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Q3.(a) m l Assume the rigid bar moves by , then m moves by l. The location at a moves by a. The equation of motion about (taking moments about the pin joint) is ml 2 [k (a ) c(a)]a Q5. (P2-11) Assume the friction force beneath the wheel is f. Equations of motion for the x and are mx kx f J fr x f kx o Merge into a single equation as J o mx kx r 0 Using geometric relationship x r , one gets ( J o mr 2 ) kr 2 0 and k (m J o / r 2 ) n x1 Q6. f1 f1 m kx1 Equilibrium about the central support f1a f 2 b 0 ( f 2 k2 x2 ) Geometric relationship f2 x2 x2 x 1 b a Equation of motion mx1 f1 k1 x1 finally b2 mx1 ( k1 k2 2 ) x1 0 a Q7. (P3-20) The ground excitation is y (t ) Y sin 2 πv . L When 2πv k , L m 2 πvt L and so the excitation frequency is there is resonance and the largest acceleration occurs. Q8. fsint The equations of motion for x and are mx kx R f sin t m (d d ) 2 Rd b 1 2 x m 1 Using geometric relationship x d1 , one gets kx R [md12 mb (d1 d 2 ) 2 ]x kd12 x fd12 sin t mb R Q9. (P5-20) Assume the center of mass moves downwards by x and the rod rotates clockwise around it by . x1 The equations of motion for x and are mx kx1 kx2 k ( x1 x2 ) kx2 kx1 J c kx1 l l kx2 4 2 The geometric relationship between displacements is l l x1 x x2 x 4 2 The final equations of motion become x x2 kl 2 k m 0 x 4 x 0 0 J kl 5kl 2 c 4 16 Q10. The matrix equation of motion is 3m 0 x1 2k k x1 0 m x k 4k x 0 2 2 The corresponding eigenvalue problem is 0 a1 2k k 2 3m ( 0 m)a 0 k 4 k 2 This requires 2k det( k k 0 2 3m 0 m ) 0 4k This leads to (2k 3m 2 )(4k m 2 ) k 2 0 or 3m 2 4 14mk 2 7k 2 0 This quadratic equation 14 14 2 4 3 7 k k k 0.57 and 4.10 6 m m m 2 Substituting each of these into (2) yields modes as 1 1 k k and for 1 2.025 for 2 0.755 m m 0.29 10.3 2 Q11. Because the center of gravity is offset from the elastic center, the wing vibrates vertically and torsionally. The two degrees-of-freedom are vertical displacement x measured from the elastic center O and angular displacement rotating about O in clockwise direction respectively. (1) (2) (3) The equation of motion of the airfoil is m(x eg) kx, J o meg x K mx meg kx 0 , meg x J o K 0 Assume x(t ) A exp( it ) , (t ) B exp( it ) It follows that k m 2 meg 2 A 0 2 2 me K J B g o x G O This leads to m( J o meg2 ) 4 (kJo mK ) 2 kK 0.76 4 1800 2 1000000 0 Two natural frequencies can be found as 29.83rad/s and 38.45rad/s (also confirmed using MATLAB). The lift force and pitching moment acting at the aerodynamic center are L qSa , M qScM,0 c (q 1 V2 ) 2 The moment equilibrium about center O is Lea K M 0 It follows that qScM,0 c qSaea K Divergence occurs when the denominator of the above equation becomes zero. This allows the critical speed for divergence to be determined as Vdiv 2K Saeg 2 100 68.04m/s 1.2 0.3 1 6 0.02 The equation of motion of the wing under air flow is mx meg kx L , meg x J o K M There are mainly three reasons why flutter may occur. (1) Inertia coupling: the terms represented by meg which links the acceleration of x with acceleration of . (2) Aerodynamic coupling: a wing rotation causes a lift change which in turn alters translation x; or a translation x (so a vertical linear velocity) alters effective incidence angle which brings about a lift change that affects wing rotation . (3) Stiffness coupling: the force in the vertical spring induced by x produces a torque about a reference point while a wing rotation about the same reference point produces a vertical force in the vertical spring. Since the reference point in Figure 4 is the elastic center of the wing, elastic coupling is not present in this question. Flutter can be prevented in theory by removing the above-mentioned inertia, aerodynamic and elastic coupling by arranging for the center of gravity, the center of independence and the elastic center to coincide. Increasing the stiffness of a wing also helps to raise the flutter speed, though this normally carries a weight penalty. It is difficult to make the center of independence coincide with the elastic center in practice. Q12 M x3 k1x1 k2x2 First, you need to define the degrees-offreedom and then the displacements forces concerned in terms of these degrees-offreedom. Assume the center of gravity G moves upwards by x and the rod rotates x3 x1 x x2 anti-clockwise around it by these are the def chosen degrees-of-freedomDenote x1 displacement profile and x2 as displacements at k1 and k2 respectively, and x3 as the displacement of the lumped mass M). The geometric relationship between displacements is x1 x l1 x2 x l2 x3 x l3 With displacements defined, forces acting on the rigid bar can be defined. The difficult is how to deal with the lumped mass M. A convenient way is to use D’Alembert principle: a force Mx3 is placed at the location (in place) of the lumped mass in the direction opposite to x3. The equations of motion for x and are mx k1 x1 k2 x2 Mx3 J k x l k x l Mx l G 1 1 1 2 2 2 3 3 Substituting the above relationship into the previous equations of motion and further mathematical manipulation yields ( m M ) x Ml3 ( k1 k2 ) x ( k2l2 k1l1 ) 0 ( J G Ml32 ) Ml3 x ( k2l2 k1l1 ) x ( k1l12 k2l22 ) 0 or more compactly m M Ml 3 Ml3 x k1 k2 J G Ml32 k2l2 k1l1 k2l2 k1l1 x 0 k1l12 k2l22 These are the (final) equations of motion of the structure in terms of x and , which are amenable to further mathematical treatment (for example, for determining the natural frequencies).