array}\right]& \left(28\right)\\ \mathrm{where}& \\ R_1=\frac{K_g-.Math..Math.K_M}{M}+\frac{K_M.Math.}{M}\left[+.Math.\frac{K_s/x_1+K_g}{m}\right]& \left(29\right)\\ R_2=-\frac{K_M+K_g}{M}+\frac{.Math..Math.K_g.Math.K_M}{\mathrm{mM}}& \left(30\right)\end{array}$

[0070] The calculation results shown in FIGS. 6 and 7 show the effects of the mass and thickness of the grips, respectively. The stiffness has a big effect on stability but, at first surprisingly, the mass has none. That calls for discussion from a different viewpointcontrollability.

[0071] According to Liapunov's definition of stability [6, Sec. 3.5], the response x.sub.i(t) of a dynamic system with initial state x.sub.i.sup.0 is stable if, for an arbitrarily small positive number , there exists a positive number such that the response to any change of the initial state x.sub.i.sup.0 smaller than will never deviate from x.sub.i(t) by more than . But, in an open system with active input y(t), what matters is the controllability.

[0072] A state x.sub.i is controllable at time t if there exists an input y(t) that transfers the state x.sub.i(t) from x.sub.i to the specified state x.sub.i within some finite time interval t. If this is true for all t, the system is controllable. Generally, a stable system is controllable, but a system can be controllable even if it is unstable (note that modern aircraft fly with wings that are unstable but controllable), while, as we showed, the mass has no effect on stability, it has a big effect on controllability, as is obvious from FIG. 4. The following five observations can be made: [0073] 1. Although increasing the mass of the grips decreases the most critical eigenvalue (a tenfold increase of m.sub.g reduces the most critical eigenvalue by 70%), stability can be reached only with infinite mass. [0074] 2. The proportional gain of the PID control, K.sub.p, is the one having the greatest effect on stability. Increasing the mass of the grips does not increase the range of values of K.sub.p leading to stability. [0075] 3. The derivative and integrative gains play a secondary role in stability compared to the proportional gain. Increasing m.sub.g does not have a very significant effect on these parameters. [0076] 4. A huge effect of grip stiffness stability (exemplified here by stability attainment, even without CMOD control, with a mere 9% stiffness increase) is not the only effect of grip stiffness, K.sub.g. A further effect is a significant contribution to the proportional gain. Increasing the stiffness by 2% reduces the minimum value of K.sub.p leading to stability by 80%, thus making the test control much easier. [0077] 5. On the other hand, the grip stiffness does not have a strong effect on the integrative and derivative gains.

Experimental Verification of Stable Postpeak Softening of Compact Tension Specimens

[0078] FIG. 3 shows the compact-tension fracture specimen of woven carbon-epoxy specimens used to study the postpeak behavior and determine the fracture energy G.sub.f of the material and the general view of the test setup in a MTS testing machine.

[0079] FIG. 8 shows the photos of the current standard grips (on the left) and of the proposed massive grips (on the right) that successfully stabilized the postpeak.

[0080] FIG. 9 demonstrates several stable postpeak load-delection diagrams measured with the proposed stiff grips on the compact-tension specimens.

Agreement of G.sub.f from Size Effect Tests with G.sub.f from the Area Under Complete Load-Displacement Curve

[0081] The area A under the complete stable load-displacement curve of the fracture specimen allows determining the fracture energy, G.sub.f, of the material; G.sub.f=A/Lb where l=length of the broken ligament and b=specimen thickness (provided that energy dissipation outside the fracture is negligible).

[0082] Another, easier, way to determine the fracture energy is the size effect method [7]. For this purpose it was more convenient to use tensile tests of geometrically similar edge-notched strip specimens of three different sizes, as shown in FIG. 10. Because this method uses only the maximum loads and the postpeak softening is not needed, it suffices to conduct the tests with the standard grips, even though they failed right after the peak load. The fracture energies obtained from the size effect and from the postpeak were respectively: from size effect: G.sub.f=73.7 N/m and from postpeak:

G.sub.f=78 N/m(31)

It is notable that the difference between these two values is only 5.8%.
Nonexistence of Snapback and of Conflict with Size Effect

[0083] Because it was impossible to observe postpeak softening it has been believed for decades that the fracture specimens of composites exhibit a severe snap-back. Based on the stiffening the grips as set forth above, it can now be seen that this view was incorrect. The misconception of snapback further shed false doubts on the applicability of fracture mechanics to fiber composites. The area under the supposed snapback curve, which must in any case be smaller than the area under a load-deflection curve with sudden vertical load drop from the peak-load point, gave a fracture energy much smaller than that deduced from the size effect, or from the measured drop of complementary energy of test specimen.

[0084] For some investigators, this severe mismatch was another reason to consider quasibrittle cohesive fracture mechanics as inapplicable to fiber composites. Now we see that this interpretation was mistaken.

[0085] The present analytical and experimental results, and especially Eq. (31), prove that fracture mechanics is equally applicable to fiber composites.

Determining why the Postpeak in Delamination Fracture Tests has been Stable

[0086] To determine the delamination fracture energy of the same carbon composite, the ASTM standard test specimen [11] was used. In these tests, the gradual postpeak softening was stable, even with the standard grips. The explanation is that the delamination specimens are much softer than the compact tension specimens. If |K.sub.s| is small enough, K.sub.t ceases to be negative since the first term in Eq. (2) is always positive. We see that the required stiffness of the grips increases with the stiffness of the fracture specimen.

CONCLUSION

[0087] 1. The specimen grips (or fixtures) of the contemporary hydraulic servo-controlled testing machines do not have sufficient stiffness and mass to enable stable measurement of postpeak softening of fracture specimens of very strong and very light materials such as fiber composites.

[0088] 2. By stability analysis based on the second law of thermodynamics, it is shown that the cause of pervasive failure to observe postpeak softening during the past half century decades of composites testing has been the instability due to insufficient stiffness and mass of the specimen grips.

[0089] 3. Based on static stability analysis of the test setup, it is proposed to use grips that are stiff by about two orders of magnitude. Calculations show that, in this way, stability is achieved.

[0090] 4. Experiments on compact-tension fracture specimens of woven fiber-polymer composites confirm the observability of stable postpeak, not only for the CMOD control but even for the load-point displacement control.

[0091] 5. The grip stiffness required for stability increases with the stiffness of the fracture specimen.

[0092] 6. Calculations of the eigenvalues of the equations of motion of the test setup confirm that the grip stiffness has a huge effect on static as well as dynamic stability, makes the PID control much easier.

[0093] 7. Calculations also indicate a large effect of the increase of mass of the grips on controllability of the postpeak response under PID control, although the effect on stability is nil.

[0094] 8. Calculations further they indicate that, if a sufficient mass is rigidly attached to the existing soft grips, the postpeak response under PID control of the CMOD should become controllable.

[0095] 9. The present stability analysis also explains why the switch in the 1960s to far stiffer testing frames sufficed to stabilize the postpeak softening in concrete and rocks, but not in composites. The specimens of concrete and rock are generally far more massive and their attachments (consisting of flat contacts, glued in the case of tension) have naturally been far stiffer than those used for fiber composites.

[0096] 10. The previous view that the impossibility of measuring postpeak softening necessarily implied a severe snapback is not correct. In the usual compact-tension specimens there is no snapback.

[0097] 11. The previous inference that the smallness of the area under the supposed snapback curve conflicted with G.sub.f measured from the size effect or from the energy release was thought to invalidate fracture mechanics. This inference was false.

[0098] 12. The present results prove that quasibrittle fracture mechanics, with finite fracture process zone and a transitional size effect, is perfectly applicable to fiber composites.

[0099] 13. The present results also prove that the previously widespread use of plasticity-based failure envelopes in terms of stress or strain has not been correct.

EXPERIMENTS

Materials

[0100] Experiments were conducted on woven composite specimens manufactured by compression molding. A DGEBA-based epoxy resin was chosen as polymer matrix whereas the reinforcement was provided by a twill 22 fabric made of carbon fibers. The material was characterized following the ASTM standard procedures [25] for testing under compact tension. The material was a [0]8 lay-up with a constant thickness of approximately 1.8 mm.

[0101] Further experiments were conducted on fiberglass reinforced polyester (FRP) composite, with the thickness of about 10 mm.

Specimen Characteristics

[0102] The modified Compact Tension (CT) specimen geometry was developed to produce stable crack growth so that the composite damage zone could be investigated. Initially, a 2 mm width notch was created by using diamond band saw. Then, the notch was extended by using artistic wire saw in order to create a shape notch tip of 0.2 mm in radius. The CT specimen with a sharp notch tip is stable under displacement control and is large enough so that the boundaries do not greatly affect the damage zone size or shape.

[0103] The specimen was loaded in tension through pins located above and below the notch. It was found that the pin holes cannot be made using steel drill bits because the carbon fiber is harder than the steel from which the drill is made. To avoid damage due to fiber tear-out and delamination around the holes caused by steel drill bits, abrasive cutting with tungsten grinding bits for nonmetals was used to create these holes. The specimen thickness of 5.4 mm sufficed to prevent of the woven composite material.

[0104] Furthermore, intra-laminar size effect tests were conducted on single-edge-notched tension (SENT) specimens (see FIG. 10), using a [0 ]8 lay-up with a constant thickness of approximately 1.9 mm. The SENT specimens were preferred to double-edge notched tension (DENT) specimens because in these specimens the response path bifurcates such that only one of the two cracks can propagate, causing asymmetric response [26].

[0105] SENT specimens of three sizes (three for each size), geometrically scaled in two-dimensions in the ratio 1:2:4, were tested. The specimen lengths, L+2L.sub.t were, respectively, 120.5, 165.0, 254.0 ram, the gauge lengths 44.5, 89.0, 178.0 mm, the widths 20, 40, 80 mm, and the notch lengths 4, 8, 16 mm. The thickness was 1.9 mm, and the tab length L.sub.t=38 mm, the same for all the sizes. The glass-epoxy tabs, for gripping purposes, were not scaled because they have no appreciable effect on the store energy release and because fracture always occurs away from the grips.

[0106] The first half of the notch of SENT specimens was cut by means of a diamond-coated bend saw which provided a width of roughly 1 mm. The second half of the notch was cut by a diamond-coated miniature blade, thanks to which a notch width of only 0.2 mm was achieved in all cases. Accordingly, the resulting crack tip radius was 0.1 mm, about 70 times smaller than the size of a Representative Unit Cell (RUC) of the material.

[0107] The top surface of all the SENT specimens investigated was treated to allow Digital Image Correlation (DIC) analysis. A thin layer of white paint was deposited on a DD area embedding the crack. Then, black speckles of average size 0.01 mm were spray-painted on the surface after drying.

Testing

[0108] The Compact Tension (CT) test set-up is shown in FIG. 3. A universal testing machine (of MTS) was used to load the CT specimens at the rate of 1 mm/min. Tensile loading was applied through 20 mm diameter pins inserted through the holes shown in FIG. 1a. An extensometer was attached to the specimens to measure the pin opening displacement (POD). The load cell signal and the extensometer signal were output and recorded.

Size Effect Tests on Single Edge-Notched Tension (SENT) Specimens

[0109] After the completion of the experiments, the load and displacement data were analyzed. FIG. 11 shows, for the various sizes, the typical load-displacement plots reported. For the largest specimen size, these curves are almost linear up to failure, which is an indication of pronounced brittle behavior.

[0110] Right after reaching the peak load, the specimens used for size effect became unstable for all the sizes and failed dynamically. This was no problem since the size effect analysis does not require postpeak (note that stiff grips cannot stabilize these specimens because the specimen itself is too soft and stores too much energy). The failed specimens showed microcracks within the layers, and tow breakage or pull-out. Delamination between the layers occurred before the peak load.

[0111] Note that that, according to strength-based criteria (e.g., Tsai and Wu [1]), the nominal strength would not depend on the structure size. However, Table 3 does show a significant decrease of N with an increasing characteristic size of the specimen, which proves the strength based failure criteria to be incorrect.

[0112] From the size effect results, the initial fracture energy was obtained as G.sub.f=73.7 N/mm.

Compact Tension Test Results

[0113] FIG. 9 gives the load vs. pin opening displacement (POD) curves of all the tested specimens. For woven composite specimens, it can be seen that, the load vs. POD curves are approximately linear up to the first load drop. After that, the crack progresses in a series of small jumps which cause further load drops.

[0114] In contrast, the FRP specimens showed a large degree of non-linearity in the load vs. POD curves. FIGS. 9a,b and 9c,d show failure modes typical of woven composites and FRP composite specimens. The failure of woven composite is characterized by development of fiber breakage along the center line of the specimen toward the back. A small amount of splitting can be observed on either side of the fiber breaks, which caused flaking of the paint for the Digital Image Correlation (DIC).

[0115] From the load vs. POD curves (FIG. 9), the fracture energy of the composites can be estimated as [7]:

[00013]$\begin{array}{cc}{G}_f=\frac{W}{{\mathrm{bl}}_l}& \left(32\right)\end{array}$

where G.sub.f=fracture energy, W=area under the load displacement curve, b=thickness of the specimen and l.sub.l=ligament length. The calculated fracture energies for woven composites are 76.34 N/mm and 79.74 N/mm for specimen 1 and specimen 2 respectively. These results are very close to the fracture energy calculated from the size effect using the size effect test (since the size effect method gives the fracture energy corresponding only to the area under the initial tangent to the cohesive stress-displacement law, it appears that this law should not have a long tail of small slope). The fracture energies of FRP composites deduced from the size effect were 14.16 N/mm and 13.09 N/mm for specimens 1 and 2, respectively.

Example

[0116] Designing a grip according to the present application may be done based on calculated stiffness. The basic design of a grip includes two parallel steel legs extending from a base to form a generally U-shaped clevis, with the legs defining a slot for receiving the test specimen. A pin is used to secure the test specimen to the parallel legs, and the entire grip is secured to the load frame by either a threaded shaft or a threaded bore.

[0117] The design process is iterative and includes the following steps: [0118] (1) The stiffness of the grip is calculated and entered into the proposed stability criterion (e.g., equation 5) to check if stable testing is enabled. [0119] (2) If the stability criteria are not satisfied, the design is improved and step (1) repeated. [0120] (3) Step (2) is repeated until the stability criteria are satisfied.

[0121] With reference to FIGS. 13a), 13b) and 13c), three grips are shown that demonstrate an example of the designing process. From design 13a) to 13c), the grips are made to be more massive, particularly in the base, and an increase in the calculated grip stiffness is observed. Only the final design, FIG. 13c), satisfies the stability criteria.

[0122] The procedure for calculating the stiffness of the grip requires first creating a 3D CAE model of the grip using a commercially-available CAD software (such as the Autodesk Inventor design application). The model is then imported into a finite element program for mechanical analysis (such as that available from Abaqus Inc.), and material properties are assigned and boundary conditions applied to simulate the loading conditions of an actual test. The stiffness of the designed grip, K, is calculated as load, F, divided by the load-point displacement, d, obtained from the post-processing results (i.e., K=F/d).

REFERENCES

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