Journal of Mechanics of Materials and Structures vol. 5 (2010 ... - MSP
Journal of Mechanics of Materials and Structures vol. 5 (2010 ... - MSP
Journal of Mechanics of Materials and Structures vol. 5 (2010 ... - MSP
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760 XIAO-TING HE, QIANG CHEN, JUN-YI SUN, ZHOU-LIAN ZHENG AND SHAN-LIN CHEN<br />
From (11), we obtain<br />
t1 =<br />
E + t 2 1<br />
1 − µ + = E−t 2 2<br />
.<br />
1 − µ −<br />
(13)<br />
Combining t1 + t2 = t, we solve for the thicknesses <strong>of</strong> the plate in tension <strong>and</strong> compression as follows:<br />
�<br />
E− (1 − µ + )<br />
� � t,<br />
E + (1 − µ − ) + E− (1 − µ + )<br />
�<br />
E + (1 − µ − )<br />
t2 = � � t.<br />
E + (1 − µ − ) + E− (1 − µ + )<br />
(14)<br />
Thus, the position <strong>of</strong> the unknown neutral layer <strong>of</strong> the plate in pure bending is finally determined analytically.<br />
3.2. Lateral force bending. While the plate is in lateral force bending, for example, under the uniformly<br />
distributed loads, q, as shown in Figure 3, not only the torsional stress, τxy, but also the transverse shear<br />
stresses, τzx <strong>and</strong> τzy, as well as the extrusion stress, σz, exist in the plate. However, according to the<br />
conclusion in Section 2.2, the neutral layer does exist if the thickness <strong>of</strong> the plate is small compared with<br />
the deflection <strong>of</strong> the plate. Therefore, the torsional stresses in the plate in tension <strong>and</strong> compression may<br />
be expressed in terms <strong>of</strong> the deflection w as, respectively,<br />
τ + xy = − E+ z<br />
1 + µ +<br />
∂2w ∂x∂y , 0 ≤ z ≤ t1, (15a)<br />
τ − xy = − E−z 1 + µ −<br />
∂2w ∂x∂y , −t2 ≤ z ≤ 0. (15b)<br />
The twist moment Mxy may be computed as<br />
� t1<br />
Mxy = τ<br />
0<br />
+ � 0<br />
xy z dz + τ<br />
−t2<br />
− �<br />
E + 3 t1 xy z dz = −1<br />
3 1 + µ + + E−t 3 2<br />
1 + µ −<br />
�<br />
∂2w . (16)<br />
∂x∂y<br />
Under uniformly distributed loads, q, the differential equation <strong>of</strong> equilibrium for bending <strong>of</strong> thin plates<br />
is<br />
∂2 Mx<br />
∂x 2 + 2∂2 Mxy<br />
∂x∂y + ∂2 My<br />
+ q = 0. (17)<br />
∂y 2<br />
Figure 3. Bimodular thin plate under lateral force bending.