Dynamics of Machines - Part II - IFS.pdf
Dynamics of Machines - Part II - IFS.pdf Dynamics of Machines - Part II - IFS.pdf
and ˙y(0) = ˙y0 ˙y1(0) ˙y2(0) = v1ini v2ini and the equation of motion eq.(52), which has to be solved, one can calculate the acceleration, when t = t0 = 0: ¨y0 = −M −1 D ˙y0 + Ky0 − ¯ jωt0 fe The first predicted values of displacement, velocity and acceleration in time t1 = ∆t , using the approximation given by eq.(71), are: t1 = ∆t ˙y1 = ˙y0 + ¨y0∆t y1 = y0 + ˙y1∆t ¨y1 = −M −1 D ˙y1 + Ky1 − ¯ jωt1 fe The second predicted values of displacement, velocity and acceleration in time t2 = t1 + ∆t , using the approximation given by eq.(71), are: t2 = 2∆t ˙y2 = ˙y1 + ¨y1∆t y2 = y1 + ˙y2∆t ¨y2 = −M −1 D ˙y2 + Ky2 − ¯ jωt2 fe The N-th predicted values of displacement, velocity and acceleration in time tN = tN−1 + ∆t , using the approximation given by eq.(74), are: tN = N∆t ˙yN = ˙yN−1 + ¨yN−1∆t yN = yN−1 + ˙yN∆t ¨yN = −M −1 D ˙yN + KyN − ¯ jωtN fe Plotting the points [y1,y2,y3, ...,yN] versus [t1, t2, t3, ..., tN], one can observe the numerical solution of the differential equation, which describes the displacements of the mass-dampingspring system in time domain. Plotting the points [ ˙y1, ˙y2, ˙y3, ..., ˙yN] versus [t1, t2, t3, ..., tN] or [¨y1, ¨y2, ¨y3, ..., ¨yN] versus [t1, t2, t3, ..., tN] one can also observe the velocity and acceleration of the mass-damping-spring system in time domain. The analytical and numerical solutions of the second order differential equation, eq.(52), are illustrated using a Matlab code. 36 (74) (73)
1.7.4 Modal Analysis using Matlab eig-function [u, w] = eig(−B, A) %%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%% % MACHINERY DYNAMICS LECTURES (41614) % % MEK - DEPARTMENT OF MECHANICAL ENGINEERING % % DTU - TECHNICAL UNIVERSITY OF DENMARK % % % % Copenhagen, February 11th, 2000 % % IFS % % % % MODAL ANALYSIS % % % % 2 D.O.F. SYSTEMS - MODAL ANALYSIS - 3 EXPERIMENTAL CASES % %%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%% clear all; close all; %Concentred Masses m1= 0.191; %[Kg] m2= 0.191; %[Kg] m3= 0.191; %[Kg] m4= 0.191; %[Kg] m5= 0.191; %[Kg] m6= 0.191; %[Kg] %Elastic Properties of the Beam of 600 mm E= 2e11; %elasticity modulus [N/m^2] b= 0.030 ; %width [m] h= 0.0012 ; %thickness [m] I= (b*h^3)/12; %area moment of inertia [m^4] % (1.CASE) Data for the mass-spring system %__________________________________________________ M1=m1; %concentrated mass [Kg] | M2=m2; %concentrated mass [Kg] | L1= 0.310; %length for positioning M1 [m] | L2= 0.610; %length for positioning M2 [m] | %__________________________________________________| % Coefficients of the Stiffness Matrix LL=(L1-4*L2)*(L1-L2)^2; K11= -12*(E*I/LL)*L2^3/L1^3; %equivalent Stiffness [N/m] K12= -6*(E*I/LL)*(L1-3*L2)/L1; %equivalent Stiffness [N/m] K21= -6*(E*I/LL)*(L1-3*L2)/L1; %equivalent Stiffness [N/m] K22= -12*(E*I/LL); %equivalent Stiffness [N/m] %Mass Matrix M= [M1 0; 0 M2]; %Stiffness Matrix K= [K11 K12; K21 K22]; %Damping Matrix D= [0 0; 0 0]; %State Matrices A= [ M D ; zeros(size(M)) M ] ; B= [ zeros(size(M)) K ; -M zeros(size(M))]; %Dynamical Properties of the Mass-Spring System [u,w]=eig(-B,A); % Eigenvectors u % Eigenvalues w [rad/s] w u pause; w_vector=diag(w); [natfreq,indice]=sort(w_vector); % Sorting the natural Frequencies % Natural Frequencies (Hz) w1=abs(imag(w_vector(indice(1))))/2/pi % First natural frequency w2=abs(imag(w_vector(indice(3))))/2/pi % Second natural frequency mass_position(1) = 0; mass_position(2) = L1; mass_position(3) = L2; % first mode shape uu1(1)=0; uu1(2)=u(1,indice(1)); uu1(3)=u(2,indice(1)); figure(1) plot(uu1,mass_position,’r*-.’,-uu1,mass_position,’r*-.’,’LineWidth’,1.5) grid f1=num2str(w1); set(gca,’FontSize’,12,’FontAngle’,’oblique’); title([’First Mode Shape - Freq.: ’,f1,’ Hz’]) 37 % second mode shape uu2(1)=0; uu2(2)=u(1,indice(3)); uu2(3)=u(2,indice(3)); figure(2) plot(uu2,mass_position,’r*-.’,-uu2,mass_position,’r*-.’,’LineWidth’,1.5) grid f2=num2str(w2); set(gca,’FontSize’,12,’FontAngle’,’oblique’); title([’Second Mode Shape - Freq.: ’,f2,’ Hz’]) pause; % (2.CASE) Increasing the Mass Values %__________________________________________________ M1=m1+m2; %concentrated mass [Kg] | M2=m3+m4; %concentrated mass [Kg] | L1= 0.310; %length for positioning M1 [m] | L2= 0.610; %length for positioning M2 [m] | %__________________________________________________| % Coefficients of the Stiffness Matrix LL=(L1-4*L2)*(L1-L2)^2; K11= -12*(E*I/LL)*L2^3/L1^3; %equivalent Stiffness [N/m] K12= -6*(E*I/LL)*(L1-3*L2)/L1; %equivalent Stiffness [N/m] K21= -6*(E*I/LL)*(L1-3*L2)/L1; %equivalent Stiffness [N/m] K22= -12*(E*I/LL); %equivalent Stiffness [N/m] %Mass Matrix M= [M1 0; 0 M2]; %Stiffness Matrix K= [K11 K12; K21 K22]; %Damping Matrix D= [0 0; 0 0]; %State Matrices A= [ M D ; zeros(size(M)) M ] ; B= [ zeros(size(M)) K ; -M zeros(size(M))]; %Dynamical Properties of the Mass-Spring System [u,w]=eig(-B,A); % Eigenvectors u % Eigenvalues w [rad/s] w u pause; w_vector=diag(w); [natfreq,indice]=sort(w_vector); % Sorting the natural Frequencies % Natural Frequencies (Hz) w1=abs(imag(w_vector(indice(1))))/2/pi % First natural frequency w2=abs(imag(w_vector(indice(3))))/2/pi % Second natural frequency mass_position(1) = 0; mass_position(2) = L1; mass_position(3) = L2; % first mode shape uu1(1)=0; uu1(2)=u(1,indice(1)); uu1(3)=u(2,indice(1)); figure(3) plot(uu1,mass_position,’b*-.’,-uu1,mass_position,’b*-.’,’LineWidth’,1.5) grid f1=num2str(w1); set(gca,’FontSize’,12,’FontAngle’,’oblique’); title([’First Mode Shape - Freq.: ’,f1,’ Hz’]) % second mode shape uu2(1)=0; uu2(2)=u(1,indice(3)); uu2(3)=u(2,indice(3)); figure(4) plot(uu2,mass_position,’b*-.’,-uu2,mass_position,’b*-.’,’LineWidth’,1.5) grid f2=num2str(w2); set(gca,’FontSize’,12,’FontAngle’,’oblique’); title([’Second Mode Shape - Freq.: ’,f2,’ Hz’]) pause; % (3.CASE) Increasing the Mass Values %__________________________________________________ M1=m1+m2+m3; %concentrated mass [Kg] | M2=m4+m5+m6; %concentrated mass [Kg] | L1= 0.310; %length for positioning M1 [m] | L2= 0.610; %length for positioning M2 [m] | %__________________________________________________| ...
- Page 1 and 2: DYNAMICS OF MACHINES 41614 PART I -
- Page 3 and 4: 1 Introduction to Dynamical Modelli
- Page 5 and 6: 1.3 Data of the Mechanical System
- Page 7 and 8: 1.5 Calculating Stiffness Matrices
- 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: zini = U c + A ⇒ c = U −1 {(zin
- 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
- Page 57 and 58: (a) Amplitude [m/s 2 ] (b) Amplitud
- Page 59 and 60: 4. Vary the number of masses attach
- Page 61 and 62: 1.10 Project 0 - Identification of
- Page 63 and 64: (a) (b) REAL(Acc/force) [(m/s 2 )/N
- Page 65 and 66: 6. Model application - As explained
- Page 67 and 68: changeable unbalanced mass for simu
- Page 69 and 70: %Modal Matrix u with mode shapes %M
- Page 71 and 72: acc [m/s 2 ] acc [m/s 2 ] 0.8 0.6 0
1.7.4 Modal Analysis using Matlab eig-function [u, w] = eig(−B, A)<br />
%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%<br />
% MACHINERY DYNAMICS LECTURES (41614) %<br />
% MEK - DEPARTMENT OF MECHANICAL ENGINEERING %<br />
% DTU - TECHNICAL UNIVERSITY OF DENMARK %<br />
% %<br />
% Copenhagen, February 11th, 2000 %<br />
% <strong>IFS</strong> %<br />
% %<br />
% MODAL ANALYSIS %<br />
% %<br />
% 2 D.O.F. SYSTEMS - MODAL ANALYSIS - 3 EXPERIMENTAL CASES %<br />
%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%%<br />
clear all; close all;<br />
%Concentred Masses<br />
m1= 0.191; %[Kg]<br />
m2= 0.191; %[Kg]<br />
m3= 0.191; %[Kg]<br />
m4= 0.191; %[Kg]<br />
m5= 0.191; %[Kg]<br />
m6= 0.191; %[Kg]<br />
%Elastic Properties <strong>of</strong> the Beam <strong>of</strong> 600 mm<br />
E= 2e11; %elasticity modulus [N/m^2]<br />
b= 0.030 ; %width [m]<br />
h= 0.0012 ; %thickness [m]<br />
I= (b*h^3)/12; %area moment <strong>of</strong> inertia [m^4]<br />
% (1.CASE) Data for the mass-spring system<br />
%__________________________________________________<br />
M1=m1; %concentrated mass [Kg] |<br />
M2=m2; %concentrated mass [Kg] |<br />
L1= 0.310; %length for positioning M1 [m] |<br />
L2= 0.610; %length for positioning M2 [m] |<br />
%__________________________________________________|<br />
% Coefficients <strong>of</strong> the Stiffness Matrix<br />
LL=(L1-4*L2)*(L1-L2)^2;<br />
K11= -12*(E*I/LL)*L2^3/L1^3; %equivalent Stiffness [N/m]<br />
K12= -6*(E*I/LL)*(L1-3*L2)/L1; %equivalent Stiffness [N/m]<br />
K21= -6*(E*I/LL)*(L1-3*L2)/L1; %equivalent Stiffness [N/m]<br />
K22= -12*(E*I/LL); %equivalent Stiffness [N/m]<br />
%Mass Matrix<br />
M= [M1 0; 0 M2];<br />
%Stiffness Matrix<br />
K= [K11 K12; K21 K22];<br />
%Damping Matrix<br />
D= [0 0; 0 0];<br />
%State Matrices<br />
A= [ M D ;<br />
zeros(size(M)) M ] ;<br />
B= [ zeros(size(M)) K ;<br />
-M zeros(size(M))];<br />
%Dynamical Properties <strong>of</strong> the Mass-Spring System<br />
[u,w]=eig(-B,A); % Eigenvectors u<br />
% Eigenvalues w [rad/s]<br />
w<br />
u<br />
pause;<br />
w_vector=diag(w);<br />
[natfreq,indice]=sort(w_vector); % Sorting the natural Frequencies<br />
% Natural Frequencies (Hz)<br />
w1=abs(imag(w_vector(indice(1))))/2/pi % First natural frequency<br />
w2=abs(imag(w_vector(indice(3))))/2/pi % Second natural frequency<br />
mass_position(1) = 0; mass_position(2) = L1; mass_position(3) =<br />
L2;<br />
% first mode shape<br />
uu1(1)=0; uu1(2)=u(1,indice(1)); uu1(3)=u(2,indice(1)); figure(1)<br />
plot(uu1,mass_position,’r*-.’,-uu1,mass_position,’r*-.’,’LineWidth’,1.5)<br />
grid f1=num2str(w1); set(gca,’FontSize’,12,’FontAngle’,’oblique’);<br />
title([’First Mode Shape - Freq.: ’,f1,’ Hz’])<br />
37<br />
% second mode shape<br />
uu2(1)=0; uu2(2)=u(1,indice(3)); uu2(3)=u(2,indice(3)); figure(2)<br />
plot(uu2,mass_position,’r*-.’,-uu2,mass_position,’r*-.’,’LineWidth’,1.5)<br />
grid f2=num2str(w2); set(gca,’FontSize’,12,’FontAngle’,’oblique’);<br />
title([’Second Mode Shape - Freq.: ’,f2,’ Hz’]) pause;<br />
% (2.CASE) Increasing the Mass Values<br />
%__________________________________________________<br />
M1=m1+m2; %concentrated mass [Kg] |<br />
M2=m3+m4; %concentrated mass [Kg] |<br />
L1= 0.310; %length for positioning M1 [m] |<br />
L2= 0.610; %length for positioning M2 [m] |<br />
%__________________________________________________|<br />
% Coefficients <strong>of</strong> the Stiffness Matrix<br />
LL=(L1-4*L2)*(L1-L2)^2;<br />
K11= -12*(E*I/LL)*L2^3/L1^3; %equivalent Stiffness [N/m]<br />
K12= -6*(E*I/LL)*(L1-3*L2)/L1; %equivalent Stiffness [N/m]<br />
K21= -6*(E*I/LL)*(L1-3*L2)/L1; %equivalent Stiffness [N/m]<br />
K22= -12*(E*I/LL); %equivalent Stiffness [N/m]<br />
%Mass Matrix<br />
M= [M1 0; 0 M2];<br />
%Stiffness Matrix<br />
K= [K11 K12; K21 K22];<br />
%Damping Matrix<br />
D= [0 0; 0 0];<br />
%State Matrices<br />
A= [ M D ;<br />
zeros(size(M)) M ] ;<br />
B= [ zeros(size(M)) K ;<br />
-M zeros(size(M))];<br />
%Dynamical Properties <strong>of</strong> the Mass-Spring System<br />
[u,w]=eig(-B,A); % Eigenvectors u<br />
% Eigenvalues w [rad/s]<br />
w<br />
u<br />
pause;<br />
w_vector=diag(w);<br />
[natfreq,indice]=sort(w_vector); % Sorting the natural Frequencies<br />
% Natural Frequencies (Hz)<br />
w1=abs(imag(w_vector(indice(1))))/2/pi % First natural frequency<br />
w2=abs(imag(w_vector(indice(3))))/2/pi % Second natural frequency<br />
mass_position(1) = 0; mass_position(2) = L1; mass_position(3) =<br />
L2;<br />
% first mode shape<br />
uu1(1)=0; uu1(2)=u(1,indice(1)); uu1(3)=u(2,indice(1)); figure(3)<br />
plot(uu1,mass_position,’b*-.’,-uu1,mass_position,’b*-.’,’LineWidth’,1.5)<br />
grid f1=num2str(w1); set(gca,’FontSize’,12,’FontAngle’,’oblique’);<br />
title([’First Mode Shape - Freq.: ’,f1,’ Hz’])<br />
% second mode shape<br />
uu2(1)=0; uu2(2)=u(1,indice(3)); uu2(3)=u(2,indice(3)); figure(4)<br />
plot(uu2,mass_position,’b*-.’,-uu2,mass_position,’b*-.’,’LineWidth’,1.5)<br />
grid f2=num2str(w2); set(gca,’FontSize’,12,’FontAngle’,’oblique’);<br />
title([’Second Mode Shape - Freq.: ’,f2,’ Hz’]) pause;<br />
% (3.CASE) Increasing the Mass Values<br />
%__________________________________________________<br />
M1=m1+m2+m3; %concentrated mass [Kg] |<br />
M2=m4+m5+m6; %concentrated mass [Kg] |<br />
L1= 0.310; %length for positioning M1 [m] |<br />
L2= 0.610; %length for positioning M2 [m] |<br />
%__________________________________________________|<br />
...