- Page 3 and 4: iiiDEDICATIONÀ mon …ls Matthieu
- Page 6 and 7: vi5 FORCED VIBRATIONS : : : : : : :
- Page 9 and 10: ixSUMMARYA novel analysis is propos
- Page 11 and 12: CHAPTER IINTRODUCTIONThe purpose of
- Page 13 and 14: 3properties have canonical forms: f
- Page 15 and 16: 5mode shape problem where eigendata
- Page 17 and 18: 7where ~v O and ~ Á are respective
- Page 19: 9yOA, I x , I y , Y, LMxm, m γFigu
- Page 24 and 25: 14twist it induces the form T E = P
- Page 26 and 27: where ~r S f and ~rC °are respecti
- Page 28 and 29: 18m fi are all equal and represent
- Page 30 and 31: 20Consider any wrench contained in
- Page 32 and 33: 22on the subject is extensive [15],
- Page 34 and 35: 24VEMyzxFigure 3.1: Elastically Sus
- Page 36 and 37: 26! 2 =k ° + k x EVy 2 + k y EVx2m
- Page 38 and 39: 28·where ^T M =~ ±T0¸Tis a trans
- Page 40 and 41: 30yVMExFigure 3.2: Location of Vibr
- Page 42 and 43: 32Theorem 10 When the center of mas
- Page 44 and 45: 34where MV x1 , MV x2 , MV x3 are t
- Page 46 and 47: 36At the center of mass,2M M =64m 0
- Page 48 and 49: 38yV 2OMEV 1TranslationalDirectionx
- Page 50 and 51: CHAPTER IVTRANSLATION AND COUPLE MO
- Page 52 and 53: 42δw rFigure 4.2: Pure Translation
- Page 54 and 55: 444.2.1 Translation ModeThe two equ
- Page 56 and 57: 46sti¤ness and mass matrices have
- Page 58 and 59: 484.3.1 Translation modeIt is known
- Page 60 and 61: 50matrix and,23k tr =640 0 0a b cd
- Page 62 and 63: 52rotations which intersect at M. T
- Page 64 and 65: 54direct consequence of assuming eq
- Page 66 and 67: 56be rewritten as,~ fTi~ ±1 = ~ ±
- Page 68 and 69: 58produced by a couple mode. The pr
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60should then be a pure translation
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62be represented as,K M = X T EMK E
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64means that one principal sti¤nes
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66Substituting (4.61) and (4.62) in
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68δ 2δ 3τ 1E; MFigure 4.7: Coupl
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70Equation (4.74) represents the ei
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72² Design K 2 such that ^w is one
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74Equation (4.83) shows that k fcan
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76make the common eigentwists paral
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78Note that ^w transforms according
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80The proposed design places 13 con
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82construction is a problem of sti
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84where·¸2~ f2 ~ f3 p 6=66430 ¡2
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86fStiffnessAxisM 2Body 2Body 1τ M
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88the centers of mass and elasticit
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90where the vector from E 2 to M 2
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92where the arbitrary linear princi
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94² The linear mass of the absorbe
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96Pfk x kγ k yFigure 4.13: Possibl
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98specialized to systems exhibiting
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100where ! 2 j is the natural frequ
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102V 1V 2ffτ MMV 3Figure 5.3: Mode
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104γ iαMMV iMFV i FfFigure 5.4: L
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106Equation (5.20) reveals that the
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108Substituting (5.23) into (5.22)
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110V 1EYMYMV 2V 3Figure 5.6: Mode 1
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112δEMV 2V 3V 1Figure 5.8: Mode 1
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114a planar rotating unbalance for
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116undamped, underdamped, criticall
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118The location of point V is given
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Note that ¡! AV can also be found
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122For planar motion, the eigenvect
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124Aδ δxδByBxyB AδA By− δx
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126position. This observation means
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Equation (6.53) reveals that the vi
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130¯c ¯± B A¯Equation (6.64) re
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13221.51Mode 1Mode 2Mode 3Imaginary
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Y134-0.4-0.5-0.6-0.7Point APoint BM
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13676δ ΑB543Mode 1Mode 2Mode 3210
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138where A and B are any points on
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140where^W A = K^T A^W B = K^T BEqu
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142where c = p ¤ =p. Equation (6.9
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1442z 0-2420x-2-4420y-2-4Figure 6.1
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146Equation (6.106) shows that the
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1486.2.4 Overdamped ModesThe eigenv
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150where ¸j and X j are respective
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152Equations (6.131) reveal that ^w
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154Hence the orthogonality conditio
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156If ~ f R and ~ f I are linearly
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CHAPTER VIIOTHER RESULTSThis chapte
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160(S) to coalesce, for the centers
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162As before, all three ~r i = ~0 w
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164The previous Theorem proved that
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166Proof.From Theorem 49, the eigen
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168the eigenwrenches with respect t
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170eigentwists of the damping matri
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172Equation (7.53) shows that the e
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174and inertia matrices to intersec
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176In Chapter 4, the occurrence of
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178APPENDIXA. Proof of Critically D
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180where S is a non-singular matrix
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182Equation (A.3) can be written as
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184REFERENCES[1] Anton, H., 1984, E
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186[35] Patterson, T. and Lipkin, H