Dynamics of Machines - Part II - IFS.pdf
Dynamics of Machines - Part II - IFS.pdf Dynamics of Machines - Part II - IFS.pdf
Integrating twice in X, it gives: EI d2 y(x) dx 2 = M(x) = C1x + C2 (3) Integrating again in X, one gets the rotation angle of the beam: EI dy(x) dx x = EIΘ(x) = C1 2 2 + C2x + C3 And finally, integrating the last time in X, one achieves the equation responsible for describing the deflexion of the beam: x EI y(x) = C1 3 6 x + C2 2 2 + C3x + C4 The boundary conditions for the clamped-free beam are: •y(x = 0) = 0 •Θ(x = 0) = 0 •M(x = L) = 0 •F(x = L) = −F (reaction) ⎫ ⎪⎬ ⎪⎭ After calculating the constants Ci using the boundary condition for the clamped-free beam case, one gets y(x) = − F E I dy(x) dx x 3 6 = Θ(x) = − F E I L x2 − 2 x 2 2 − L x Using the relationship between applied force F and the induced deflexion at a given point along the beam length, x = L for instance, one gets the equivalent stiffness as: K = F y(L) = 3 EI L 3 Suggestion (I): Change the beam boundary conditions, for example bi-supported at both ends, and calculate the equivalent stiffness in the new case. Suggestion (II): Change the beam boundary conditions, for example clamped-clamped at both ends, and calculate the equivalent stiffness in the new case. 6 (4) (5) (6) (7) (8) (9)
1.5 Calculating Stiffness Matrices – Beam Theory Two Different Lengths for Applying Forces – To facilitate the understanding of steps which will be presented, one can introduce the follow nomenclature (see figure 3(b)): • L ∗ = L1 or L ∗ = L2 – length where the force F is applied. • x = L1 or x = L2 – length where the displacement is measured. Taking into account two different points for applying the forces and measuring the displacements of the beam, one works with the following set of equations x [0, L ∗ ] and x [L ∗ , L] ⎧ ⎪⎨ ⎪⎩ ⎧ ⎪⎨ ⎪⎩ y(x) = − F E I dy(x) dx = − F E I x3 6 − L∗ x2 2 x2 2 − L∗ x y(x) = y(L ∗ ) + dy(x) dx dy(x) dx = dy(x) dx x=L ∗ x=L∗ · (x − L∗ ) which are responsible for describing the deflection of the beam, considering the loading on different coordinates. Let us introduce an example of a system with two points of force application. Assuming in case (I) the force F is applied to the first coordinate L ∗ = L1. One can measure and/or calculate the beam deflection at the coordinates x = L1 and x = L2 through equations (10) and (11): y1 = y(L1) = F · L3 1 3 · EI and y2 = y(L2) = F 6EI · (2L3 1 + 3L 2 1(L2 − L1)) (13) Assuming in case (II) that the force F is applied to the second coordinate L ∗ = L2, one can measure and/or calculate the follow beam displacements at the coordinates x = L1 and x = L2 through the equations (10) and (11): y1 = y(L1) = F 6EI · (2L3 1 + 3L 2 1(L2 − L1)) (14) and y2 = y(L2) = F · L3 2 3 · EI 7 (10) (11) (12) (15)
- Page 1 and 2: DYNAMICS OF MACHINES 41614 PART I -
- Page 3 and 4: 1 Introduction to Dynamical Modelli
- Page 5: 1.3 Data of the Mechanical System
- Page 9 and 10: 1.6 Mechanical Systems with 1 D.O.F
- Page 11 and 12: Demanding (λ 2 + 2ξωnλ + ω 2 n
- Page 13 and 14: 1 yini − A det λ1 vini − A C2
- Page 15 and 16: 1.6.4 Analytical and Numerical Solu
- Page 17 and 18: (a) y(t) [m] (b) y(t) [m] (c) y(t)
- Page 19 and 20: 1.6.6 Homogeneous Solution or Free-
- Page 21 and 22: (a) Amplitude [m/s 2 ] x Signal 10
- Page 23 and 24: (a) Amplitude [m/s 2 ] (b) Amplitud
- Page 25 and 26: Imag(A(ω)) [m/N] 0 −1 −2 −3
- Page 27 and 28: 1.6.11 Superposition of Transient a
- Page 29 and 30: (a) Amplitude [m/s 2 ] (b) Amplitud
- Page 31 and 32: 1.7 Mechanical Systems with 2 D.O.F
- Page 33 and 34: ⎧ ⎫ ⎪⎨ ˙y1(t) ⎪⎬ ˙y
- Page 35 and 36: zini = U c + A ⇒ c = U −1 {(zin
- Page 37 and 38: 1.7.4 Modal Analysis using Matlab e
- Page 39 and 40: 0.7 0.6 0.5 0.4 0.3 0.2 0.1 First M
- Page 41 and 42: %__________________________________
- Page 43 and 44: ||y 1 (ω)|| [m/N] Phase [ o] Excit
- Page 45 and 46: ||y i (ω)|| [m/N] Phase [ o] 0.8 0
- Page 47 and 48: Imag(y i (ω)/f 1 (ω)) (i=1,2) [m/
- Page 49 and 50: 1.8 Mechanical Systems with 3 D.O.F
- Page 51 and 52: which could be verified using Modal
- Page 53 and 54: %%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%
- Page 55 and 56: 1.8.4 Theoretical Frequency Respons
Integrating twice in X, it gives:<br />
EI d2 y(x)<br />
dx 2 = M(x) = C1x + C2 (3)<br />
Integrating again in X, one gets the rotation angle <strong>of</strong> the beam:<br />
EI dy(x)<br />
dx<br />
x<br />
= EIΘ(x) = C1<br />
2<br />
2 + C2x + C3<br />
And finally, integrating the last time in X, one achieves the equation responsible for describing<br />
the deflexion <strong>of</strong> the beam:<br />
x<br />
EI y(x) = C1<br />
3<br />
6<br />
x<br />
+ C2<br />
2<br />
2 + C3x + C4<br />
The boundary conditions for the clamped-free beam are:<br />
•y(x = 0) = 0<br />
•Θ(x = 0) = 0<br />
•M(x = L) = 0<br />
•F(x = L) = −F (reaction)<br />
⎫<br />
⎪⎬<br />
⎪⎭<br />
After calculating the constants Ci using the boundary condition for the clamped-free beam case,<br />
one gets<br />
y(x) = − F<br />
E I<br />
dy(x)<br />
dx<br />
x 3<br />
6<br />
= Θ(x) = − F<br />
E I<br />
<br />
L x2<br />
−<br />
2<br />
x 2<br />
2<br />
<br />
− L x<br />
Using the relationship between applied force F and the induced deflexion at a given point along<br />
the beam length, x = L for instance, one gets the equivalent stiffness as:<br />
K = F<br />
y(L)<br />
= 3 EI<br />
L 3<br />
Suggestion (I): Change the beam boundary conditions, for example bi-supported at both ends,<br />
and calculate the equivalent stiffness in the new case.<br />
Suggestion (<strong>II</strong>): Change the beam boundary conditions, for example clamped-clamped at both<br />
ends, and calculate the equivalent stiffness in the new case.<br />
6<br />
(4)<br />
(5)<br />
(6)<br />
(7)<br />
(8)<br />
(9)