ME 563 Mechanical Vibrations Fall 2010 1 1 ME 563 MECHANICAL VIBRATIONS Fall 2010 Potter MWF 4 30 p m 5 20 p m Instructor Prof D E Adams
the two shafts vibrating screen with inertia along the Y and X direction We will seek the vibration equa tion below Set the displacement in the x direction and y direc tion as follows Figure 2 The force diagram of inertial screen with two shafts y = λ y sin ωt −a y x = λ x sin ωt −a x 3 In which λ y λ xthe amplitude in
This work presents the development of a discrete parameter model consisting of a concentrated mass which is supported by a set of springs and dampers positioned in two orthogonal directions such that the mass can move horizontally and vertically in a plane A non ideal motor is attached to the mass such that the phenomenon of resonance capture can occur Resonance capture
If the input torque is increased to T = 480 Nm the estimated output shaft speed is 160 rad/s and the simulated average output shaft speed See Fig 3 a is 148 5 rad/s The system has escaped the resonance capture at about 20s which is associated with an upward speed jump together with a simultaneous reduction in torsional vibration amplitude and speed fluctuations of the input shaft
Yl 4 5 6 Contents 3 3 Balancing of Rotors 55 3 4 Whirling of Rotating Shafts 58 3 5 Support Motion 62 3 6 Vibration Isolation 64 3 7 Energy Dissipated by Damping 68 3 8 Equivalent Viscous Damping 72 3 9 Structural Damping 74 3 10 Sharpness of Resonance 76 3 11 Response to Periodic Forces 77 3 12 Vibration Measuring Instruments 78 TRANSIENT VIBRATION
Synchronization of two exciters with asymmetric structure is more widely used in engineering such as vibrating conveyer dewatering screen vibrating screen however the synchronization state of two exciters with asymmetric structure in the sub resonant and super resonant states is less considered and it is a valuable research topic Firstly we establish a kind of weakly nonlinear
The problem of controlled passage through resonance zone for mechanical systems with several degrees of freedom is studied Control algorithm design is based on speed gradient method and estimate for the frequency of the slow motion near resonance Blekhman frequency The simulation results for two rotor flexible vibration units illustrating efficiency of the proposed algorithms and fractal
Ch 1 Introduction of Mechanical Vibrations Modeling 1 1 That You Should Know Vibration is the repetitive motion of the system relative to a stationary frame of reference or nominal position
that of the vibrating system For example the motion of a double pendulum in planar motion can be represented completely either by θ θ1 2 the rotation of the first and second link respectively or by x y x y1 1 2 2 the Cartesian coordinates of first and second links While in the later case 4 coordinates are required to represent
The next step in large vibrating Screens Following extensive design effort using JOEST Australia FEA methods JOEST has commenced construction of a single deck screen 4 88 m wide 9 76 m long screening area 47m² The screen weighing 36 t will be installed in a Pilbara Iron Ore process plant in July this year To date
Shaft deflection runout vibration and axial motion Chapter D4 Page 7 Contact Kalsi Engineering Search this handbook Figure 6 Shaft deflection due to side load This schematic illustrates how an overhung side load produces lateral shaft deflection through flexure of the shaft When the location of the side load moves the deflection can impact
However inertia of the beam will cause the beam to vibrate around that initial location Assuming the elastic modulus inertia and cross sectional area A are constant along the beam length the equation for that vibration is Volterra p 310 3 where is the linear mass density of the beam Equation 3 is best solved by separation of
Synchronization of two exciters with asymmetric structure is more widely used in engineering such as vibrating conveyer dewatering screen vibrating screen however the synchronization state of two exciters with asymmetric structure in the sub resonant and super resonant states is less considered and it is a valuable research topic Firstly we establish a kind of weakly nonlinear
This work presents the development of a discrete parameter model consisting of a concentrated mass which is supported by a set of springs and dampers positioned in two orthogonal directions such that the mass can move horizontally and vertically in a plane A non ideal motor is attached to the mass such that the phenomenon of resonance capture can occur Resonance capture
Vibrational conveyers with a centrifugal vibration exciter transmit their load based on the jumping method The trough is oscillated by a common unbalanced mass driver This vibration causes the load to move forward and upward The motion is substantially related to the vibrational parameters The transition of the vibratory system for over resonance excited by rotating unbalances is important
FOUNDATIONS FOR VIBRATING MACHINES Special Issue April May 2006 of the Journal of Structural Engineering SERC Madras multiple of the operating frequency of the machine to avoid resonance with the higher harmonics A centrifuge has a 0 01 in 0 250 mm double amplitude at 750 rpm The value of the service factor from Table 1 is 2
The torsional vibration phenomenon in the running gear of reciprocating engine systems isusually dealt with by considering a series of constant inertias connected by sections of massless shafting However in reality a slider crank mechanism is a vibrating system with varying inertia because the effective inertia of the total oscillating mass of each crank assembly varies twice per revolution
Structural resonance Structural resonance refers to excessive vibrations of non rotating components usually machine parts or supporting structures Due to the complexity of these components it is the more common resonant condition and usually occurs at or near the rotating speed of the machine Even slight vibratory forces from residual
Keywords vibrating machine unbalanced rotor asynchronous electric motor resonant mode control system 1 Introduction One of the basic principles of creation of power efficient vibrational machines consists in using a resonant mode of the working body oscillations However in certain cases there is a problem
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vibration of machines that are mounted on floors or walls Obviously the best place to mount a vibrating machine is on the ground floor Unfortunately but fortunately for noise control consultants this is not always possible A typical problem is a rotating machine such as a pump AC compressor blower engine etc mounted on a roof or on
Excitation of poly harmon brations in single body vibration machine with inertia drive due to non linearity elastic clutch is investigated in 28 Design of nonlinear anti resonance vibrating s
Aiming at the shortcomings of traditional vibrating screens with large vibration mass a double eccentric cam self synchronous vibrating screen is proposed The motion differential equation of the vibrating screen system is derived by using Lagrange equation and the steady state solution is obtained According to Hamilton principle the synchronization condition of the vibration system is
the two shafts vibrating screen with inertia along the Y and X direction We will seek the vibration equa tion below Set the displacement in the x direction and y direc tion as follows Figure 2 The force diagram of inertial screen with two shafts y = λ y sin ωt −a y x = λ x sin ωt −a x 3 In which λ y λ xthe amplitude in
NOISE CONTROL Vibration Isolation 12 2 J S Lamancusa Penn State 5/28/2002 A vibration problem can also be nicely described by the same sourcepathreceiver model we previously used to characterize the noise control problem
4 3 Mathematical Analysis For a cantilever beam subjected to free vibration and the system is considered as continuous system in which the beam mass is considered as distributed along with the stiffness of the shaft the equation of motion can be written as Meirovitch 1967 4 1
Circular vibrating screen is single axis circular movement inertial vibrating screen whose working depends on inertial motor and inertial strength produced by eccentric plate Because of the vibration of screen box the materials are thrown out so that materials of certain size go through the screen mesh and the screening aim is realized
non linear dynamic of non linear systems subjected to double excitations Dimentberg et al 2001 that studied the self synchronization of rotors and Sommerfeld effect and Blekhman 1988 that studied the self synchronization of two unbalanced rotating machines mounted on a
Previous studies indicate that the separation efficiency of vibrating screen can be obviously increased through the double frequency synchronization motion between metal strap and gearbox but the large inertial load and impact load easily result in fatigue failure of the drive system
The double shaft inertia shaker centre of force theoretical that proposes is taught and non etc mass radius product follow motor synchronizing and synchronous regime Theory of Stability carries out calculating design according to Southwest Petrol University Zhang Minghong vibrating carrier screen box 8 has been installed two power
The linear vibrating screen uses an inertial vibration exciter to generate vibration and its vibration source is a motor belt Dynamic exciter the exciter has two shafts each shaft has an eccentric weight and in the opposite direction is also called double shaft vibrating screen which is
parameters for resonance appearance is to perform calculation of a free non damped torsional vibration i e to solve the equation MX KX 0 tt and build a resonance table or plot a Campbell diagram 1924 like shown on Fig 3 1 Fig 3 1 Campbell diagram for generator set vibration
brations in single body vibration machine with inertia drive due to non linearity in the elastic clutch is investigated in 28 Design of nonlinear anti resonance vibrating screen is described in 29 A changeable amplitude frequency mode is implemented in 30 for the vertical concrete compactor using interfer ed fields of vibration waves
The next step in large vibrating Screens Following extensive design effort using JOEST Australia FEA methods JOEST has commenced construction of a single deck screen 4 88 m wide 9 76 m long screening area 47m² The screen weighing 36 t will be installed in a Pilbara Iron Ore process plant in July this year To date
resonance regime of the vibrating screen by the use of shape memory alloy SMA springs to change the dynamic characteristics of the system 14 Springs made of high grade steelsare susceptible to cracks due to high cycle fatigue HCF Using traditional non destructive testing methods of diagnostics ultrasound magnetic etc is d ifficult to
The double layer high frequency vibrating screen machine is widely used in the tobacco industry and its controllability of vibration has a great influence on the screening quality of cut tobacco In this paper we obtain the factors affecting the motion characteristics of the vibrating screen by theoretical derivation and experimental measurement of the motion parameters of the double layer
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