SKATEBOARD: A HUMAN CONTROLLED NON-HOLONOMIC SYSTEM
|
|
- Gervais Fisher
- 6 years ago
- Views:
Transcription
1 Proceedings of the ASME 205 International Design Engineering Technical Conferences & Computers and Information in Engineering Conference IDETC/CIE 205 August 2-5, 205, Boston, Massachusetts, USA DETC SKATEBOARD: A HUMAN CONTROLLED NON-HOLONOMIC SYSTEM Balazs Varszegi Department of Applied Mechanics Budapest University of Technology and Economics Budapest, Hungary H- varszegi@mm.me.hu Denes Takacs MTA-BME Research Group on Dynamics of Machines and Vehicles Budapest, Hungary, H- takacs@mm.me.hu ABSTRACT A simple mechanical model of the skateoard-skater system is analyzed, in which a linear PD controller with delay is included to mimic the effect of human control. The equations of motion of the non-holonomic system are derived with the help of the Gis-Appell method. The linear staility analysis of rectilinear motion is carried out analytically using the D-sudivision method. It is shown how the control gains have to e varied with respect to the speed of the skateoard in order to stailize the uniform motion. The critical reflex delay of the skater is determined as a function of the speed and the fore-aft location of the skater on the oard. Based on these, an explanation is given for the well-known instaility of the skateoard-skater system at high speed. Gaor Stepan Department of Applied Mechanics Budapest University of Technology and Economics Budapest, Hungary, H- stepan@mm.me.hu ple, [3]) appear even nowadays. The speed dependent staility of non-holonomic systems still have unexplored ehaviors although their dynamics have een investigated for more than 00 years. This is clearly shown y recent pulications, where the lateral staility of the icycle and the three-dimensional iped walking machines are studied (see, for example, [4, 5]). Another interesting challenge is to explain the alancing effort of the person on the skateoard. Reflex delay in the control loop usually plays an important role in dynamical systems, as is shown y papers on the human alancing prolem from iological to engineering points of view [6 8]. In this paper, a mechanical model of the skateoard is constructed in which human control is taken into account. We can say, that the skater wants to control his angle y a torque at his ankle, what is produced y muscles. This is an usual approach in modeling of human control, when we model the human as a root, what is ale to act with forces and torques [6, 8]. INTRODUCTION Skateoard was invented only in 950 s and already enjoys worldwide popularity. The challenge of understanding the motion of the skateoard is due to the kinematic constraints and the complexity of the skater-skateoard system. If the skateoard is tilted around its longitudinal axis then the wheel-pairs also turn around their steering axes ecause of the wheel mounting geometry. This phenomenon makes the mechanical model non-holonomic and the equation of motion can e derived y means of the Gis-Appell method []. The effect of speed on the staility of the skateoard was investigated a not long after the invention of skateoards [2] ut pulications (see, for exam- So we use a very simple linear PD control loop to apply torque at the skaters ankle, and we also consider the reflex delay of human control. The staility analysis of the rectilinear motion is investigated analytically, and a case study is presented to emphasize the physical meaning of the results. Let us note here, other control models can etter represent the higher-frequency ehavior (for example McRuer approach [9]). This phenomenon can e investigated in further researches after this paper. Copyright 205 y ASME
2 m Z ϕ C h C m ϕ dinal direction of the skateoard; ϕ is the deflection angle of the skater from the vertical direction; and finally, β is the deflection angle of the oard (see Fig. ). As it is also shown in Fig., the rotation of the skateoard aout its longitudinal axis is resisted y the torsional spring of stiffness s t, which is originated in the special wheel suspension system of the skateoard. The rotation of the skater around the longitudinal axis of the skateoard is opposed y the internal torque of the PD controller. Herey, the rectilinear motion is considered as the desired motion, which means that zero torque is produced y the controller when the deflection angle of the skater is zero (i.e.: ϕ = 0). Thus, the control torque can e calculated as s t PD S R Z Y ψ X d S v R R S F V a l l FIGURE. THE MECHANICAL MODEL OF THE SKATEBOARD-SKATER SYSTEM THE MECHANICAL MODEL The mechanical model in question (see Fig. ) is ased on [3] and [0], where simpler mechanical models of the skateoard were used ut a human control-loop was also implemented. Here, a more realistic model is constructed, in which the oard and the skater can move separately and a control torque acts at the skater s ankle. The model consists of two massless rods. One of them models the skateoard etween the front (F) and rear (R) points. Although we neglect the mass of the oard its mass moment of inertia around its longitudinal axis is taken into account. The other rod etween the center point (S) of the contact patch etween the skater and the oard and the mass center (C) models the skater having a lumped mass. These two rods are connected y a hinge parallel to the longitudinal axis at the point S. The geometrical parameters are the following: 2h denotes the height of the skater, 2l is the length of the oard, a characterizes the location of the skater on the oard (a > 0 means that the skater stands in front of the center of the oard), the mass point m represents the mass of the skater, J is the mass moment of inertia of the skateoard around its longitudinal axis and g stands for of the gravity acceleration (g =9.8 [m/s 2 ]). In this study, we do not consider the loss of contact etween the wheels and the ground, consequently that the longitudinal axis of the skateoard is always parallel to the ground. One can choose five generalized coordinates to descrie the motion: X and Y are the coordinates of the point S; ψ descries the longitu- v F d S M PD (t) = Pϕ(t τ) + D ϕ(t τ), () where τ refers to the time delay, P and D represent the proportional and the differential control gains, respectively. Regarding the rolling wheels of the skateoard, kinematic constraining equations can e given for the velocities v F, v R of points F and R. The directions of the velocities of these points depend on the deflection angle β of the oard through the socalled steering angle δ S (see Fig. ). This connection can e descried y the expression: sinβ tanκ = tanδ S, (2) where κ is the fixed complementary angle of the so-called rake angle in the skateoard wheel suspension system [3, 0]. Based on this, two scalar kinematic constraining equations can e constructed: ( sinψ + cosψ sinβ tanκ)ẋ+ (cosψ + sinψ sinβ tanκ)ẏ + (l a) ψ = 0, (sinψ + cosψ sinβ tanκ)ẋ+ ( cosψ + sinψ sinβ tanκ)ẏ + (l + a) ψ = 0. We also introduce a third kinematic constraint, namely, the longitudinal speed V of the oard is kept constant: (3) (4) Ẋ cosψ +Ẏ cosψ = V. (5) We do not present details, ut it can e proven that the condition of the linear staility of rectilinear motion of skateoard remains the same even if the constraint Eqn. (5) does not hold, nevertheless, it makes our calculations simpler. Since all of the kinematic constraints (Eqns. (3) (5)) are linear cominations of the generalized velocities they can e written in the following form: A(q) q = A 0, (6) 2 Copyright 205 y ASME
3 where A = q T = [ X Y ψ φ β ], (7) [ ] cosψ sinβ tanκ sinψ sinψ sinβ tanκ + cosψ l a 0 0 cosψ sinβ tanκ + sinψ sinψ sinβ tanκ cosψ l + a 0 0, (8) cosψ sinψ where G refers to the center of the gravity of the ody and a G is the acceleration of G. The angular acceleration and the angular velocity are denoted y α and ω, respectively. The mass of the ody and its matrix of mass moment of inertia are m and J G, respectively. In case of skateoarding, there are two rigid odies: the skater with a lumped mass m at C and the oard with mass moment of inertia J around the hinge axis, while the mass of the oard is neglected compared to the mass of the skater. So the energy of acceleration forms: A T 0 = [ 0 0 V ]. (9) Note, that if the mass moment of inertia J of the oard is zero, then β and ϕ are not independent and β can e expressed as a function of ϕ and ϕ. Thus, the kinematic constraints are not linear functions of the generalized velocities if J = 0, and the Gis-Appell method can not e used. Therefore, we consider the case when J > 0. In order to apply the Gis-Appell equation (see in []), pseudo velocities have to e chosen, y which the kinematic constraints can e eliminated. In our case, two pseudo velocities are required since the difference of the numers of the generalized coordinates and the kinematic constraints is two. An appropriate choice can e the angular velocity components of the skater and the skateoard around the longitudinal axis, respectively: σ (t) := ϕ(t) and σ 2 (t) := β(t). (0) The generalized velocities can e expressed with the help of these two pseudo velocities and with the generalized coordinates: Ẋ V ( cosψ + a l tanκ sinβ sinψ) Ẏ ψ ϕ = V ( sinψ a l tanκ sinβ cosψ) V l tanκ sinβ σ. () β σ 2 The derivation of oth sides of this expression with respect to time leads to the generalized accelerations as functions of the pseudo accelerations, pseudo velocities and generalized coordinates. During the derivation of the equation of motion, the socalled energy of acceleration (A ) is needed. For a rigid ody it can e computed as: A = 2 ma G a G + 2 αt J G α+α T (ω (J G ω))+ 2 ωt (J G ω)ω 2, (2) A = mhv l 2 tanκ cosϕv sinβ(l htanκ sinβ sinϕ) σ + mhav l tanκ cosϕ cosβσ 2 σ + mh2 2 σ J cos 2 (2ψ) σ (3) The expressions that do not contain pseudo accelerations is not computed, ecause the equation of motion can e otained in the form: A σ i = Γ i, (4) where the right hand side is the pseudo force Γ i related to the ith pseudo velocity σ i. It can e determined from the virtual power of the active forces namely: the gravitational force, the torque produced y the controller and the torque produced y the spring: δp = mghsinϕδσ s t βδσ 2 + M PD (t)(δσ 2 δσ ), (5) where notation δ refers to the virtual quantities. Thus the equations of motion are: ( σ = sinϕ g h + V 2 tan 2 κ sin 2 β cosϕ l 2 a h V l tanκ cosβ cosϕσ 2 V 2 hl σ 2 = M PD(t) s t sinhβ, cos 2 (2ψ)J Ẋ = V ( cosψ + a l tanκ sinβ sinψ), Ẏ = V ( sinψ a l tanκ sinβ cosψ), ψ = V l tanκ sinβ, ϕ = σ, β = σ 2. ) h M PD(t)+ tanκ sinβ cosϕ, (6) Note that X, Y and ψ are cyclic coordinates, so only the first two and the last two equations of Eqn. (6) have to e used for our further investigation. LINEAR STABILITY ANALYSIS In this section we are going to investigate the linear staility of the rectilinear motion of a skateoard-skater system. First, we take the linearized equation of motion around the stationary 3 Copyright 205 y ASME
4 solution with respect to small perturations in σ, σ 2, ϕ and β. It can e written as where Ẋ(t) = J X(t) + T X(t τ), (7) 0 av hl tanκ g h V 2 hl tanκ σ (t) J = s t J 0 0 0, X(t) = σ 2 (t) ϕ(t), ψ(t) D 0 P 0 mh 2 mh 2 and T = J D 0 J P (8) The characteristic function D c (λ) can e determined y means of the sustitution of the trial solution X(t) = Ke λt (K C 4 and λ C) into Eqn. (7). It leads to: D c (λ) = V e λτ HJ l ( + e λτ mh 2 tanκe λτ (aλ +V )(Dλ + P)+ ) λ 2 + s t (Dλ J + mhe λτ ( hλ 2 g ) + P ) (9) and the characteristic equation can e written in the form D c (λ) = 0. This equation has infinitely many complex roots. The fixed point in question, i.e. the rectilinear motion, is asymptotically stale if and only if all of the characteristic roots are situated in the left-half of the complex plane. The limit of staility corresponds to the case when the characteristic roots are located at the imaginary axis for some particular system parameters. Two different types of staility oundaries can e distinguished; saddle-node (SN) ifurcation when oth the real and imaginary parts of the characteristic root are zero, and Hopf ifurcation when the characteristic roots are pure complex. In our model, SN ifurcation occurs if D c (0) = 0, namely: gs ( t J H + st mj H 2 + V 2 ) tanκ P = 0. (20) J hl The critical proportional gain P SN can e determined: P SN = mghls t mhv 2 tanκ + s t l. (2) In case of Hopf ifurcation, the critical characteristic exponent can e written as pure imaginary numers (λ H =±iω, TABLE. Hopf PARAMETERS OF THE SKATER-BOARD SYSTEM h [m] m [kg] a [m] τ [s] s t [Nm/rand] l [m] κ [ o ] J [kgm 2 ] D SN FIGURE 2. P SN ω D stale P ω D SN ω stale P STRUCTURE OF STABILITY CHART ω R + ). The characteristic equation D c (iω) can e separated into real and imaginary parts, which procedure is referred to D- sudivision method. The critical control gains can e expressed: where P H = p (ω)p 2 (ω) p 4 (ω), D H = p (ω)p 3 (ω) ω p 4 (ω), (22) p (ω) = 2hlmcosκ ( g + hω 2)( J ω 2 ) s t, p 2 (ω) = l cosκ ( J ω 2 ) s t cos(τω) mhv sinκ(aω sin(τω) +V cos(τω)), p 3 (ω) = l cosκ ( J ω 2 ) ( s t sin(τω) + mhv sinκ(aω cos(τω) V sin(τω)), p 4 (ω) = cos(2κ) l 2 ( s t J ω 2) 2 h 2 m 2 V 2 ( a 2 ω 2 +V 2)) + l 2 ( s t J ω 2) m 2 h 2 V 2 ( a 2 ω 2 +V 2) + 2mhlV 2 sin(2κ) ( s t J ω 2). (23) Let us construct the linear staility chart of the rectilinear motion in the P D parameter plane (see in Fig. 2) for the realistic parameters of Ta.. The staility oundary given y Eqn. (22) starts like in case of the PD controlled inverted pendulum [6], ut it does not spiral outwards continuously. Actually it will cross the origin of the parameter plane at ω = ω, where st ω = (24) J is the natural angular frequency of the skateoard without control (i.e. P = 0 and D = 0 corresponds to the switched off control). As a consequence, a loop of the staility oundary is showing up like for the simplified model in [0]). It can e proved, that only the internal region of this loop can e stale. As a summary, there are three different oundaries of the stale parameter domain: 4 Copyright 205 y ASME
5 τ a [s] a = 0. [m] stailizale for only skater s front position a = - 0. [m] stailizale for any skater s position V [m/s] FIGURE 3. THE EFFECT OF THE SPEED ON THE ULTIMATE REFLEX TIME the SN for static loss of staility and a low-frequency and a highfrequency Hopf ifurcation. One can verify, that the aove descried closed loop of Hopf oundaries rotates counterclockwise around the origin as the reflex delay τ increases. EFFECTS OF THE LONGITUDINAL SPEED AND THE REFLEX DELAY When the effects of a human controller are neglected it can e shown that the higher the speed, the easier it is to stailize the skateoard [2, 3]. However, a more complex picture arises when the human control is taken into consideration. This was recognized in [0] using a simpler mechanical model that also exhiits rotating closed loop staility oundaries in the P D parameter plane. Here we determine the necessary and sufficient conditions to stailize the skateoard with respect to the skater s reaction time. A condition can e developed y examining the starting point of the D-curve. If the curve starts to the left hand side at ω = 0 then stale domain can not exist. This leads to the ultimate critical time delay τ cr,u of the controller. If the delay is larger than this value, then the investigated equilirium is for sure. Fig. 3 shows the variation of the ultimate time delay versus the longitudinal speed for two different cases. The continuous line corresponds to a = 0.m, i.e. the skater stands ahead of the center of the skateoard, while the dashed line corresponds to a = 0.m, i.e. the skater stands ehind the center of the oard. As it can e oserved in the figure, the maximal time delay, y which the system can e stailized, is larger for any speed when the skater stands in front of the center point of the oard. However, in case of smaller reflex delay, the stailization of the rectilinear motion is possile even when the skater stands ehind the center of the oard. This can also e confirmed y practical experiences. Previous models without control-loop do not explain such ehaviors of the skateoard. For example, it is proved in [2, 3] that the stailizale stailizale stailizale stailizale FIGURE 4. BILITY a = [m] a = 0.05 [m] V=2 [m/s] V=3 [m/s] V=5 [m/s] V=7 [m/s] THE EFFECT OF THE REFLEX TIME ON THE STA- rectilinear motion cannot e stale for any speed in case a < 0. Figure 3 also represents that the skater s position is more relevant at low speeds ut oth curves of the ultimate critical delays tend to the same value as the speed tends to infinity. Independently from the skater s position, the critical time delay is also the same at zero speed. The curves of Fig. 3 are characterized y where τ V 0 ut,max = 2 ω 2 s and ω s = τ V ut,max = 2 ω 2 s τ [s] ω 2, (25) g h. (26) The ultimate reflex time at zero speed (τut,max) V 0 is identical with the critical time delay of the human alancing prolem [6]. Based on the formulas, it is easy to show that τut,max V 0 > τut,max V ut the difference is very small for realistic parameters. For example, the parameters of Ta. leads to 0.04% relative difference due to the fact that the natural angular frequency ω is very high. The ultimate critical time (see in Fig. 3) is close, ut higher, to the human reflex delay for hand [7]. As it was mentioned, former studies [3] proved that the system is for a < 0. Here we show that this statement can e reconsidered in some special cases, moreover, standing ehind the center of the oard can e even advantageous. In order to do this, the effect of the reflex time has to e investigated in more details. In Fig. 4, the existence of the stale P D parameter domain is illustrated versus the reflex delay. The figures are constructed for different longitudinal speeds. The continuous and the dashed lines elong to a = 0.05m and a = 0.05m, respectively. It can e oserved that the condition τ < τ ut,max is not sufficient from point of view of the staility. There are several reflex time ranges, where the system is not stailizale for any control gains, which is due to the rotation of the Hopf loop around the origin 5 Copyright 205 y ASME
6 D [Nms] stale 0 stale V=.2 [m/s] V=.5 [m/s] V=2.25 [m/s] control gains, which can enlarge the effects of the dead-zones of the human control. Clearly, the skater cannot apply close to zero control torque and cannot even sense very small tilting angles of the oard. In human alancing models, the existences of dead-zones are also suspected as the reason of micro-chaotic and transient-chaotic virations around linearly equilirium with large surviving times [8]. V= 3.5 [m/s] V=7 [m/s] P [Nm] FIGURE 5. STABLE PARAMETER DOMAIN FOR DIFFERENT LONGITUDINAL SPEEDS ACKNOWLEDGMENT This research was partly supported y the Janos Bolyai Research Scholarship of the Hungarian Academy of Sciences and y the Hungarian National Science Foundation under grant no. OTKA PD with increasing τ. However, the locations of these ranges depend on the standing positions, namely, in some cases a > 0, in other cases a < 0 can lead to stale rectilinear motion. Nevertheless, if the speed tends to infinity, the applicale time delay ranges do not depend on the skater s position anymore. Having a time delay elow the sharp critical value is not enough to ensure stale rectilinear motion, the choice of adequate control gains (P and D) is also important. The variation of the stale domains in the P D parameter plane can e seen in Fig. 5 for τ = 0.24s and for different speeds. The stale domain tends to the origin (P = 0, D = 0) as the speed increases. As a consequence, the skater has to tune the control parameters more and more precisely in order to catch the very narrower and narrower stale parameter domain at increasing high speeds. Nevertheless, the switching off of the control (i.e., P = 0 and D = 0) could e a solution ut only at infinite (very high) speed. CONCLUSION A mechanical model of the skateoard-skater system was constructed, in which the effect of the human alancing was taken into account y a linear delayed PD controller. The reflex time of the skater was also considered. The staility of the rectilinear motion of the skateoard was analyzed and staility charts were composed with special attention to the effects of the reflex time and the longitudinal speed. Time delays were determined for realistic parameters, y which the skateoarding can e performed. The effect of the skater s position on the oard was also investigated. It was verified, that the variation of the skater s position can qualitatively influence the staility of the rectilinear motion. The presented staility charts can also explain the loss of staility at high speed. The stale parameter domain of the control gains reduces and its location tends towards the origin as the speed increases. As a consequence, the skater must decrease the REFERENCES [] Gantmacher, F., 975. Lectures in Analytical Mechanics. MIR Pulisher, Moscow, Russia. [2] Huard, M., 980. Human control of the skateoard. Journal of Biomechanics, 3, pp [3] Kremnev, A. V., and Kuleshov, A. S., Dynamics and simulation of the simplest model of skateoard. In Proceedings of Sixth EUROMECH Nonlinear Dynamics Conference. [4] Kooijman, J. D. G., Meijaard, J. P., Papadopoulos, J. M., Ruina, A., and Schwa, A. L., 20. A icycle can e self-stale without gyroscopic or caster effects. Science, 332, pp [5] Wisse, M., and A, S., Skateoard, icycles, and three-dimensional iped walking machines: Velocitydependent staility y means of lean-to-yaw coupling. The International Journal of Rootics Research, 24(6), pp [6] Stepan, G., Delay effects in the human sensory system during alancing. Philosophical Transactions of The Royal Society, 367, pp [7] Milton, J., Solodkin, A., Hlustik, P., and Small, S. L., The mind of expert motor performance is cool and focused. NeuroImage, 35, pp [8] Insperger, T., and Milton, J., 204. Sensory uncertainty and stick alancing at the fingertip. Biological Cyernetics, 08, pp [9] McRuer, D. T., Weir, D. H., Jex, H. R., Magdeleno, R. E., and Allen, E. W., 975. Measurement of driver-vehicle multiloop response properties with a single disturance input. IEEE Transactions on systems, Man, and Cyernetics, SMC-5, pp [0] Varszegi, B., Takacs, D., Stepan, G., and Hogan, S. J., 204. Balancing of the skateoard with reflex delay. In Proceedings of Eighth EUROMECH Nonlinear Dynamics Conference, ENOC Copyright 205 y ASME
Balancing of the skateboard with reflex delay
ENOC 214, July 6-11, 214, Vienna, Austria Balancing of the skateboard with reflex delay Balazs Varszegi, Denes Takacs, Gabor Stepan and S. John Hogan Department of Applied Mechanics, Budapest University
More informationUniversity of Bristol - Explore Bristol Research. Peer reviewed version. Link to published version (if available): /rsif.2016.
Varszegi, B., Takacs, D., Stepan, G., & Hogan, J. 2016). Stabilizing skateboard speed-wobble with reflex delay. Journal of the Royal Society Interface, 13121), [20160345]. DOI: 10.1098/rsif.2016.0345 Peer
More informationStability of towed wheels in cornering manoeuvre
Stability of towed wheels in cornering manoeuvre Henrik Sykora Department of Applied Mechanics, Budapest niversity of Technology and Economics, Budapest, Hungary Dénes Takács MTA-BME Research Group on
More informationHierarchical steering control for a front wheel drive automated car
Hierarchical steering control for a front wheel drive automated car Sándor Beregi, Dénes Takács, Chaozhe R. He, Sergei S. Avedisov, Gábor Orosz Department of Applied Mechanics, Budapest University of Technology
More informationSection 8.5. z(t) = be ix(t). (8.5.1) Figure A pendulum. ż = ibẋe ix (8.5.2) (8.5.3) = ( bẋ 2 cos(x) bẍ sin(x)) + i( bẋ 2 sin(x) + bẍ cos(x)).
Difference Equations to Differential Equations Section 8.5 Applications: Pendulums Mass-Spring Systems In this section we will investigate two applications of our work in Section 8.4. First, we will consider
More informationExact Free Vibration of Webs Moving Axially at High Speed
Eact Free Viration of Wes Moving Aially at High Speed S. HATAMI *, M. AZHARI, MM. SAADATPOUR, P. MEMARZADEH *Department of Engineering, Yasouj University, Yasouj Department of Civil Engineering, Isfahan
More informationComments on A Time Delay Controller for Systems with Uncertain Dynamics
Comments on A Time Delay Controller for Systems with Uncertain Dynamics Qing-Chang Zhong Dept. of Electrical & Electronic Engineering Imperial College of Science, Technology, and Medicine Exhiition Rd.,
More informationSolution: (a) (b) (N) F X =0: A X =0 (N) F Y =0: A Y + B Y (54)(9.81) 36(9.81)=0
Prolem 5.6 The masses of the person and the diving oard are 54 kg and 36 kg, respectivel. ssume that the are in equilirium. (a) Draw the free-od diagram of the diving oard. () Determine the reactions at
More informationLecture Notes Multibody Dynamics B, wb1413
Lecture Notes Multibody Dynamics B, wb1413 A. L. Schwab & Guido M.J. Delhaes Laboratory for Engineering Mechanics Mechanical Engineering Delft University of Technolgy The Netherlands June 9, 29 Contents
More informationExperimental investigation of micro-chaos
Experimental investigation of micro-chaos Gergely Gyebrószki Gábor Csernák Csaba Budai Department of Applied Mechanics Budapest University of Technology and Economics Budapest Hungary MTA-BME Research
More informationDesign Parameter Sensitivity Analysis of High-Speed Motorized Spindle Systems Considering High-Speed Effects
Proceedings of the 2007 IEEE International Conference on Mechatronics and Automation August 5-8, 2007, Harin, China Design Parameter Sensitivity Analysis of High-Speed Motorized Spindle Systems Considering
More informationMath 216 Second Midterm 28 March, 2013
Math 26 Second Midterm 28 March, 23 This sample exam is provided to serve as one component of your studying for this exam in this course. Please note that it is not guaranteed to cover the material that
More informationThe single track model
The single track model Dr. M. Gerdts Uniersität Bayreuth, SS 2003 Contents 1 Single track model 1 1.1 Geometry.................................... 1 1.2 Computation of slip angles...........................
More informationEffect of Uniform Horizontal Magnetic Field on Thermal Instability in A Rotating Micropolar Fluid Saturating A Porous Medium
IOSR Journal of Mathematics (IOSR-JM) e-issn: 78-578, p-issn: 39-765X. Volume, Issue Ver. III (Jan. - Fe. 06), 5-65 www.iosrjournals.org Effect of Uniform Horizontal Magnetic Field on Thermal Instaility
More informationF. C. Moon (ed.), Applications of Nonlinear and Chaotic Dynamics in Mechanics, Kluwer Academic Publisher, Dordrecht, 1998, pp
F. C. Moon (ed.), Applications of Nonlinear and Chaotic Dynamics in Mechanics, Kluwer Academic Publisher, Dordrecht, 1998, pp. 373-386. DELAY, NONLINEAR OSCILLATIONS AND SHIMMYING WHEELS G. STÉPÁN Department
More informationImpedance Control for a Free-Floating Robot in the Grasping of a Tumbling Target with Parameter Uncertainty
Impedance Control for a Free-Floating Root in the Grasping of a Tumling Target with arameter Uncertainty Satoko Aiko, Roerto ampariello and Gerd Hirzinger Institute of Rootics and Mechatronics German Aerospace
More informationTyre induced vibrations of the car-trailer system
Tyre induced vibrations of the car-trailer system S. Beregi a, D. Takács b, G. Stépán a a Department of Applied Mechanics, Budapest University of Technology and Economics b MTA-BME Research Group on Dynamics
More information506. Modeling and diagnostics of gyroscopic rotor
506. Modeling and diagnostics of gyroscopic rotor V. Barzdaitis 1,a, M. Bogdevičius 2,, R. Didžiokas 3,c, M. Vasylius 3,d 1 Kaunas University of Technology, Department of Engineering Mechanics, Donelaičio
More informationAssignments VIII and IX, PHYS 301 (Classical Mechanics) Spring 2014 Due 3/21/14 at start of class
Assignments VIII and IX, PHYS 301 (Classical Mechanics) Spring 2014 Due 3/21/14 at start of class Homeworks VIII and IX both center on Lagrangian mechanics and involve many of the same skills. Therefore,
More informationBuckling Behavior of Long Symmetrically Laminated Plates Subjected to Shear and Linearly Varying Axial Edge Loads
NASA Technical Paper 3659 Buckling Behavior of Long Symmetrically Laminated Plates Sujected to Shear and Linearly Varying Axial Edge Loads Michael P. Nemeth Langley Research Center Hampton, Virginia National
More informationStabilization of Motion of the Segway 1
Stabilization of Motion of the Segway 1 Houtman P. Siregar, 2 Yuri G. Martynenko 1 Department of Mechatronics Engineering, Indonesia Institute of Technology, Jl. Raya Puspiptek-Serpong, Indonesia 15320,
More informationInvestigation of a Ball Screw Feed Drive System Based on Dynamic Modeling for Motion Control
Investigation of a Ball Screw Feed Drive System Based on Dynamic Modeling for Motion Control Yi-Cheng Huang *, Xiang-Yuan Chen Department of Mechatronics Engineering, National Changhua University of Education,
More informationMathematical Modeling and response analysis of mechanical systems are the subjects of this chapter.
Chapter 3 Mechanical Systems A. Bazoune 3.1 INRODUCION Mathematical Modeling and response analysis of mechanical systems are the subjects of this chapter. 3. MECHANICAL ELEMENS Any mechanical system consists
More informationDistributed control of "ball on beam" system
XI International PhD Workshop OWD 29, 17 2 Octoer 29 Distriuted control of "all on eam" system Michał Ganois, University of Science and Technology AGH Astract This paper presents possiilities of control
More informationSOLVING DYNAMICS OF QUIET STANDING AS NONLINEAR POLYNOMIAL SYSTEMS
SOLVING DYNAMICS OF QUIET STANDING AS NONLINEAR POLYNOMIAL SYSTEMS Zhiming Ji Department of Mechanical Engineering, New Jersey Institute of Technology, Newark, New Jersey 070 ji@njit.edu Abstract Many
More information1 Systems of Differential Equations
March, 20 7- Systems of Differential Equations Let U e an open suset of R n, I e an open interval in R and : I R n R n e a function from I R n to R n The equation ẋ = ft, x is called a first order ordinary
More informationRobot Control Basics CS 685
Robot Control Basics CS 685 Control basics Use some concepts from control theory to understand and learn how to control robots Control Theory general field studies control and understanding of behavior
More informationExperimental Comparison of Adaptive Controllers for Trajectory Tracking in Agricultural Robotics
Experimental Comparison of Adaptive Controllers for Trajectory Tracking in Agricultural Rootics Jarle Dørum, Tryve Utstumo, Jan Tommy Gravdahl Department of Engineering Cyernetics Norwegian University
More informationMathematical Modelling And Simulation of Quadrotor
IOSR Journal of Electrical and Electronics Engineering (IOSR-JEEE) e-issn: 78-1676,p-ISSN: 3-3331, Volume 1, Issue 6 Ver. II (Nov. Dec. 17), PP 11-18 www.iosrjournals.org Mathematical Modelling And Simulation
More informationDynamic Optimization of Geneva Mechanisms
Dynamic Optimization of Geneva Mechanisms Vivek A. Suan and Marco A. Meggiolaro Department of Mechanical Engineering Massachusetts Institute of Technology Camridge, MA 09 ABSTRACT The Geneva wheel is the
More informationMotion Analysis of Euler s Disk
Motion Analysis of Euler s Disk Katsuhiko Yaada Osaka University) Euler s Disk is a nae of a scientific toy and its otion is the sae as a spinning coin. In this study, a siple atheatical odel is proposed
More informationSWING UP A DOUBLE PENDULUM BY SIMPLE FEEDBACK CONTROL
ENOC 2008, Saint Petersburg, Russia, June, 30 July, 4 2008 SWING UP A DOUBLE PENDULUM BY SIMPLE FEEDBACK CONTROL Jan Awrejcewicz Department of Automatics and Biomechanics Technical University of Łódź 1/15
More informationUNIT-I (FORCE ANALYSIS)
DHANALAKSHMI SRINIVASAN INSTITUTE OF RESEACH AND TECHNOLOGY DEPARTMENT OF MECHANICAL ENGINEERING QUESTION BANK ME2302 DYNAMICS OF MACHINERY III YEAR/ V SEMESTER UNIT-I (FORCE ANALYSIS) PART-A (2 marks)
More informationDESIGN SUPPORT FOR MOTION CONTROL SYSTEMS Application to the Philips Fast Component Mounter
DESIGN SUPPORT FOR MOTION CONTROL SYSTEMS Application to the Philips Fast Component Mounter Hendri J. Coelingh, Theo J.A. de Vries and Jo van Amerongen Dreel Institute for Systems Engineering, EL-RT, University
More informationP = ρ{ g a } + µ 2 V II. FLUID STATICS
II. FLUID STATICS From a force analysis on a triangular fluid element at rest, the following three concepts are easily developed: For a continuous, hydrostatic, shear free fluid: 1. Pressure is constant
More informationLab 11: Rotational Dynamics
Lab 11: Rotational Dynamics Objectives: To understand the relationship between net torque and angular acceleration. To understand the concept of the moment of inertia. To understand the concept of angular
More informationChapter 9. Rotational Dynamics
Chapter 9 Rotational Dynamics 9.1 The Action of Forces and Torques on Rigid Objects In pure translational motion, all points on an object travel on parallel paths. The most general motion is a combination
More informationIsolated large amplitude periodic motions of towed rigid wheels
Nonlinear Dyn 2008) 52: 27 34 DOI 10.1007/s11071-007-9253-y ORIGINAL PAPER Isolated large amplitude periodic motions of towed rigid wheels Dénes Takács Gábor Stépán S. John Hogan Received: 8 August 2006
More informationME 323 Examination #2
ME 33 Eamination # SOUTION Novemer 14, 17 ROEM NO. 1 3 points ma. The cantilever eam D of the ending stiffness is sujected to a concentrated moment M at C. The eam is also supported y a roller at. Using
More informationFinQuiz Notes
Reading 9 A time series is any series of data that varies over time e.g. the quarterly sales for a company during the past five years or daily returns of a security. When assumptions of the regression
More information= o + t = ot + ½ t 2 = o + 2
Chapters 8-9 Rotational Kinematics and Dynamics Rotational motion Rotational motion refers to the motion of an object or system that spins about an axis. The axis of rotation is the line about which the
More informationEXAMPLE 2: CLASSICAL MECHANICS: Worked examples. b) Position and velocity as integrals. Michaelmas Term Lectures Prof M.
CLASSICAL MECHANICS: Worked examples Michaelmas Term 2006 4 Lectures Prof M. Brouard EXAMPLE 2: b) Position and velocity as integrals Calculate the position of a particle given its time dependent acceleration:
More informationConcept Question: Normal Force
Concept Question: Normal Force Consider a person standing in an elevator that is accelerating upward. The upward normal force N exerted by the elevator floor on the person is 1. larger than 2. identical
More informationChapter 8 Rotational Motion
Chapter 8 Rotational Motion Chapter 8 Rotational Motion In this chapter you will: Learn how to describe and measure rotational motion. Learn how torque changes rotational velocity. Explore factors that
More informationRotational Kinetic Energy
Lecture 17, Chapter 10: Rotational Energy and Angular Momentum 1 Rotational Kinetic Energy Consider a rigid body rotating with an angular velocity ω about an axis. Clearly every point in the rigid body
More informationTransient stabilization of an inverted pendulum with digital control
12th IFAC Symposium on Robot Control, Budapest, Hungary, August 27-3, 218. Paper No. 18. Transient stabilization of an inverted pendulum with digital control Gergely Geza Lublovary, Tamas Insperger Department
More informationragsdale (zdr82) HW7 ditmire (58335) 1 The magnetic force is
ragsdale (zdr8) HW7 ditmire (585) This print-out should have 8 questions. Multiple-choice questions ma continue on the net column or page find all choices efore answering. 00 0.0 points A wire carring
More informationThe Simplest Model of the Turning Movement of a Car with its Possible Sideslip
TECHNISCHE MECHANIK, Band 29, Heft 1, (2009), 1 12 Manuskripteingang: 19. November 2007 The Simplest Model of the Turning Movement of a Car with its Possible Sideslip A.B. Byachkov, C. Cattani, E.M. Nosova,
More informationTextbook Reference: Wilson, Buffa, Lou: Chapter 8 Glencoe Physics: Chapter 8
AP Physics Rotational Motion Introduction: Which moves with greater speed on a merry-go-round - a horse near the center or one near the outside? Your answer probably depends on whether you are considering
More information8.012 Physics I: Classical Mechanics Fall 2008
MIT OpenCourseWare http://ocw.mit.edu 8.012 Physics I: Classical Mechanics Fall 2008 For information about citing these materials or our Terms of Use, visit: http://ocw.mit.edu/terms. MASSACHUSETTS INSTITUTE
More informationExpansion formula using properties of dot product (analogous to FOIL in algebra): u v 2 u v u v u u 2u v v v u 2 2u v v 2
Least squares: Mathematical theory Below we provide the "vector space" formulation, and solution, of the least squares prolem. While not strictly necessary until we ring in the machinery of matrix algera,
More informationGyroscopes and statics
Gyroscopes and statics Announcements: Welcome back from Spring Break! CAPA due Friday at 10pm We will finish Chapter 11 in H+R on angular momentum and start Chapter 12 on stability. Friday we will begin
More informationChaos and Dynamical Systems
Chaos and Dynamical Systems y Megan Richards Astract: In this paper, we will discuss the notion of chaos. We will start y introducing certain mathematical concepts needed in the understanding of chaos,
More informationPADEU. The 1 : 2 resonance in the Sitnikov problem. 1 Introduction. T. Kovács 1
PADEU PADEU 7, (6) ISBN 963 463 557, ISSN 38-43 c Pulished y the Astron. Dept. of the Eötvös Univ. The : resonance in the Sitnikov prolem T. Kovács Eötvös University, Department of Astronomy, H-58 Budapest,
More informationExam 3 Practice Solutions
Exam 3 Practice Solutions Multiple Choice 1. A thin hoop, a solid disk, and a solid sphere, each with the same mass and radius, are at rest at the top of an inclined plane. If all three are released at
More informationPhysics 201. Professor P. Q. Hung. 311B, Physics Building. Physics 201 p. 1/1
Physics 201 p. 1/1 Physics 201 Professor P. Q. Hung 311B, Physics Building Physics 201 p. 2/1 Rotational Kinematics and Energy Rotational Kinetic Energy, Moment of Inertia All elements inside the rigid
More informationTorque and Rotation Lecture 7
Torque and Rotation Lecture 7 ˆ In this lecture we finally move beyond a simple particle in our mechanical analysis of motion. ˆ Now we consider the so-called rigid body. Essentially, a particle with extension
More informationPhys 7221 Homework # 8
Phys 71 Homework # 8 Gabriela González November 15, 6 Derivation 5-6: Torque free symmetric top In a torque free, symmetric top, with I x = I y = I, the angular velocity vector ω in body coordinates with
More informationECEN 420 LINEAR CONTROL SYSTEMS. Lecture 6 Mathematical Representation of Physical Systems II 1/67
1/67 ECEN 420 LINEAR CONTROL SYSTEMS Lecture 6 Mathematical Representation of Physical Systems II State Variable Models for Dynamic Systems u 1 u 2 u ṙ. Internal Variables x 1, x 2 x n y 1 y 2. y m Figure
More informationLecture 38: Equations of Rigid-Body Motion
Lecture 38: Equations of Rigid-Body Motion It s going to be easiest to find the equations of motion for the object in the body frame i.e., the frame where the axes are principal axes In general, we can
More informationAMS 147 Computational Methods and Applications Lecture 13 Copyright by Hongyun Wang, UCSC
Lecture 13 Copyright y Hongyun Wang, UCSC Recap: Fitting to exact data *) Data: ( x j, y j ), j = 1,,, N y j = f x j *) Polynomial fitting Gis phenomenon *) Cuic spline Convergence of cuic spline *) Application
More informationChapter 9. Rotational Dynamics
Chapter 9 Rotational Dynamics 9.1 The Action of Forces and Torques on Rigid Objects In pure translational motion, all points on an object travel on parallel paths. The most general motion is a combination
More informationChapter 9. Rotational Dynamics
Chapter 9 Rotational Dynamics In pure translational motion, all points on an object travel on parallel paths. The most general motion is a combination of translation and rotation. 1) Torque Produces angular
More informationMCE 366 System Dynamics, Spring Problem Set 2. Solutions to Set 2
MCE 366 System Dynamics, Spring 2012 Problem Set 2 Reading: Chapter 2, Sections 2.3 and 2.4, Chapter 3, Sections 3.1 and 3.2 Problems: 2.22, 2.24, 2.26, 2.31, 3.4(a, b, d), 3.5 Solutions to Set 2 2.22
More informationWEEKS 8-9 Dynamics of Machinery
WEEKS 8-9 Dynamics of Machinery References Theory of Machines and Mechanisms, J.J.Uicker, G.R.Pennock ve J.E. Shigley, 2011 Mechanical Vibrations, Singiresu S. Rao, 2010 Mechanical Vibrations: Theory and
More informationDynamical Systems Solutions to Exercises
Dynamical Systems Part 5-6 Dr G Bowtell Dynamical Systems Solutions to Exercises. Figure : Phase diagrams for i, ii and iii respectively. Only fixed point is at the origin since the equations are linear
More informationSolving Homogeneous Trees of Sturm-Liouville Equations using an Infinite Order Determinant Method
Paper Civil-Comp Press, Proceedings of the Eleventh International Conference on Computational Structures Technology,.H.V. Topping, Editor), Civil-Comp Press, Stirlingshire, Scotland Solving Homogeneous
More informationReview for 3 rd Midterm
Review for 3 rd Midterm Midterm is on 4/19 at 7:30pm in the same rooms as before You are allowed one double sided sheet of paper with any handwritten notes you like. The moment-of-inertia about the center-of-mass
More informationFor a rigid body that is constrained to rotate about a fixed axis, the gravitational torque about the axis is
Experiment 14 The Physical Pendulum The period of oscillation of a physical pendulum is found to a high degree of accuracy by two methods: theory and experiment. The values are then compared. Theory For
More information557. Radial correction controllers of gyroscopic stabilizer
557. Radial correction controllers of gyroscopic stabilizer M. Sivčák 1, J. Škoda, Technical University in Liberec, Studentská, Liberec, Czech Republic e-mail: 1 michal.sivcak@tul.cz; jan.skoda@pevnosti.cz
More informationSingle-track models of an A-double heavy vehicle combination
Single-track models of an A-double heavy vehicle combination PETER NILSSON KRISTOFFER TAGESSON Department of Applied Mechanics Division of Vehicle Engineering and Autonomous Systems Vehicle Dynamics Group
More informationProblem Set x Classical Mechanics, Fall 2016 Massachusetts Institute of Technology. 1. Moment of Inertia: Disc and Washer
8.01x Classical Mechanics, Fall 2016 Massachusetts Institute of Technology Problem Set 10 1. Moment of Inertia: Disc and Washer (a) A thin uniform disc of mass M and radius R is mounted on an axis passing
More informationRobotics. Dynamics. Marc Toussaint U Stuttgart
Robotics Dynamics 1D point mass, damping & oscillation, PID, dynamics of mechanical systems, Euler-Lagrange equation, Newton-Euler recursion, general robot dynamics, joint space control, reference trajectory
More informationTechnische Universität Berlin
Technische Universität Berlin Institut für Mathematik M7 - A Skateboard(v1.) Andreas Steinbrecher Preprint 216/8 Preprint-Reihe des Instituts für Mathematik Technische Universität Berlin http://www.math.tu-berlin.de/preprints
More informationNumerical Study of Heat Propagation in Living Tissue Subjected to Instantaneous Heating
Indian Journal of Biomechanics: Special Issue (NCBM 7-8 March 9) Numerical Study of Heat Propagation in Living Tissue Sujected to Instantaneous Heating P. R. Sharma 1, Sazid Ali, V. K. Katiyar 1 Department
More informationChapter 8 Rotational Motion and Equilibrium. 1. Give explanation of torque in own words after doing balance-the-torques lab as an inquiry introduction
Chapter 8 Rotational Motion and Equilibrium Name 1. Give explanation of torque in own words after doing balance-the-torques lab as an inquiry introduction 1. The distance between a turning axis and the
More informationSTATE-DEPENDENT, NON-SMOOTH MODEL OF CHATTER VIBRATIONS IN TURNING
Proceedings of the ASME 215 International Design Engineering Technical Conferences & Computers and Information in Engineering Conference IDETC/CIE 215 August 2-5, 215, Boston, Massachusetts, USA DETC215-46748
More informationExploring the relationship between a fluid container s geometry and when it will balance on edge
Exploring the relationship eteen a fluid container s geometry and hen it ill alance on edge Ryan J. Moriarty California Polytechnic State University Contents 1 Rectangular container 1 1.1 The first geometric
More informationLecture 38: Equations of Rigid-Body Motion
Lecture 38: Equations of Rigid-Body Motion It s going to be easiest to find the equations of motion for the object in the body frame i.e., the frame where the axes are principal axes In general, we can
More informationOn Temporal Instability of Electrically Forced Axisymmetric Jets with Variable Applied Field and Nonzero Basic State Velocity
Availale at http://pvamu.edu/aam Appl. Appl. Math. ISSN: 19-966 Vol. 6, Issue 1 (June 11) pp. 7 (Previously, Vol. 6, Issue 11, pp. 1767 178) Applications and Applied Mathematics: An International Journal
More informationRotation. Rotational Variables
Rotation Rigid Bodies Rotation variables Constant angular acceleration Rotational KE Rotational Inertia Rotational Variables Rotation of a rigid body About a fixed rotation axis. Rigid Body an object that
More informationAnalytical estimations of limit cycle amplitude for delay-differential equations
Electronic Journal of Qualitative Theory of Differential Equations 2016, No. 77, 1 10; doi: 10.14232/ejqtde.2016.1.77 http://www.math.u-szeged.hu/ejqtde/ Analytical estimations of limit cycle amplitude
More informationGame Physics. Game and Media Technology Master Program - Utrecht University. Dr. Nicolas Pronost
Game and Media Technology Master Program - Utrecht University Dr. Nicolas Pronost Rigid body physics Particle system Most simple instance of a physics system Each object (body) is a particle Each particle
More informationEXPERIMENT 7: ANGULAR KINEMATICS AND TORQUE (V_3)
TA name Lab section Date TA Initials (on completion) Name UW Student ID # Lab Partner(s) EXPERIMENT 7: ANGULAR KINEMATICS AND TORQUE (V_3) 121 Textbook Reference: Knight, Chapter 13.1-3, 6. SYNOPSIS In
More informationPhysics 218 Exam 3 Spring 2010, Sections
Physics 8 Exam 3 Spring 00, Sections 5-55 Do not fill out the information below until instructed to do so! Name Signature Student ID E-mail Section # Rules of the exam:. You have the full class period
More informationLecture 13 REVIEW. Physics 106 Spring What should we know? What should we know? Newton s Laws
Lecture 13 REVIEW Physics 106 Spring 2006 http://web.njit.edu/~sirenko/ What should we know? Vectors addition, subtraction, scalar and vector multiplication Trigonometric functions sinθ, cos θ, tan θ,
More informationEnergy-Rate Method and Stability Chart of Parametric Vibrating Systems
Reza N. Jazar Reza.Jazar@manhattan.edu Department of Mechanical Engineering Manhattan College New York, NY, A M. Mahinfalah Mahinfalah@msoe.edu Department of Mechanical Engineering Milwaukee chool of Engineering
More informationLecture 6 Physics 106 Spring 2006
Lecture 6 Physics 106 Spring 2006 Angular Momentum Rolling Angular Momentum: Definition: Angular Momentum for rotation System of particles: Torque: l = r m v sinφ l = I ω [kg m 2 /s] http://web.njit.edu/~sirenko/
More informationCEE 271: Applied Mechanics II, Dynamics Lecture 27: Ch.18, Sec.1 5
1 / 42 CEE 271: Applied Mechanics II, Dynamics Lecture 27: Ch.18, Sec.1 5 Prof. Albert S. Kim Civil and Environmental Engineering, University of Hawaii at Manoa Tuesday, November 27, 2012 2 / 42 KINETIC
More informationLecture 14. Rotational dynamics Torque. Give me a lever long enough and a fulcrum on which to place it, and I shall move the world.
Lecture 14 Rotational dynamics Torque Give me a lever long enough and a fulcrum on which to place it, and I shall move the world. Archimedes, 87 1 BC EXAM Tuesday March 6, 018 8:15 PM 9:45 PM Today s Topics:
More informationBig Idea 4: Interactions between systems can result in changes in those systems. Essential Knowledge 4.D.1: Torque, angular velocity, angular
Unit 7: Rotational Motion (angular kinematics, dynamics, momentum & energy) Name: Big Idea 3: The interactions of an object with other objects can be described by forces. Essential Knowledge 3.F.1: Only
More informationEQUIVALENT SINGLE-DEGREE-OF-FREEDOM SYSTEM AND FREE VIBRATION
1 EQUIVALENT SINGLE-DEGREE-OF-FREEDOM SYSTEM AND FREE VIBRATION The course on Mechanical Vibration is an important part of the Mechanical Engineering undergraduate curriculum. It is necessary for the development
More informationDYNAMICAL MODELING AN INTERDISCIPLINARY APPROACH OF THE ECONOMIC REALITY
DYNAMICAL MODELING AN INTERDISCIPLINARY APPROACH OF THE ECONOMIC REALITY Assoc. Prof. Laura Ungureanu, Spiru Haret University Craiova, Romania Assoc. Prof. Ion Viorel Matei Spiru Haret University Craiova,
More informationPhysics 207: Lecture 24. Announcements. No labs next week, May 2 5 Exam 3 review session: Wed, May 4 from 8:00 9:30 pm; here.
Physics 07: Lecture 4 Announcements No labs next week, May 5 Exam 3 review session: Wed, May 4 from 8:00 9:30 pm; here Today s Agenda ecap: otational dynamics and torque Work and energy with example Many
More informationLANMARK UNIVERSITY OMU-ARAN, KWARA STATE DEPARTMENT OF MECHANICAL ENGINEERING COURSE: MECHANICS OF MACHINE (MCE 322). LECTURER: ENGR.
LANMARK UNIVERSITY OMU-ARAN, KWARA STATE DEPARTMENT OF MECHANICAL ENGINEERING COURSE: MECHANICS OF MACHINE (MCE 322). LECTURER: ENGR. IBIKUNLE ROTIMI ADEDAYO SIMPLE HARMONIC MOTION. Introduction Consider
More informationPHYS2330 Intermediate Mechanics Fall Final Exam Tuesday, 21 Dec 2010
Name: PHYS2330 Intermediate Mechanics Fall 2010 Final Exam Tuesday, 21 Dec 2010 This exam has two parts. Part I has 20 multiple choice questions, worth two points each. Part II consists of six relatively
More informationChapter 14 Periodic Motion
Chapter 14 Periodic Motion 1 Describing Oscillation First, we want to describe the kinematical and dynamical quantities associated with Simple Harmonic Motion (SHM), for example, x, v x, a x, and F x.
More informationIM4. Modul Mechanics. Coupled Pendulum
IM4 Modul Mechanics Coupled Pendulum Two pendulums that can exchange energy are called coupled pendulums. The gravitational force acting on the pendulums creates rotational stiffness that drives each pendulum
More informationSelected Topics in Physics a lecture course for 1st year students by W.B. von Schlippe Spring Semester 2007
Selected Topics in Physics a lecture course for st year students by W.B. von Schlippe Spring Semester 7 Lecture : Oscillations simple harmonic oscillations; coupled oscillations; beats; damped oscillations;
More informationMembers Subjected to Torsional Loads
Members Subjected to Torsional Loads Torsion of circular shafts Definition of Torsion: Consider a shaft rigidly clamped at one end and twisted at the other end by a torque T = F.d applied in a plane perpendicular
More information