Free Vibration of Pre-Tensioned Electromagnetic NanobeamsIOSRJM
The transverse free vibration of electromagnetic nanobeams subjected to an initial axial tension based on nonlocal stress theory is presented. It considers the effects of nonlocal stress field on the natural frequencies and vibration modes. The effects of a small-scale parameter at molecular level unavailable in classical macro-beams are investigated for three different types of boundary conditions: simple supports, clamped supports and elastically constrained supports. Analytical solutions for transverse deformation and vibration modes are derived. Through numerical examples, effects of the dimensionless Hartmann number, nano-scale parameter andpre-tension on natural frequencies are presented and discussed.
Oscillatory Behaviors of Second Order Forced Functional Differential Equation.IOSR Journals
Oscillatory behaviors of second order forced functional differential equation is considered. The
oscillation of this equation is shown to be maintained under the effect of certain forcing terms, and the
oscillatory equation can serve as mathematical tool for simulation of processes and phenomina observed in
control theory.
Mechanical Vibrations Theory and Applications 1st Edition Kelly Solutions Manualvilyku
Full download http://alibabadownload.com/product/mechanical-vibrations-theory-and-applications-1st-edition-kelly-solutions-manual/
Mechanical Vibrations Theory and Applications 1st Edition Kelly Solutions Manual
Free Vibration of Pre-Tensioned Electromagnetic NanobeamsIOSRJM
The transverse free vibration of electromagnetic nanobeams subjected to an initial axial tension based on nonlocal stress theory is presented. It considers the effects of nonlocal stress field on the natural frequencies and vibration modes. The effects of a small-scale parameter at molecular level unavailable in classical macro-beams are investigated for three different types of boundary conditions: simple supports, clamped supports and elastically constrained supports. Analytical solutions for transverse deformation and vibration modes are derived. Through numerical examples, effects of the dimensionless Hartmann number, nano-scale parameter andpre-tension on natural frequencies are presented and discussed.
Oscillatory Behaviors of Second Order Forced Functional Differential Equation.IOSR Journals
Oscillatory behaviors of second order forced functional differential equation is considered. The
oscillation of this equation is shown to be maintained under the effect of certain forcing terms, and the
oscillatory equation can serve as mathematical tool for simulation of processes and phenomina observed in
control theory.
Mechanical Vibrations Theory and Applications 1st Edition Kelly Solutions Manualvilyku
Full download http://alibabadownload.com/product/mechanical-vibrations-theory-and-applications-1st-edition-kelly-solutions-manual/
Mechanical Vibrations Theory and Applications 1st Edition Kelly Solutions Manual
Single degree of freedom system free vibration part -i and iiSachin Patil
Dynamics of Machinery Unit -I ( SPPU Pune) Single Degree of Freedom Free Vibration - Fundamentals of Vibration , Determination of natural Frequency , Problems on Spring in Series and Parallel , Problems on Equilibrium and Energy Method
single degree of freedom systems forced vibrations KESHAV
SDOF, Forced vibration
includes following content
Forced vibrations of longitudinal and torsional systems,
Frequency Response to harmonic excitation,
excitation due to rotating and reciprocating unbalance,
base excitation, magnification factor,
Force and Motion transmissibility,
Quality Factor.
Half power bandwidth method,
Critical speed of shaft having single rotor of undamped systems.
Identification of coulomb, viscous and particle damping parameters from the r...ijiert bestjournal
This paper deals with Theoretical and Experimental methods for identification of coulomb ,Viscous and Particle
damping parameters from the response of Single degree of freedom harmonically forced linear oscillator when
system damped with more than one type of damping ,which parameter is responsible for the control of resonant
response of vibrating systems, in experimental method setup have been presented to investigate steady state
response amplitude xi for SDOF system for different values of amplitude Yi of the base excitation from this
relationship of (Xi ,Yi) the values of viscous damping coefficient „c‟ and coulomb friction force F0 ,also
equivalent viscous damping ratios ,have been calculated from frequency response analysis for the systems with
viscous damping ,Viscous and Coulomb friction damping, coulomb friction damping and particle damping by
using half power band-width method and in theoretical studies expression for steady state amplitude X0
obtained is used to study the effect of frequency ratio and coulomb friction parameters on phase angle and
amplitude ratio.
This paper proposed a nonlinear robust control for spacecraft attitude based on passivity and
disturbance suppression vector. The spacecraft model was described using quaternion. The control law
introduced the suppression vector of external disturbances and had no information related to the system
parameters. The desired performance of spacecraft attitude control could be achieved using the designed
control law. And stability conditions of the nonlinear robust control for spacecraft attitude were given. The
stability could be proved by applying Lyapunov approach. The verification of the proposed attitude control
method was performed through a series of simulations. The numerical results showed the effectiveness of
the proposed control method in controlling the spacecraft attitude in the presence of external disturbances.
The main benefit of the proposed attitude control method does not need angular velocity measurement
and has its robustness against model uncertainties and external disturbances.
What is a continuous structure?
How to analyse the vibration of string, bars and shafts?
How to analyse the vibration of beams?
#WikiCourses
https://wikicourses.wikispaces.com/Topic+Vibration+of+Continuous+Structures
https://eau-esa.wikispaces.com/Vibration+of+structures
Single degree of freedom system free vibration part -i and iiSachin Patil
Dynamics of Machinery Unit -I ( SPPU Pune) Single Degree of Freedom Free Vibration - Fundamentals of Vibration , Determination of natural Frequency , Problems on Spring in Series and Parallel , Problems on Equilibrium and Energy Method
single degree of freedom systems forced vibrations KESHAV
SDOF, Forced vibration
includes following content
Forced vibrations of longitudinal and torsional systems,
Frequency Response to harmonic excitation,
excitation due to rotating and reciprocating unbalance,
base excitation, magnification factor,
Force and Motion transmissibility,
Quality Factor.
Half power bandwidth method,
Critical speed of shaft having single rotor of undamped systems.
Identification of coulomb, viscous and particle damping parameters from the r...ijiert bestjournal
This paper deals with Theoretical and Experimental methods for identification of coulomb ,Viscous and Particle
damping parameters from the response of Single degree of freedom harmonically forced linear oscillator when
system damped with more than one type of damping ,which parameter is responsible for the control of resonant
response of vibrating systems, in experimental method setup have been presented to investigate steady state
response amplitude xi for SDOF system for different values of amplitude Yi of the base excitation from this
relationship of (Xi ,Yi) the values of viscous damping coefficient „c‟ and coulomb friction force F0 ,also
equivalent viscous damping ratios ,have been calculated from frequency response analysis for the systems with
viscous damping ,Viscous and Coulomb friction damping, coulomb friction damping and particle damping by
using half power band-width method and in theoretical studies expression for steady state amplitude X0
obtained is used to study the effect of frequency ratio and coulomb friction parameters on phase angle and
amplitude ratio.
This paper proposed a nonlinear robust control for spacecraft attitude based on passivity and
disturbance suppression vector. The spacecraft model was described using quaternion. The control law
introduced the suppression vector of external disturbances and had no information related to the system
parameters. The desired performance of spacecraft attitude control could be achieved using the designed
control law. And stability conditions of the nonlinear robust control for spacecraft attitude were given. The
stability could be proved by applying Lyapunov approach. The verification of the proposed attitude control
method was performed through a series of simulations. The numerical results showed the effectiveness of
the proposed control method in controlling the spacecraft attitude in the presence of external disturbances.
The main benefit of the proposed attitude control method does not need angular velocity measurement
and has its robustness against model uncertainties and external disturbances.
What is a continuous structure?
How to analyse the vibration of string, bars and shafts?
How to analyse the vibration of beams?
#WikiCourses
https://wikicourses.wikispaces.com/Topic+Vibration+of+Continuous+Structures
https://eau-esa.wikispaces.com/Vibration+of+structures
Evaluation of Vibrational Behavior for A System With TwoDegree-of-Freedom Und...IJERA Editor
Analysis of the vibrational behavior of a system is extremely important, both for the evaluation of operating conditions, as performance and safety reason. The studies on vibration concentrate their efforts on understanding the natural phenomena and the development of mathematical theories to describe the vibration of physical systems. The purpose of this study is to evaluate an undamped system with two-degrees-of-freedom and demonstrate by comparing the results obtained in the experimental, numerical and analytical modeling the characteristics that describe a structure in terms of its natural characteristics. The experiment was conducted in PUC-MG where the data were acquired to determine the natural frequency of the system. We also developed an experimental test bed for vibrations studies for graduate and undergraduate students. In analytical modeling were represented all the important aspects of the system. In order, to obtain the mathematical equations is used MATLAB to solve the equations that describe the characteristics of system behavior. For the simulation and numerical solution of the system, we use a computational tool ABAQUS. The comparison between the results obtained in the experiment and the numerical was considered satisfactory using the exact solutions. This study demonstrates that calculation of the adopted conditions on a system with two-degrees-of-freedom can be applied to complex systems with many degrees of freedom and proved to be an excellent learning tool for determining the modal analysis of a system. One of the goals is to use the developed platform to be used as a didactical experiment system for vibration and modal analysis classes at PUC Minas. The idea is to give the students an opportunity to test, play, calculate and confirm the results in vibration and modal analysis in a low-cost platform
In this article free vibration of a nonlinear cyclic symmetry system is examined. The system is composed of six identical beams which are fixed at the end. The coupling between beams is introduced via a nonlinear stiffness running between two consecutive beams. The equations of motion are as a system of second order nonlinear differential equations which are coupled by cubic nonlinear terms. To solve the equations of motion, the numerical methods are used, and the results are compared with those of the harmonic balance method. The effect of nonlinear stiffness on the backbone curves is examined. The results show that the effect of nonlinear stiffness is increased as the diametrical mode number is increased from 1 to 3, whereas there is no effect on zero-diameter mode.
A new two-scroll chaotic system with two nonlinearities: dynamical analysis a...TELKOMNIKA JOURNAL
Chaos theory has several applications in science and engineering. In this work, we announce a
new two-scroll chaotic system with two nonlinearities. The dynamical properties of the system such as
dissipativity, equilibrium points, Lyapunov exponents, Kaplan-Yorke dimension and bifurcation diagram are
explored in detail. The presence of coexisting chaotic attractors, coexisting chaotic and periodic attractors
in the system is also investigated. In addition, the offset boosting of a variable in the new chaotic system is
achieved by adding a single controlled constant. It is shown that the new chaotic system has rotation
symmetry about the z-axis. An electronic circuit simulation of the new two-scroll chaotic system is built
using Multisim to check the feasibility of the theoretical model.
Higher-Order Squeezing of a Generic Quadratically-Coupled Optomechanical SystemIOSRJAP
Using short-time dynamics and analytical solution of Heisenberg equation of motion for the Hamiltonian of quadratically-coupled optomechanical system for different field modes, we have investigated the existence of higher-order single mode squeezing, sum squeezing and difference squeezing in absence of driving and dissipation. Depth of squeezing increases with order number for higher-order single mode squeezing. Squeezing factor exhibits a series of revival-collapse phenomena for single mode, which becomes more pronounced as order number increases. In case of sum squeezing amounts of squeezing is greater than single mode higher-order squeezing (n = 2). It is also greater than from difference squeezing for same set of interaction parameters. Sum squeezing is prominently better for extracting information regarding squeezing.
A REVIEW OF NONLINEAR FLEXURAL-TORSIONAL VIBRATION OF A CANTILEVER BEAMijiert bestjournal
A beam is an elongated member,usually slender,intended to resist lateral loads by bending (Cook,1999). Structures such as antennas,helicopter rotor blades,aircraft wing s,towers and high rise buildings are examples of beams. These beam-like structures are typically subjected to dynamic loads. Therefore,the vibration of beams is of particular interest to the engineer. The paper reviews the derivation by Crespo da Silva and Glyn (1978) for the nonlinear flexural-flexural-torsional vibration of a cant ilever beam. Also the numerical algorithm used to solve the equation of motion for the planar vibration of the beam subjected to harmonic excitation at the base.
Investigate the Route of Chaos Induced Instabilities in Power System NetworkIJMER
In this paper possible causes of various instability and chances of system break down in a
power system network are investigated based on theory of nonlinear dynamics applied to a Power system
network. Here a simple three bus power system model is used for the analysis. First the routes to chaotic
oscillation through various oscillatory modes are completely determined. Then it is shown that chaotic
oscillation eventually leads to system break-down characterized by collapse of system voltage and large
deviation in Generator rotor angle (angle divergence), also known as chaos induced instability. It has
been shown that chaos and chaos induced instability in Power system take place due to the variation in
system parameters and the inherent nonlinear nature of the power system network. The relation between
chaotic oscillation and various system instabilities are discussed here. Using the simple power system
model, here it is shown that how chaos leads to voltage collapse and angle divergence, taken place
simultaneously when the stability condition of the chaotic oscillation are broken. All nonlinear analysis
is implemented using MATLAB. It is indicated that there is a maximum lodability point after which the
system enters into instability modes. All these studies are helpful to understand the mechanism of various
instability modes and to find out effective anti-chaos strategies to prevent power system instability.
Modified Projective Synchronization of Chaotic Systems with Noise Disturbance,...IJECEIAES
The synchronization problem of chaotic systems using active modified projective non- linear control method is rarely addressed. Thus the concentration of this study is to derive a modified projective controller to synchronize the two chaotic systems. Since, the parameter of the master and follower systems are considered known, so active methods are employed instead of adaptive methods. The validity of the proposed controller is studied by means of the Lyapunov stability theorem. Furthermore, some numerical simulations are shown to verify the validity of the theoretical discussions. The results demonstrate the effectiveness of the proposed method in both speed and accuracy points of views.
Modeling of the damped oscillations of the viscous beams structures with swiv...eSAT Journals
Abstract
Mechanic studies realized on the two dimensional beams structures with swivel joints show that in statics, the vertical displacement is
continuous, but the rotation is discontinuous at the node where there is a swivel joint. Moreover, in dynamics, many authors do not
usually take into account the friction effect, modeling of these structures. We propose in this paper, a modeling of the beams structures
with swivel joints which integrates viscosity effects in dynamics. Hence this work we will present the formulation of motion equations
of such structures and the modal analysis method which is used to solve these equations.
Keywords: Beams, Swivel joint, Viscosity, Vibration, Modal Method.
ADAPTIVE CONTROL AND SYNCHRONIZATION OF A HIGHLY CHAOTIC ATTRACTORijistjournal
Recently, a novel three-dimensional highly chaotic attractor has been discovered by Srisuchinwong and Munmuangsaen (2010). This paper investigates the adaptive control and synchronization of this highly chaotic attractor with unknown parameters. First, adaptive control laws are designed to stabilize the highly chaotic system to its unstable equilibrium point at the origin based on the adaptive control theory and Lyapunov stability theory. Then adaptive control laws are derived to achieve global chaos synchronization of identical highly chaotic systems with unknown parameters. Numerical simulations are shown to demonstrate the effectiveness of the proposed adaptive control and synchronization schemes.
ADAPTIVE CONTROL AND SYNCHRONIZATION OF A HIGHLY CHAOTIC ATTRACTORijistjournal
Recently, a novel three-dimensional highly chaotic attractor has been discovered by Srisuchinwong and Munmuangsaen (2010). This paper investigates the adaptive control and synchronization of this highly chaotic attractor with unknown parameters. First, adaptive control laws are designed to stabilize the highly chaotic system to its unstable equilibrium point at the origin based on the adaptive control theory and Lyapunov stability theory. Then adaptive control laws are derived to achieve global chaos synchronization of identical highly chaotic systems with unknown parameters. Numerical simulations are shown to demonstrate the effectiveness of the proposed adaptive control and synchronization schemes.
IJRET : International Journal of Research in Engineering and Technology is an international peer reviewed, online journal published by eSAT Publishing House for the enhancement of research in various disciplines of Engineering and Technology. The aim and scope of the journal is to provide an academic medium and an important reference for the advancement and dissemination of research results that support high-level learning, teaching and research in the fields of Engineering and Technology. We bring together Scientists, Academician, Field Engineers, Scholars and Students of related fields of Engineering and Technology.
vertical response of a hereditary deformable systemIJAEMSJORNAL
An investigation of a viscoelastic material damping effect is studied on an example of plenum air-cushion craft model. A numerical investigation was conducted to determine the vertical response characteristic of an open plenum air-cushion structure. The pure vertical motion of an air-cushion structure is investigated using a non-linear mathematical model; this incorporates a simple model to account hereditary deformable characteristic of the material.
Vibration analysis of line continuum with new matrices of elastic and inertia...eSAT Publishing House
IJRET : International Journal of Research in Engineering and Technology is an international peer reviewed, online journal published by eSAT Publishing House for the enhancement of research in various disciplines of Engineering and Technology. The aim and scope of the journal is to provide an academic medium and an important reference for the advancement and dissemination of research results that support high-level learning, teaching and research in the fields of Engineering and Technology. We bring together Scientists, Academician, Field Engineers, Scholars and Students of related fields of Engineering and Technology
UiPath Test Automation using UiPath Test Suite series, part 4DianaGray10
Welcome to UiPath Test Automation using UiPath Test Suite series part 4. In this session, we will cover Test Manager overview along with SAP heatmap.
The UiPath Test Manager overview with SAP heatmap webinar offers a concise yet comprehensive exploration of the role of a Test Manager within SAP environments, coupled with the utilization of heatmaps for effective testing strategies.
Participants will gain insights into the responsibilities, challenges, and best practices associated with test management in SAP projects. Additionally, the webinar delves into the significance of heatmaps as a visual aid for identifying testing priorities, areas of risk, and resource allocation within SAP landscapes. Through this session, attendees can expect to enhance their understanding of test management principles while learning practical approaches to optimize testing processes in SAP environments using heatmap visualization techniques
What will you get from this session?
1. Insights into SAP testing best practices
2. Heatmap utilization for testing
3. Optimization of testing processes
4. Demo
Topics covered:
Execution from the test manager
Orchestrator execution result
Defect reporting
SAP heatmap example with demo
Speaker:
Deepak Rai, Automation Practice Lead, Boundaryless Group and UiPath MVP
Welocme to ViralQR, your best QR code generator.ViralQR
Welcome to ViralQR, your best QR code generator available on the market!
At ViralQR, we design static and dynamic QR codes. Our mission is to make business operations easier and customer engagement more powerful through the use of QR technology. Be it a small-scale business or a huge enterprise, our easy-to-use platform provides multiple choices that can be tailored according to your company's branding and marketing strategies.
Our Vision
We are here to make the process of creating QR codes easy and smooth, thus enhancing customer interaction and making business more fluid. We very strongly believe in the ability of QR codes to change the world for businesses in their interaction with customers and are set on making that technology accessible and usable far and wide.
Our Achievements
Ever since its inception, we have successfully served many clients by offering QR codes in their marketing, service delivery, and collection of feedback across various industries. Our platform has been recognized for its ease of use and amazing features, which helped a business to make QR codes.
Our Services
At ViralQR, here is a comprehensive suite of services that caters to your very needs:
Static QR Codes: Create free static QR codes. These QR codes are able to store significant information such as URLs, vCards, plain text, emails and SMS, Wi-Fi credentials, and Bitcoin addresses.
Dynamic QR codes: These also have all the advanced features but are subscription-based. They can directly link to PDF files, images, micro-landing pages, social accounts, review forms, business pages, and applications. In addition, they can be branded with CTAs, frames, patterns, colors, and logos to enhance your branding.
Pricing and Packages
Additionally, there is a 14-day free offer to ViralQR, which is an exceptional opportunity for new users to take a feel of this platform. One can easily subscribe from there and experience the full dynamic of using QR codes. The subscription plans are not only meant for business; they are priced very flexibly so that literally every business could afford to benefit from our service.
Why choose us?
ViralQR will provide services for marketing, advertising, catering, retail, and the like. The QR codes can be posted on fliers, packaging, merchandise, and banners, as well as to substitute for cash and cards in a restaurant or coffee shop. With QR codes integrated into your business, improve customer engagement and streamline operations.
Comprehensive Analytics
Subscribers of ViralQR receive detailed analytics and tracking tools in light of having a view of the core values of QR code performance. Our analytics dashboard shows aggregate views and unique views, as well as detailed information about each impression, including time, device, browser, and estimated location by city and country.
So, thank you for choosing ViralQR; we have an offer of nothing but the best in terms of QR code services to meet business diversity!
Observability Concepts EVERY Developer Should Know -- DeveloperWeek Europe.pdfPaige Cruz
Monitoring and observability aren’t traditionally found in software curriculums and many of us cobble this knowledge together from whatever vendor or ecosystem we were first introduced to and whatever is a part of your current company’s observability stack.
While the dev and ops silo continues to crumble….many organizations still relegate monitoring & observability as the purview of ops, infra and SRE teams. This is a mistake - achieving a highly observable system requires collaboration up and down the stack.
I, a former op, would like to extend an invitation to all application developers to join the observability party will share these foundational concepts to build on:
A tale of scale & speed: How the US Navy is enabling software delivery from l...sonjaschweigert1
Rapid and secure feature delivery is a goal across every application team and every branch of the DoD. The Navy’s DevSecOps platform, Party Barge, has achieved:
- Reduction in onboarding time from 5 weeks to 1 day
- Improved developer experience and productivity through actionable findings and reduction of false positives
- Maintenance of superior security standards and inherent policy enforcement with Authorization to Operate (ATO)
Development teams can ship efficiently and ensure applications are cyber ready for Navy Authorizing Officials (AOs). In this webinar, Sigma Defense and Anchore will give attendees a look behind the scenes and demo secure pipeline automation and security artifacts that speed up application ATO and time to production.
We will cover:
- How to remove silos in DevSecOps
- How to build efficient development pipeline roles and component templates
- How to deliver security artifacts that matter for ATO’s (SBOMs, vulnerability reports, and policy evidence)
- How to streamline operations with automated policy checks on container images
GraphRAG is All You need? LLM & Knowledge GraphGuy Korland
Guy Korland, CEO and Co-founder of FalkorDB, will review two articles on the integration of language models with knowledge graphs.
1. Unifying Large Language Models and Knowledge Graphs: A Roadmap.
https://arxiv.org/abs/2306.08302
2. Microsoft Research's GraphRAG paper and a review paper on various uses of knowledge graphs:
https://www.microsoft.com/en-us/research/blog/graphrag-unlocking-llm-discovery-on-narrative-private-data/
Le nuove frontiere dell'AI nell'RPA con UiPath Autopilot™UiPathCommunity
In questo evento online gratuito, organizzato dalla Community Italiana di UiPath, potrai esplorare le nuove funzionalità di Autopilot, il tool che integra l'Intelligenza Artificiale nei processi di sviluppo e utilizzo delle Automazioni.
📕 Vedremo insieme alcuni esempi dell'utilizzo di Autopilot in diversi tool della Suite UiPath:
Autopilot per Studio Web
Autopilot per Studio
Autopilot per Apps
Clipboard AI
GenAI applicata alla Document Understanding
👨🏫👨💻 Speakers:
Stefano Negro, UiPath MVPx3, RPA Tech Lead @ BSP Consultant
Flavio Martinelli, UiPath MVP 2023, Technical Account Manager @UiPath
Andrei Tasca, RPA Solutions Team Lead @NTT Data
Smart TV Buyer Insights Survey 2024 by 91mobiles.pdf91mobiles
91mobiles recently conducted a Smart TV Buyer Insights Survey in which we asked over 3,000 respondents about the TV they own, aspects they look at on a new TV, and their TV buying preferences.
Elevating Tactical DDD Patterns Through Object CalisthenicsDorra BARTAGUIZ
After immersing yourself in the blue book and its red counterpart, attending DDD-focused conferences, and applying tactical patterns, you're left with a crucial question: How do I ensure my design is effective? Tactical patterns within Domain-Driven Design (DDD) serve as guiding principles for creating clear and manageable domain models. However, achieving success with these patterns requires additional guidance. Interestingly, we've observed that a set of constraints initially designed for training purposes remarkably aligns with effective pattern implementation, offering a more ‘mechanical’ approach. Let's explore together how Object Calisthenics can elevate the design of your tactical DDD patterns, offering concrete help for those venturing into DDD for the first time!
Builder.ai Founder Sachin Dev Duggal's Strategic Approach to Create an Innova...Ramesh Iyer
In today's fast-changing business world, Companies that adapt and embrace new ideas often need help to keep up with the competition. However, fostering a culture of innovation takes much work. It takes vision, leadership and willingness to take risks in the right proportion. Sachin Dev Duggal, co-founder of Builder.ai, has perfected the art of this balance, creating a company culture where creativity and growth are nurtured at each stage.
SAP Sapphire 2024 - ASUG301 building better apps with SAP Fiori.pdfPeter Spielvogel
Building better applications for business users with SAP Fiori.
• What is SAP Fiori and why it matters to you
• How a better user experience drives measurable business benefits
• How to get started with SAP Fiori today
• How SAP Fiori elements accelerates application development
• How SAP Build Code includes SAP Fiori tools and other generative artificial intelligence capabilities
• How SAP Fiori paves the way for using AI in SAP apps
PHP Frameworks: I want to break free (IPC Berlin 2024)Ralf Eggert
In this presentation, we examine the challenges and limitations of relying too heavily on PHP frameworks in web development. We discuss the history of PHP and its frameworks to understand how this dependence has evolved. The focus will be on providing concrete tips and strategies to reduce reliance on these frameworks, based on real-world examples and practical considerations. The goal is to equip developers with the skills and knowledge to create more flexible and future-proof web applications. We'll explore the importance of maintaining autonomy in a rapidly changing tech landscape and how to make informed decisions in PHP development.
This talk is aimed at encouraging a more independent approach to using PHP frameworks, moving towards a more flexible and future-proof approach to PHP development.
Dev Dives: Train smarter, not harder – active learning and UiPath LLMs for do...UiPathCommunity
💥 Speed, accuracy, and scaling – discover the superpowers of GenAI in action with UiPath Document Understanding and Communications Mining™:
See how to accelerate model training and optimize model performance with active learning
Learn about the latest enhancements to out-of-the-box document processing – with little to no training required
Get an exclusive demo of the new family of UiPath LLMs – GenAI models specialized for processing different types of documents and messages
This is a hands-on session specifically designed for automation developers and AI enthusiasts seeking to enhance their knowledge in leveraging the latest intelligent document processing capabilities offered by UiPath.
Speakers:
👨🏫 Andras Palfi, Senior Product Manager, UiPath
👩🏫 Lenka Dulovicova, Product Program Manager, UiPath
When stars align: studies in data quality, knowledge graphs, and machine lear...
Pages from jam 12-1185 author-proof-2
1. PROOF COPY [JAM-12-1185]
Vladimir Stojanovic´1
Department of Mechanical Engineering,
University of Nisˇ,
Medvedeva 14,
18000 Nisˇ, Serbia
e-mail: stojanovic.s.vladimir@gmail.com
Marko Petkovic´
Department of Science and Mathematics,
University of Nisˇ,
Visˇegradska 33,
18000 Nisˇ, Serbia
Moment Lyapunov Exponents
1 and Stochastic Stability of a
Three-Dimensional System
2 on Elastic Foundation Using
3 a Perturbation Approach4
5 In this paper, the stochastic stability of the three elastically connected Euler beams on
elastic foundation is studied. The model is given as three coupled oscillators. Stochastic
stability conditions are expressed by the Lyapunov exponent and moment Lyapunov expo-
nents. It is determined that the new set of transformation for getting It^o differential equa-
tions can be applied for any system of three coupled oscillators. The method of regular
perturbation is used to determine the asymptotic expressions for these exponents in the
presence of small intensity noises. Analytical results are presented for the almost sure
and moment stability of a stochastic dynamical system. The results are applied to study
the moment stability of the complex structure with influence of the white noise excitation
due to the axial compressive stochastic load. [DOI: 10.1115/1.4023519]
Keywords: Winkler elastic layer, stochastic stability, perturbation, moment Lyapunov
6 exponent
7 1 Introduction
8 Frequent uncontrolled influences of the earthquakes, winds, and
9 waves, theoretical knowledge of the behavior of complex struc-
10 tures become more important.AQ1 Vibration and especially problems
11 of stochastic instability of beams or beam-columns on elastic
12 foundations occupy an important place in many fields of structural
13 and foundation engineering. This problem is very often encountered
14 in aeronautical, mechanical, and civil engineering applications. The
15 present work contains two parts in introduction to describe the fol-
16 lowing model. In the first is given past work of researchers who did
17 investigation of elastically connected beams, and the second part
18 focuses on the research in the field of stochastic stability.
19 Fundamental early work was conducted by Hyer et al. [1,2],
20 who made the theoretical and experimental investigation in non-
21 linear vibrations of the three-beam system with viscoelastic cores.
22 Researchers also have studied the vibrations of elastically con-
23 nected triple beams with effects of rotary inertia and shear [3].
24 Kelly and Srinivas [4] investigated the problem of the free vibra-
25 tions of a set of n axially loaded stretched Bernoulli–Euler beams
26 connected by elastic layers and connected to a Winkler-type foun-
27 dation. A normal-mode solution is applied to the governing partial
28 differential equations to derive a set of coupled ordinary differen-
29 tial equations, which are used to determine the natural frequencies
30 and mode shapes. It is shown that the set of differential equations
31 can be written in self-adjoint form with an appropriate inner prod-
32 uct. An exact solution for the general case is obtained, but numeri-
33 cal procedures must be used to determine the natural frequencies
34 and mode shapes. The numerical procedure is difficult to apply,
35 especially in determining higher frequencies. For the special case
36 of identical beams, an exact expression for the natural frequencies
37 is obtained in terms of the natural frequencies of a corresponding
38set of unstretched beams and the eigenvalues of the coupling
39matrix. Basic theoretical fundaments were used for a triple system
40of sandwich beams [5]. Stojanovic´ et al. [6] presented a general
41procedure for the determination of the natural frequencies and
42static stability for a set of beam systems under compressive axial
43loading using Timoshenko and high-order shear deformation
44theory. Matsunaga [7] studied buckling instabilities of a simply
45supported thick elastic beam subjected to axial stresses. Taking
46into account the effects of shear deformations and thickness
47changes, buckling loads and buckling displacement modes of
48thick beams are obtained. Based on the power series expansion of
49displacement components, a set of fundamental equations of a
50one-dimensional higher order beam theory was derived through
51the principle of virtual displacement. Several sets of truncated
52approximate theories are applied to solve the eigenvalue problems
53of a thick beam. Faruk [8] analyzed dynamic behavior of Timo-
54shenko beams on a Pasternak-type viscoelastic foundation sub-
55jected to time-dependent loads using the Laplace transformation
56and the complementary functions method to calculate exactly the
57dynamic stiffness matrix of the problem. Ma et al. [9] studied
58the static response of an infinite beam supported on a unilateral (ten-
59sionless) two-parameter Pasternak foundation. On the basis of the
60Bernoulli–Euler beam theory, the properties of free transverse vibra-
61tion and buckling of a double-beam system under compressive axial
62loading are investigated in the paper of Zhang et al. [10]. Explicit
63expressions are derived for the natural frequencies and the associated
64amplitude ratios of the two beams, and the analytical solutions of the
65critical buckling load is obtained. The influences of the compressive
66axial loading on the responses of the double-beam system are dis-
67cussed. It is shown that the critical buckling load of the system is
68related to the axial compression ratio of the two beams and the Win-
69kler elastic layer, and the properties of free transverse vibration of
70the system greatly depend on the axial compressions.
71Dynamic stability and instability of continuous systems under
72time-dependent deterministic or stochastic loading has been stud-
73ied by many authors for the last 40 years. The theory of random
1
Corresponding author.
Manuscript received May 6, 2012; final manuscript received December 29, 2012;
accepted manuscript posted January 29, 2013; published online xx xx, xxxx. Assoc.
Editor: Wei-Chau Xie.
J_ID: JAM DOI: 10.1115/1.4023519 Date: 9-February-13 Stage: Page: 1 Total Pages: 11
ID: sambasivamt Time: 12:10 I Path: S:/3b2/JAM#/Vol00000/130036/APPFile/AS-JAM#130036
Journal of Applied Mechanics MONTH 2013, Vol. 00 / 000000-1Copyright VC 2013 by ASME
2. PROOF COPY [JAM-12-1185]
74 dynamic systems and a comprehensive list of references can be
75 found in Arnold et al. [11]. Khasminskii and Moshchuk [12]
76 obtained an asymptotic expansion of the moment Lyapunov expo-
77 nents of a two-dimensional system under white noise parametric
78 excitation in terms of the small fluctuation parameter e, from
79 which the stability index was obtained. Kozic´ et al. [13] investi-
80 gated the Lyapunov exponent and moment Lyapunov exponent of
81 a double-beam system without connected damping coefficient
82 fluctuated by white noise considered as a separate viscosity sys-
83 tem. The method of regular perturbation was used to obtain
84 explicit expressions for these exponents in the presence of small
85 intensity noises. Xie [14] obtained weak noise expansions of the
86 moment Lyapunov exponents of a two-dimensional system
87 under real noise excitation, an Ornstein–Uhlenbeck process. Sri
88 Namachchivaya and Van Roessel [15] used a perturbation
89 approach to calculate the asymptotic growth rate of a stochasti-
90 cally coupled two-degree-of-freedom system. The noise was
91 assumed to be white and of small intensity in order to calculate
92 the explicit asymptotic formulas for the maximum Lyapunov
93 exponent. Sri Namachchivaya et al. [16] used a perturbation
94 approach to obtain an approximation for the moment Lyapunov
95 exponents of two coupled oscillators with commensurable fre-
96 quencies driven by small intensity real noise with dissipation. The
97 generator for the eigenvalue problem associated with the moment
98 Lyapunov exponents was derived without any restriction on the
99 size of the pth moment.
100 In the present study, instability of the complex system of the
101 beams and weak noise expansion for the moment Lyapunov expo-
102 nents are investigated for the six-dimensional stochastic system. It
103 is determined that the new set of transformation for getting It^o
104 differential equations for a system of three DOFAQ2 as a form of six
105 Stratonovich differential equations. The noise is assumed to be
106 white noise of small intensity such that one can obtain an asymp-
107 totic growth rate. The Lyapunov exponent is then obtained using
108 the relationship between the moment Lyapunov exponents and the
109 Lyapunov exponent. These results are applied to study the pth
110 moment stability and almost sure stability of a system on the elas-
111 tic foundation.
112 2 Application to Beams Under Stochastic Loads
113 Physical problems of real engineering can apply the further
114 investigation of the transverse vibration instability of a complex
115 system on elastic foundation subjected to stochastic compressive
116 axial loading.AQ3 It is assumed that the three beams of the system are
117 under the stochastic excitation. The rotary inertia and shear defor-
118 mation should be negligible in motion of the beams is governed
119 by the partial differential Eqs. (1a), (1b), and (1c).AQ4 This theory is
120 based on the assumption that plane cross-sections of a beam
121 remain plane during flexure and that the radius of curvature of a
122 bent beam is larger than the beam’s depth. It is valid only if the
123ratio of the depth to the length of the beam is small. We can obtain
124the general equations for transverse vibrations of elastically con-
125nected beams shown in Fig. 1 if we set m ¼ 3, ignore rotary inertia
126and shear effects, and include viscous damping in Eqs. (8a), (8b),
127and (8c) given in Stojanovic´ et al. [6].
EI1
@4
w1
@z4
þ qA1
@2
w1
@t2
þ ec0 2
@w1
@t
À
@w2
@t
þ F1ðtÞ
@2
w1
@z2
þ eKð2w1 À w2Þ ¼ 0 (1a)
EI2
@4
w2
@z4
þ qA2
@2
w2
@t2
þ ec0 2
@w2
@t
À
@w1
@t
À
@w3
@t
þ F2ðtÞ
@2
w2
@z2
þ eKð2w2 À w1 À w3Þ ¼ 0 (1b)
EI3
@4
w3
@z4
þ qA3
@2
w3
@t2
þ ec0
@w3
@t
À
@w2
@t
þ F3ðtÞ
@2
w3
@z2
þ eKðw3 À w2Þ ¼ 0 (1c)
128where w1, w2, and w3 are transverse beam deflections, which are
129positive if downward; I1; I2, and I3 are the second moments of
130inertia of the beams; A1; A2, and A3 are the cross-sectional area
131of the beams; and E and q are Young’s modulus and the mass den-
132sity. Thus, c0 represents the damping coefficients per unit axial
133length, respectively, and K is the stiffness modulus of a Winkler
134elastic layer. F1ðtÞ; F2ðtÞ, and F3ðtÞ are stochastically varying
135static loads. Simply supported ends for the same length l of the
136beams are satisfied with boundary conditions wið0; tÞ ¼ wiðl; tÞ
¼ @2
wið0; tÞ=@z2
¼ @2
wiðl; tÞ=@z2
¼ 0; i ¼ 1; 2; 3: Using the
137Galerkin method only for fundamental modes are considered; AQ5
138boundary conditions are satisfied by taking and substituting
wiðz; tÞ ¼ TiðtÞ sinðpz=lÞ; ði ¼ 1; 2; 3Þ into equations of motion
139Eqs. (1a), (1b), and (1c). Unknown time functions can be
140expressed as
€T1 þ
c0e
qA1
ð2 _T1 À _T2Þ þ
EI1
qA1
p4
l4
þ
2Ke
qA1
À
p2
qA1l2
F1ðtÞ
T1
À
2Ke
qA1
T2 ¼ 0 (2)
€T2 þ
c0e
qA2
ð2 _T2 À _T3 À _T1Þ þ
EI2
qA2
p4
l4
þ
2Ke
qA2
À
p2
qA2l2
F2ðtÞ
T2
À
Ke
qA2
T3 À
Ke
qA2
T1 ¼ 0 (3)
€T3 þ
c0e
qA3
_T3 À
c0e
qA3
_T2 þ
EI3
qA3
p4
l4
þ
Ke
qA3
À
p2
qA3l2
F3ðtÞ
T3
À
Ke
qA3
T2 ¼ 0 (4)
Fig. 1 Geometry of complex three-beam system on elastic foundation
J_ID: JAM DOI: 10.1115/1.4023519 Date: 9-February-13 Stage: Page: 2 Total Pages: 11
ID: sambasivamt Time: 12:10 I Path: S:/3b2/JAM#/Vol00000/130036/APPFile/AS-JAM#130036
000000-2 / Vol. 00, MONTH 2013 Transactions of the ASME
3. PROOF COPY [JAM-12-1185]
141 Using the further substitutions,
x2
1 ¼
EI1
qA1
p4
l4
; x2
2 ¼
EI2
qA2
p4
l4
; x2
3 ¼
EI3
qA3
p4
l4
; b1 ¼
C0
qA1
;
b2 ¼
C0
qA2
; b3 ¼
C0
qA3
K1 ¼
p2
qA1l2
; K2 ¼
p2
qA2l2
; K3 ¼
p2
qA3l2
; H1 ¼
K
qA1
;
H2 ¼
K
qA2
; H3 ¼
K
qA3
142 and assume that the compressive axial forces are stochastic white-
143 noise processes with small intensity F1ðtÞ ¼ F2ðtÞ ¼ F3ðtÞ
¼
ffiffi
e
p
cðtÞ, we have an oscillatory system in the form
d2
T1
dt2
þ x2
1T1 þ eb1 2
dT1
dt
À
dT2
dt
þ eH1ð2T1 À T2Þ
À
ffiffi
e
p
K1cðtÞT1 ¼ 0
d2
T2
dt2
þ x2
2T2 þ eb2 2
dT2
dt
À
dT3
dt
À
dT1
dt
þ eH2ð2T2 À T3 À T1Þ
À
ffiffi
e
p
K2cðtÞT2 ¼ 0
d2
T3
dt2
þ x2
3T3 þ eb3
dT3
dt
À
dT2
dt
þ eH3ðT3 À T2Þ
À
ffiffi
e
p
K3cðtÞT3 ¼ 0 (5)
144 The system consists of unknown generalized coordinates in func-
145 tions of time Ti; natural frequencies xi, and viscous damping
146coefficients ebi; ði ¼ 1; 2; 3Þ. The stochastic term
ffiffi
e
p
cðtÞ presents
147a white-noise process with small intensity. Dynamic stability of
148a oscillatory system can be known to determine the maximal
149Lyapunov exponent and the pth moment Lyapunov exponent,
150which is described as
kT ¼ lim
t!1
1
t
log Tðt; T0Þk k
151where Tðt; T0Þ is the solution process of a linear dynamic system.
152The almost sure stability depends upon the sign of the maximal
153Lyapunov exponent, which is an exponential growth rate of the
154solution of the randomly perturbed dynamic system. A negative
155sign of the maximal Lyapunov exponent implies the almost sure
156stability, whereas a nonnegative value indicates instability. The
157exponential growth rate E Tðt; T0; _T0Þ
p Ã
is provided by the
158moment Lyapunov exponent, defined as
KTðpÞ ¼ lim
t!1
1
t
log E Tðt; T0Þk kp
½ Š
159where E½ Š denotes the expectation. If KTðpÞ 0; then, by defini-
160tion, E Tðt; T0; _T0Þ
p Ã
! 0 as t ! 0, and this is referred to
161as pth moment stability. Although the moment Lyapunov expo-
162nents are important in the study of the dynamic stability of the
163stochastic systems, the actual evaluations of the moment Lyapu-
164nov exponents are very difficult, and the almost sure and moment
165stability of the equilibrium state T ¼ _T ¼ 0 of Eq. (32). Using the
166transformation T1 ¼ x1; _T1 ¼ x1x2; T2 ¼ x3; _T2 ¼ x2x4; T3 ¼ x5;
_T3 ¼ x3x6, the Eq. (1) can be represented in the first-order form
167by Stratonovich differential equations,
d
x1
x2
x3
x4
x5
x6
8
:
9
=
;
¼
0 x1 0 0 0 0
À2h1e À x1 À2eb1 eh1 eb1x2=x1 0 0
0 0 0 x2 0 0
h2e eb2x1=x2 À2h2e À x2 À2eb2 h2e eb2x3=x2
0 0 0 0 0 x3
0 0 eh3 eb3x2=x3 Àeh3 À x3 Àeb3
2
6
6
6
6
6
6
6
6
4
3
7
7
7
7
7
7
7
7
5
x1
x2
x3
x4
x5
x6
8
:
9
=
;
dt
þ
ffiffi
e
p
0 0 0
k1 0 0
0 0 0
0 0 0
0 0 0
0 0 0
0 0 k2
0 0 0
0 0 0
0 0 0
0 0 0
0 k3 0
2
6
6
6
6
6
6
6
6
4
3
7
7
7
7
7
7
7
7
5
x1
x2
x3
x4
x5
x6
8
:
9
=
;
dc tð Þ
(6)
168 where h1 ¼ H1=x1; h2 ¼ H2=x2; h3 ¼ H3=x3; k1 ¼ K1=x1;
k2 ¼ K2=x2; k3 ¼ K3=x3 Á c tð Þ is the white-noise process with
169 zero mean and autocorrelation function,
Rcc t1; t2ð Þ ¼ E c t1ð Þc t1ð Þ½ Š ¼ r2
d t2 À t1ð Þ (7)
170 where r is the intensity of the random process c tð Þ; dðÞ is the Dirac
171 d function, and E½ Š denotes expectation. Using corresponding
172 transformation,
x1 ¼ a cos u1 cos u2 cos h1; x2 ¼ Àa cos u1 cos u2 sin h1;
x3 ¼ a cos u1 sin u2 cos h2 x4 ¼ Àa cos u1 sin u2 sin h2;
x5 ¼ a sin u1 cos h3; x6 ¼ Àa sin u1 sin h3
P ¼ ap
¼ ðx2
1 þ x2
2 þ x2
3 þ x2
4 þ x2
5 þ x2
6Þ
p
2
À1 p 1; 0 hi 2p; 0 uj
p
2
; i ¼ 1; 2; 3; j ¼ 1; 2
It^o’s rule gets the set of equations for the pth power of the
173norm of the response and phase variables. Trigonometric trans-
174formation represents a as a norm of the response, where h1; h2,
175and h3 are the angles of the three oscillators and u1 and u2
176describe the coupling or exchange of energy between the
177oscillators.
dh1 ¼ m1 h1; h2; h3; u1; u2ð Þdt þ r11 h1; h2; h3; u1; u2ð ÞdW tð Þ
dh2 ¼ m2 h1; h2; h3; u1; u2ð Þdt þ r21 h1; h2; h3; u1; u2ð ÞdW tð Þ
dh3 ¼ m3 h1; h2; h3; u1; u2ð Þdt þ r31 h1; h2; h3; u1; u2ð ÞdW tð Þ
du1 ¼ m4 h1; h2; h3; u1; u2ð Þdt þ r41 h1; h2; h3; u1; u2ð ÞdW tð Þ
du2 ¼ m5 h1; h2; h3; u1; u2ð Þdt þ r51 h1; h2; h3; u1; u2ð ÞdW tð Þ
dP ¼ Pm6 h1; h2; h3; u1; u2ð Þdt þ Pr61 h1; h2; h3; u1; u2ð ÞdW tð Þ
(8)
J_ID: JAM DOI: 10.1115/1.4023519 Date: 9-February-13 Stage: Page: 3 Total Pages: 11
ID: sambasivamt Time: 12:10 I Path: S:/3b2/JAM#/Vol00000/130036/APPFile/AS-JAM#130036
Journal of Applied Mechanics MONTH 2013, Vol. 00 / 000000-3
4. PROOF COPY [JAM-12-1185]
178 where W tð Þ is the standard Weiner process and
m1 h1; h2; h3; u1; u2ð Þ
¼ x1 À eb1 sin 2h1 À
x2
x1
cos h1 sin h2 tan u2
þ eh1 1 þ cos2h1 À cos h1 cos h2 tan u2ð Þ
À e
k2
1r2
8
cos3h1 sin h1 þ 2 sin 2h1 þ cosh1 sin 3h1ð Þ (9)
r11 h1; h2; h3; u1; u2ð Þ ¼ À
ffiffi
e
p
k1r cos2
h1 (10)
m2 h1;h2;h3;u1;u2ð Þ
¼ x2 Àeb2
sin2h2 À
x1
x2
cosh2 cotu2 sinh1
À
x3
x2
cosh2 sinh3
tanu1
sinu2
þeh2
1þcos2h2 Àcosh1 cosh2 cotu2
À
tanu1
sinu2
cosh2 sinh3
Àe
k2
2r2
8
cos3h2 sinh2 þ2sin2h2
þcosh2 sin3h2
(11)
r21 h1; h2; h3; u1; u2ð Þ ¼ À
ffiffi
e
p
k2r cos2
h2 (12)
m3 h1; h2; h3; u1; u2ð Þ
¼
x3
16
13 þ cos2h3 þ
5 þ 4cos2h3 À cos4h3
2 1 þ cos2h3ð Þ
À
eb3
8
3 sin 2h3 þ tan h3 1 þ cos 2h3ð Þ
À 4
x2
x3
sin u2 cot u1 sin h2 cos h3 þ
1
cos h3
À tan h3
!
þ
eh3
2
1 þ cos 2h3 À cos h2 cos h3 cot u1 sin u2
À
cos h2
cos h3
cot u1 sin u2 þ cos h2 cot u1 sin h3 sin u2 tan h3
À e
k2
3r2
8
cos 3h3 sin h3 þ 2 sin 2h3 þ cos h3 sin 3h3ð Þ (13)
r31 h1; h2; h3; u1; u2ð Þ ¼ À
ffiffi
e
p
k3r cos2
h3 (14)
m4 h1; h2; h3; u1; u2ð Þ ¼ e
(
h1
4
Â
cos h2 sin h1 sin 2u1 sin 2u2 À sin 2h1
À
cos 2u2 sin 2u1 þ sin 2u1
ÁÃ
þ
b1
4
sin 2u1 1 À cos 2h1ð Þ 1 þ cos 2u2ð Þ À
x2
x1
sin h1 sin h1 sin 2u2
!'
þ
h2
4
sin 2u1 cos 2u2 sin 2h2 À sin 2h2 þ sin 2u2 cos h1 sin h2ð Þ þ 2 sin h2 cos h3 sin u2 1 À cos 2u1ð Þ½ Š
þ
b2
4
sin 2u1 1 À cos 2h2ð Þ 1 À cos 2u2ð Þ À
2x3
x2
1 À cos 2u1ð Þ sin h2 sin h3 sin u2
À
x1
x2
sin h1 sin h2 sin 2u1 sin 2u2
!'
þ
h3
4
sin 2h3 sin 2u1 À 2 cos h2 sin h3 sin u2 1 þ cos 2u1ð Þ½ Š
þ
b3
4
sin 2u1 cos 2h3 À 1ð Þ þ
2x2
x3
sin h2 sin h3 sin 2u2 1 þ cos 2u1ð Þ
!
þ
r2
64
2k2
1 cos2
u2
Â
sin 4u1 sin2
2h1 cos2
u2 À 8 cos2
h1 sin 2u1
À
cos2
h1 À cos 2u2 sin2
h1
ÁÃ
þ 2k2
2 sin2
u2 sin 4u1 sin2
2h2 sin2
u2 À 8cos2
h2 sin 2u1 cos2
h2 þ cos 2u2 sin2
h2
À ÁÂ Ã
þ 16k2
3 sin 2u1cos2
h3 cos 2h3 þ cos 2u1sin2
h3
À Á
þ k1k2 sin2
2u2 sin 2h1 sin 2h2 4 sin 2u1 þ sin 4u1ð Þ
À 4k1k3 cos2
u2 sin 4u1 sin 2h1 sin 2h3 À 4k2k3 sin2
u2 sin 4u1 sin 2h2 sin 2h3
')
(15)
r41 h1; h2; h3; u1; u2ð Þ ¼
ffiffi
e
p
r
8
sin 2u1 k1 sin 2h1 1 þ cos 2u2ð Þ þ k2 sin 2h2 1 À cos 2u2ð Þ À 2k3 sin 2h3 sin2u1Š½ (16)
m5 h1; h2; h3; u1; u2ð Þ ¼ e
(
h1
Â
sin h1 sin u2
À
cos h2 sin u2 À 2 cos h1 cos u2
ÁÃ
þ b1
Â
sin h1 sin u2
À
2 cos u2 sin h1 À
x2
x1
sin h2 sin u2
ÁÃ
À h2
Â
sin h2 cos u2
À
cos h1 cos u2 À 2 cos h2 sin u2 þ cos h3 tan u1
ÁÃ
þ b2 sin h2
x1
x2
cos2
u2 sin h1 À sin h2 sin 2u2 þ
x3
x2
cos u2 sin h3 tan u1
!
À
r2
16
f½4k2
1 cos2
h1 sin 2u2ðcos 2h1 À cos 2u2 sin2
h1ÞŠ À ½4k2
2 cos2
h2 sin 2u2ðcos 2h2 þ cos 2u2 sin2
h2ÞŠ
þ ½k1k2 sin 2h1 sin 2h2 sin 4u2Š
É
)
(17)
r51 h1; h2; h3; u1; u2ð Þ ¼
ffiffi
e
p
r
4
sin 2u2 k1 sin 2h1 À k2 sin2h2Š½ (18)
J_ID: JAM DOI: 10.1115/1.4023519 Date: 9-February-13 Stage: Page: 4 Total Pages: 11
ID: sambasivamt Time: 12:10 I Path: S:/3b2/JAM#/Vol00000/130036/APPFile/AS-JAM#130036
000000-4 / Vol. 00, MONTH 2013 Transactions of the ASME
5. PROOF COPY [JAM-12-1185]
m6 h1; h2; h3; u1; u2ð Þ ¼ ep
h1
Â
cos2
u1 cos u2 sin h1
À
2 cos h1 cos u2 À cos h2 sin u2
ÁÃ
þ b1 cos2
u1 cos u2 sin h1
Â
x2
x1
sin h2 sin u2 À 2 cos u2 sin h1
!
þ
h2
2
Â
sin u2 sin h2
À
À cos h3 sin 2u1 À 2 cos2
u1
À
cos h1 cos u2
À 2 cos h2 sin u2
ÁÁÃ
þ
b2
2
sin u2 sin h2
x3
x2
sin h2 sin 2u1 þ 2 cos2
u1
x1
x2
cos u2 sin h1 À 2 sin h2 sin u2
!
þ
r2
k2
1
128
cos2
u1
À
2 cos2
h1 cos 2u2
À
10 þ 3p þ 4ð2 þ pÞ À ðp À 2Þ cos 2h1ð3 þ 4 cos 2u2ÞÞ þ ðp À 2Þ sin2
2h1
 ð8 cos 2u1 cos4
u2 þ cos 4u2Þ þ
r2
k2
2
128
cos2
u1ð2 cos2
h2 cos 2u2ð10 þ 3p À 4
À
2 þ p
Á
þ ðp À 2Þ cos 2h2Þ
 ð4 cos 2u2 À 3ÞÞ þ ðp À 2Þ sin2
2h2
À
cos 4u2 þ 8 cos 4u1 sin4
u2Þ
Á
þ
r2
k2
3
64
ð2 cos2
h3ð4 cos 2u1 À 3Þ cos 2h3
 p À 2ð Þ þ 3p þ 2 À 4p cos 2u1Þ þ ðp À 2Þ cos 4u1 sin2
2h3 þ
r2
k1k2
16
ðp À 2Þ sin 2h1 sin 2h2 cos4
u1 sin2
2u2
þ
r2
k1k3
16
À
p À 2
Á
sin 2h1 sin 2h3 cos2
u2 sin2
2u1 þ
r2
k1k3
16
À
p À 2
Á
sin 2h2 sin 2h3 sin2
u2 sin2
2u1
'
(19)
r61 h1; h2; h3; u1; u2ð Þ ¼
Àp
ffiffi
e
p
r
2
À
k1 sin 2h1 cos2
u1 cos2
u2
þ k2sin2h2 cos2
u1 sin2
u2
þ k3 sin 2h3 sin2
u1
Á
(20)
179 Applying a linear stochastic transformation, given by Wedig [17],
S ¼ T h1; h2; h3; u1; u2ð ÞP; P ¼
S
T h1; h2; h3; u1; u2ð Þ
(21)
180 introducing the new norm process S by means of the scalar func-
181 tion T h1; h2; h3; u1; u2ð Þ, which is defined on the stationary phase
182 process uj; the Itoˆ equation for the new pth norm process S can be
183 obtained from Itoˆ’s Lemma,
dS ¼ P
1
2
r2
11
@2
T
@h2
1
þ r2
21
@2
T
@h2
2
þ r2
31
@2
T
@h2
3
þ r2
41
@2
T
@u2
1
þ r2
51
@2
T
@u2
2
!
þ r11r21
@2
T
@h1@h2
þ r11r31
@2
T
@h1@h3
þ r11r41
@2
T
@h1@u1
þ r31r51
@2
T
@h3@u2
þ r41r51
@2
T
@u1@u2
þ m1
@T
@h1
þ m2
@T
@h2
þ m3
@T
@h3
þ m4
@T
@u1
þ m5
@T
@u2
þ m6T þ r11r61
@T
@h1
þ r21r61
@T
@h2
þ r31r61
@T
@h3
þ r41r61
@T
@u1
þ r51r61
@T
@u2
!
dT
þ P
r11
@T
@h1
þ r21
@T
@h2
þ r31
@T
@h3
þ r41
@T
@u1
þ r51
@T
@u2
r61T
 dW tð Þ (22)
184 In the case that transformation function TðujÞ is bounded and non-
185 singular, both processes P and S possess the same stability behav-
186 ior. Therefore, transformation function TðujÞ is chosen so that the
187 drift term of the Itoˆ differential Eq. (43) does not depend on the
188 phase process uj, so that
dS ¼ K pð ÞSdt þ
S
T
r11
@T
@h1
þ r21
@T
@h2
þ r31
@T
@h3
þ r41
@T
@u1
þ r51
@T
@u2
þ r61T
dW tð Þ (23)
189 Comparing Eqs. (22) and (23), transformation function T h1; h2;ð
h3; u1; u2Þ is given by the following equation:
L0 þ eL1½ ŠT h1; h2; h3; u1; u2ð Þ ¼ K pð ÞT h1; h2; h3; u1; u2ð Þ (24)
190where L0 and L1 are the differential operators in the forms
L0 ¼ x1
@
@h1
þ x2
@
@h2
þ x3
@
@h3
;
L1 ¼ a1
@2
@h2
1
þ a2
@2
@h2
2
þ a3
@2
@h2
3
þ a4
@2
@u2
1
þ a5
@2
@u2
2
þ a6
@2
@h1@h2
þ a7
@2
@h1@h3
þ a8
@2
@h1@u1
þ a9
@2
@h1@u2
þ a10
@2
@h2@h3
þ a11
@2
@h2@u1
þ a12
@2
@h2@u2
þ a13
@2
@h3@u1
þ a14
@2
@h3@u2
þ a15
@2
@u1@u2
þ b1
@
@h1
þ b2
@
@h2
þ b3
@
@h3
þ b4
@
@u1
þ b5
@
@u2
þ c (25)
191where
ai ¼ ai h1; h2; h3; u1; u2ð Þ; i ¼ 1; 2; …15;
bj ¼ bj h1; h2; h3; u1; u2ð Þ; j ¼ 1; 2; …5 (26)
192and
c ¼ c h1; h2; h3; u1; u2ð Þ (27)
193Functional coefficients ai; bj, and c are available in the.nb
194Mathematica 8 file - (http://www.2shared.com/file/-pI4nFbZ/
195coeff_ai_bj_c_and_Lyapunov_1.html).
1963 Moment Lyapunov Exponents
197The eigenvalue problem for a differential operator of five
198independent variables is identified from Eq. (24), in which K pð Þ is
199the eigenvalue and T h1; h2; h3; u1; u2ð Þ is the associated eigen-
200function. Equation (23) defines that the eigenvalue K pð Þ is the
201Lyapunov exponent of the pth moment of system in Eq. AQ6(6). This
202approach was first applied by Wedig [17] to derive the eigenvalue
203problem for the moment Lyapunov exponent of a two-
204dimensional linear Itoˆ stochastic system. Applying the method of
205regular perturbation, both the moment Lyapunov exponent K pð Þ
206and the eigenfunction T h1; h2; h3; u1; u2ð Þ are expanded in power
207series of e to obtain a weak noise expansion of the Lyapunov
J_ID: JAM DOI: 10.1115/1.4023519 Date: 9-February-13 Stage: Page: 5 Total Pages: 11
ID: sambasivamt Time: 12:10 I Path: S:/3b2/JAM#/Vol00000/130036/APPFile/AS-JAM#130036
Journal of Applied Mechanics MONTH 2013, Vol. 00 / 000000-5
6. PROOF COPY [JAM-12-1185]
208 exponent of a system with stochastic excitation, described by six-
209 dimensional components as
K pð Þ ¼ K0 pð Þ þ eK1 pð Þ þ e2
K2 pð Þ þ ÁÁÁ
þ en
Kn pð Þ þ ÁÁÁ;
T h1;h2;h3;u1;u2ð Þ ¼ T0 h1;h2;h3;u1;u2ð Þ þ eT1 h1;h2;h3;u1;u2ð Þ
þ e2
T2 h1;h2;h3;u1;u2ð Þ þ ÁÁÁ
þ e2
T2 h1;h2;h3;u1;u2ð Þ þ ÁÁÁ
þ en
Tn h1;h2;h3;u1;u2ð Þ þ ÁÁÁ (28)
210 Equating terms of the equal powers of e from Eqs. (24) and (28),
211 the following equations may be written as
e0
: L0T0 h1; h2; h3; u1; u2ð Þ ¼ K0 pð ÞT0 h1; h2; h3; u1; u2ð Þ;
e1
: L0T1 h1; h2; h3; u1; u2ð Þ þ L1T0 h1; h2; h3; u1; u2ð Þ
¼ K0 pð ÞT1 h1; h2; h3; u1; u2ð Þ þ K1 pð ÞT0 h1; h2; h3; u1; u2ð Þ;
e2
: L0T2 h1; h2; h3; u1; u2ð Þ þ L1T1 h1; h2; h3; u1; u2ð Þ
¼ K0 pð ÞT2 h1; h2; h3; u1; u2ð Þ þ K1 pð ÞT1 h1; h2; h3; u1; u2ð Þ
þ K2 pð ÞT0 h1; h2; h3; u1; u2ð Þ;
e3
: L0T3 h1; h2; h3; u1; u2ð Þ þ L1T2 h1; h2; h3; u1; u2ð Þ
¼ K0 pð ÞT3 h1; h2; h3; u1; u2ð Þ þ K1 pð ÞT2 h1; h2; h3; u1; u2ð Þ
þ K2 pð ÞT1 h1; h2; h3; u1; u2ð Þ þ K3 pð ÞT0 h1; h2; h3; u1; u2ð Þ;
…
en
: L0Tn h1; h2; h3; u1; u2ð Þ þ L1TnÀ1 h1; h2; h3; u1; u2ð Þ
¼ K0 pð ÞTn h1; h2; h3; u1; u2ð Þ þ K1 pð ÞTnÀ1 h1; h2; h3; u1; u2ð Þ
þ Á Á Á þ Kn pð ÞT0 h1; h2; h3; u1; u2ð Þ (29)
212 where each function Ts h1; h2; h3; u1; u2ð Þ; s ¼ 1; 2; 3; … must be
213 positive and periodic in the range 0 hi 2p:
214 3.1 Zeroth Order Perturbation. From Eqs. (24) and (29),
215 the zeroth order perturbation equation is L0T0 ¼ K0 pð ÞT0 and can
216 be written as
x1
@T0 h1; h2; h3; u1; u2ð Þ
@h1
þ x2
@T0 h1; h2; h3; u1; u2ð Þ
@h2
þ x3
@T0 h1; h2; h3; u1; u2ð Þ
@h3
¼ K0 pð ÞT0 h1; h2; h3; u1; u2ð Þ
(30)
217 Equation (30) can be easily solved from the moment Lyapunov
218 exponent characteristic, which results in Kn 0ð Þ ¼ 0 for
n ¼ 0; 1; 2; 3; … because of K 0ð Þ ¼ K0 0ð Þ þ eK1 0ð Þ þ e2
K2 0ð Þ
þ Á Á Á þ en
Kn 0ð Þ ¼ 0. The eigenvalue K0 pð Þ is independent of p.
219 Hence, K0 0ð Þ ¼ 0 leads to K0 pð Þ ¼ 0. The solutions of Eq. (30)
220 have a periodic solution if and only if
K0 pð Þ ¼ 0; T0 h1; h2; h3; u1; u2ð Þ ¼ 1 (31)
3.2 First-Order Perturbation. The equation given from
221 first-order perturbation is
L0T1 h1; h2; h3; u1; u2ð Þ þ L1T0 h1; h2; h3; u1; u2ð Þ
¼ K0 pð ÞT1 h1; h2; h3; u1; u2ð Þ þ K1 pð ÞT0 h1; h2; h3; u1; u2ð Þ
(32)
222 and Eq. (32) has a periodic solution if and only if
ð2p
0
ð2p
0
ð2p
0
ðp=2
0
ðp=2
0
L1 Á 1 À K1 pð Þ½ Šdu1du2dh1dh2dh3 ¼ 0 (33)
223which yields
K1 pð Þ ¼
1
2p5
ð2p
0
ð2p
0
ð2p
0
ðp=2
0
ðp=2
0
c h1; h2; h3; u1; u2ð Þ½ Š
 du1du2dh1dh2dh3
¼ r2 k2
1 þ k2
2
1024
p 9p þ 46ð Þ þ
k2
3
128
p 3p þ 10ð Þ
!
À
p
4
b1 þ b2 þ b3ð Þ (34)
224The first-order perturbation equation can be rewritten as
x1
@T1 h1; h2; h3; u1; u2ð Þ
@h1
þ x2
@T1 h1; h2; h3; u1; u2ð Þ
@h2
þ x3
@T1 h1; h2; h3; u1; u2ð Þ
@h3
þ c h1; h2; h3; u1; u2ð Þ ¼ K1 pð Þ
(35)
225It is important to take into consideration commensurable frequen-
226cies where exists a relation of the form of m1x1 ¼ m2x2 ¼ m3x3,
227where m1; m2, and m3 integers and expressions for second and
228third frequency are x2 ¼ l1x1 and x3 ¼ l2x1, respectively. The
229function c h1; h2; h3; u1; u2ð Þ in Eq. (35) can be written in the form
c h1; h2; h3; u1; u2ð Þ ¼ K1 pð Þ þ f0 h1; h2; h3ð Þ
þ f1 h1; h2; h3ð Þ cos 2u1 þ f2 h1; h2; h3ð Þ
 cos 2u2 þ f3 h1; h2; h3ð Þ cos 4u1
þ f4 h1; h2; h3ð Þ cos 4u2 þ f5 h1; h2; h3ð Þ
 sin 2u2 þ f6 h1; h2; h3ð Þ cos 2u1 cos 2u2
þ f7 h1; h2; h3ð Þ cos 2u1 sin 2u2
þ f8 h1; h2; h3ð Þ cos 2u1 cos 4u2
þ f9 h1; h2; h3ð Þ cos 4u1 cos 2u2
þ f10 h1; h2; h3ð Þ cos 4u1 cos 4u2
þ f11 h1; h2; h3ð Þ sin 2u1 sin u2 (36)
230Functions fr h1; h2; h3ð Þ are periodic in h1; h2, and h3 and given as
fr h1; h2; h3ð Þ ¼ U srf g; r ¼ 0; 1; …; 11 (37)
231where U½ Š is the vector in the form
Ub c ¼ h1 b1 h2 b2 h3 b3 r2
k2
1 r2
k2
2 r2
k2
3 r2
k1k2 r2
k1k3 r2
k2k3
Ä Å
232and the values of column vectors srf g are available in the.nb file –
233(http://www.2shared.com/file/-xPP9Snp/Sr_online.html). Equa-
234tion (35) cannot be obtained explicitly for T1 h1; h2; h3; u1; u2ð Þ:
235The combination of coefficients u1 and u2 in Eq. (36) suggests
236that function T1 h1; h2; h3; u1; u2ð Þ can be written as
T1 h1; h2; h3; u1; u2ð Þ ¼ T10 h1; h2; h3ð Þ þ T11 h1; h2; h3ð Þ cos 2u1
þ T12 h1; h2; h3ð Þ cos 2u2 þ T13 h1; h2; h3ð Þ
 cos 4u1 þ T14 h1; h2; h3ð Þ cos 4u2
þ T15 h1; h2; h3ð Þ sin 2u2 þ T16 h1; h2; h3ð Þ
 cos 2u1 cos 2u2 þ T17 h1; h2; h3ð Þ cos 2u1
 sin 2u2 þ T18 h1; h2; h3ð Þ cos 2u1 cos 4u2
þ T19 h1; h2; h3ð Þ cos 4u1 cos 2u2
þ T110 h1; h2; h3ð Þ cos 4u1 cos 4u2
þ T111 h1; h2; h3ð Þ sin 2u1 sin u2 (38)
237Substituting Eq. (38) into Eq. (35) and equating terms of the equal
238trigonometry function to give a set of partial differential
239equations,
J_ID: JAM DOI: 10.1115/1.4023519 Date: 9-February-13 Stage: Page: 6 Total Pages: 11
ID: sambasivamt Time: 12:10 I Path: S:/3b2/JAM#/Vol00000/130036/APPFile/AS-JAM#130036
000000-6 / Vol. 00, MONTH 2013 Transactions of the ASME
7. PROOF COPY [JAM-12-1185]
x1
@T1r h1; h2; h3ð Þ
@h1
þ x2
@T1r h1; h2; h3ð Þ
@h2
þ x3
@T1r h1; h2; h3ð Þ
@h3
þ fr h1; h2; h3ð Þ ¼ 0; r ¼ 0; 1; …; 11 (39)
240 The functions T1r h1; h2; h3ð Þ can be written as
T1r h1; h2; h3ð Þ ¼ U½ Š vrf g þ Cr h2 À l1h1; h3 À l2h1ð Þ;
r ¼ 0; 1; …; 11 (40)
241 where the calculated values of column vectors vrf g are available in
242 the.nb file – (http://www.2shared.com/file/7Eb8_wIV/Vr_onli-
243 ne.html). Here, Crðh2 À l1h1; h3 À l2h1Þ are the same arbitrary func-
244 tions of three variables, for which we make assumptions as follows:
Cr h2 À l1h1;h3 À l2h1ð Þ ¼ A1r þ B1r sin 2h2 À 2l1h1ð Þ
þ C1r sin 4h2 À 4l1h1ð Þ
þ D1r sin 2h3 À 2l2h1ð Þ
þ E1r sin 4h3 À 4l2h1ð Þ; r ¼ 0;1;…;11
(41)
245 As each function T1r h1; h2; h3ð Þ; r ¼ 0; 1; …; 11 must be positive
246 and periodic, unknown constants A1r; B1r; C1r; D1r; and E1r can
247 be determined using conditions
T1r 0; 0; 0ð Þ ¼ T1r 0; 0; 2pð Þ ¼ T1r 0; 2p; 0ð Þ ¼ T1r 2p; 0; 0ð Þ
¼ T1r 2p; 2p; 0ð Þ ¼ T1r 0; 2p; 2pð Þ
¼ T1r 2p; 0; 2pð Þ ¼ T1r 2p; 2p; 2pð Þ ¼ 0 (42)
@T1r 0; 0; 0ð Þ
@h1
¼
@T1r 2p; 0; 0ð Þ
@h1
;
@T1r 0; 0; 0ð Þ
@h2
¼
@T1r 0; 2p; 0ð Þ
@h2
;
@T1r 0; 0; 0ð Þ
@h3
¼
@T1r 0; 0; 2pð Þ
@h3
; r ¼ 0; 1; …; 11 (43)
248and give the following constants available in the.nb file – (http://
249www.2shared.com/file/247fMXuz/Coefficients_A1r_B1r_C1r_D1r_a.
250html).
2513.2 Second-Order Perturbation. The second-order pertur-
252bation equation must satisfy the condition of periodic function
T2 h1; h2; h3; u1; u2ð Þ in h1; h2, and h3, given as
L0T2 h1; h2; h3; u1; u2ð Þ þ L1T2 h1; h2; h3; u1; u2ð Þ
¼ K1 pð ÞT1 h1; h2; h3; u1; u2ð Þ þ K2 pð Þ (44)
253We have
K2 pð Þ ¼
1
2p5
ð2p
0
ð2p
0
ð2p
0
ðp=2
0
ðp=2
0
a1
@2
T1
@h2
1
(
þ a2
@2
T1
@h2
2
þ a3
@2
T1
@h2
3
þ a4
@2
T1
@u2
1
þ a5
@2
T1
@u2
2
þ a6
@2
T1
@h1@h2
þ a7
@2
T1
@h1@h3
þ a8
@2
T1
@h1@u1
þ a9
@2
T1
@h1@u2
þ a10
@2
T1
@h2@h3
þ a11
@2
T1
@h2@u1
þ a12
@2
T1
@h2@u2
þ a13
@2
T1
@h3@u1
þ a14
@2
T1
@h3@u2
þ a15
@2
T1
@u1@u2
þ b1
@T1
@h1
þ b2
@T1
@h2
b3
@T1
@h3
þ b4
@T1
@u1
þ b5
@T1 h1; h2; h3; u1; u2ð Þ
@u2
þ c À K1 pð ÞŠT1½
'
du1du2dh1dh2dh3 (45)
K2 pð Þ can be obtained symbolically. We made a program in software Mathematica 8 to pass the critical point of the work and to find
254 the solution of the integral given in Eq. (45). Procedure in detail is presented in Appendix A. After integrating, the solution has the fol-
255 lowing form:
K2 pð Þ ¼
K20 pð Þ þ K21 pð Þ sin 4l2p þ K22 pð Þ cos 4l2p þ K23 pð Þ cos 3l2p sin l2p þ K24ðpÞ cos l2p sin 3l2p
x1 l2
1 À 1
À Á
l2
2 À 1
À Á
l2
1 À l2
2
À Á
2 þ cos 4l2pð Þ
(46)
256 The values K20 pð Þ; K21 pð Þ; K22 pð Þ; K23 pð Þ, and K24 pð Þ are available in the.nb file – (http://www.2shared.com/file/SLB4GzXx/Lamb-
257 da_parts_second_perturbati.html). The weak noise expansion of the moment Lyapunov exponent in the second-order perturbation for
258 the stochastic system [5] is determined in the form
K pð Þ ¼ eK1 pð Þ þ e2
K2 pð Þ þ O e3
À Á
(47)
259 The Lyapunov exponent for the system in Eq. (26) can be obtained from Eq. (47) by using a property of the moment Lyapunov
260 exponent,
k ¼
dK pð Þ
dp
p¼0
¼ ek1 þ e2
k2 þ O e3
À Á
¼ e
23
512
k2
1 þ k2
2
À Á
þ
5
64
k2
3
!
r2
À
1
4
ðb1 þ b2 þ b3Þ
'
þ e2 k20 þ k21 sin 4l2p þ k22 cos 4l2p þ k23 cos 3l2p sin l2p þ k24 cos l2p sin 3l2p
x1 l2
1 À 1
À Á
l2
2 À 1
À Á
l2
1 À l2
2
À Á
2 þ cos 4l2pð Þ
þ O e3
À Á
(48)
261 The values k20; k21; k22; k23, and k24 are available in the.nb file –
262 (http://www.2shared.com/file/qXWvZYOS/Small_Lambda_20_21_
263 22_23_24.html).
2643.3 Stochastic Stability Conditions. The values used for the pa-
265rameters of the stochastic system in the calculations for determining
266moment Lyapunov exponent and Lyapunov exponent are given as follows:
J_ID: JAM DOI: 10.1115/1.4023519 Date: 9-February-13 Stage: Page: 7 Total Pages: 11
ID: sambasivamt Time: 12:10 I Path: S:/3b2/JAM#/Vol00000/130036/APPFile/AS-JAM#130036
Journal of Applied Mechanics MONTH 2013, Vol. 00 / 000000-7
8. PROOF COPY [JAM-12-1185]
E ¼ 1 Â 1010
NmÀ2
; K ¼ 2 Â 105
NmÀ2
; q ¼ 2 Â 103
kgmÀ3
;
l ¼ 10 m; A1 ¼ A2 ¼ A3 ¼ 5 Â 10À2
m2
; I1 ¼ 4 Â 10À4
m4
;
I2 ¼
25
4
 10À4
m4
; I3 ¼
35
4
 10À4
m4
(49)
267 where we assume, for simplicity, that
H1 ¼ H2 ¼ H3 ¼
K
qA
; K1 ¼ K2 ¼ K3 ¼
p2
l2qA
(50)
268 We determined analytically the pth moment stability boundary in
269 the first-order perturbation for various values p ¼ 1; 2; 4; respec-
270 tively, with the definition of the moment stability K pð Þ 0. Using
271 the results for the moment Lyapunov exponent from first-order
272 perturbation, K pð Þ ¼ eK1 pð Þ þ O e2
ð Þ, we obtained
K 1ð Þ 0 ¼)
pert:1
c0
55
768
ðk2
1 þ k2
2Þ þ
13
96
k2
3
!
r2
qA;
K 2ð Þ 0 ¼)
pert:1
c0
1
12
ðk2
1 þ k2
2 þ 2k2
3Þr2
qA;
K 4ð Þ 0 ¼)
pert:1
c0
41
384
ðk2
1 þ k2
2Þ þ
11
48
k2
3
!
r2
qA (51)
273 An almost-sure stability boundary of the oscillatory system can be
274 determined in the first-order perturbation from knowing that the
275 oscillatory stochastic system is asymptotically stable only if the
276 Lyapunov exponent k 0: From the expression k ¼ ek1 þ O e2
ð Þ,
277 we have
k 0 ¼)
pert:1
c0
23
384
ðk2
1 þ k2
2Þ þ
5
48
k2
3
!
r2
qA (52)
278 Following the same procedure, using the values of natural fre-
279 quencies x1 ¼ 19:739 sÀ1
; x2 ¼ 24:674 sÀ1
, and x3 ¼ 29:194 sÀ1
280 calculated for the parameters of the system, we determined the
281 moment stability boundary in the second-order perturbation in the
282 form of equations
K 1ð Þ 0 ¼)
pert:2
0:0004287 þ 0:02258090c0 þ 1:50619 Â 10À6
c2
0 0
K 2ð Þ 0 ¼)
pert:2
0:00099457 þ 0:0453544c0 þ 4:0165 Â 10À6
c2
0 0
K 4ð Þ 0 ¼)
pert:2
0:0025176 þ 0:0914795c0 þ 0:00001204c2
0 0
(53)
283 We determined the almost-sure stability boundary in the second-
284 order perturbation by the same procedure applied to k ¼ ek1
þ e2
k2 þ O e3
ð Þ, and we have the condition
k 0 ¼)
pert:2
0:0003586 þ 0:022485c0 þ 1:00412 Â 10À6
c2
0 0
(54)
285 The variation of moment Lyapunov exponent for double-beam
286 and three-beam systems on elastic foundation is presented in
287 Fig. 2. Values for the double-beam system in numerical experi-
288 ment are chosen from the present study Eq. (49) for the properties
289 of the beams 1 and 2 and compared with results for moment
290 Lyapunov exponent for the three-beam system on elastic founda-
291 tion. The main point of the presented results in Fig. 2 is that the
292 stochastic stability of the three-beam system on elastic foundation
293 is higher than for the double-beam system without foundation. We
294 compared stability when one more beam and elastic foundation is
295 included with the simple double-beam system. Our investigation
296 shows that, regardless, because we increased the number of free-
297 dom of the system with one more beam, elastic foundation has
298 significant influence on increasing the region of the stochastic
299stability, and the system considered in the present work is more
300stable because the values of K pð Þ are negative on the bigger
301region of the p. Negative values of the K pð Þ show when the sys-
302tem is stable. Figure 3 just shows moment stability boundaries for
303first perturbation with respect to the damping coefficients. We can
304conclude that the stability region is increasing with increasing of
305the damping coefficient, which was expected. AQ7
3064 Conclusions
307In this paper, the dynamic stability of a complex dynamic sys-
308tem of the class of six-dimensional under white noise excitations
309is studied through the determination of the moment Lyapunov
310exponents and the Lyapunov exponents. An eigenvalue problem
311for the moment Lyapunov exponent is established using the theory
312of stochastic dynamic systems. For weak noise excitations, a sin-
313gular perturbation method is employed to obtain second-order
314expansions of the moment Lyapunov exponent. The Lyapunov
315exponent is then obtained using the relationship between the
316moment Lyapunov exponent and the Lyapunov exponent. Expres-
317sions (51)–(54) show the almost-sure and pth moment stability
318boundaries in the first and second perturbation with respect to the
319damping coefficients c0: When the Lyapunov exponent is nega-
320tive, the system in Eq. (6) is almost-sure stable with probability 1;
321otherwise, it is unstable. Figure 2 shows the comparison in
Fig. 2 Moment Lyapunov exponent K pð Þ for r
5
ffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi
2003103
p
; d1 5 d2 5 c0 5 0:01; thin lines - double beam [13],
thick lines – three beam system on elastic foundation, dashed
lines – second perturbation of the three beam system
Fig. 3 Stability regions for almost-sure (a-s) and pth moment
stability for e ¼ 0:002
J_ID: JAM DOI: 10.1115/1.4023519 Date: 9-February-13 Stage: Page: 8 Total Pages: 11
ID: sambasivamt Time: 12:10 I Path: S:/3b2/JAM#/Vol00000/130036/APPFile/AS-JAM#130036
000000-8 / Vol. 00, MONTH 2013 Transactions of the ASME
9. PROOF COPY [JAM-12-1185]
322 transverse stochastic stability between a double-beam and three-
323 beam system on elastic foundation. It was concluded that the Win-
324 kler elastic layer has a significant influence on the stochastic sta-
325 bility of beams. This influence is reflected in the increase of
326 stochastic stability. Conditions of stability are determined for a
327 complex three-beam system, and, in future research, this study
328 can be extended to other structures, such as plates on viscoelastic
329 foundation. Transformations given in the present work for the
330 three-DOF system can be applied as a direct extension of the
331 work of Ariaratnam et al. [18] and Xie [19].
332Acknowledgment
333The research is supported by the Ministry of Science and Envi-
334ronment Protection of the Republic of Serbia, grant No. ON
335174011.
336Appendix A
337
338Second Order Perturbation – Integral Solving Procedure.
339See Figs. 4 and 5.
Fig. 4AQ8
Fig. 5
J_ID: JAM DOI: 10.1115/1.4023519 Date: 9-February-13 Stage: Page: 9 Total Pages: 11
ID: sambasivamt Time: 12:10 I Path: S:/3b2/JAM#/Vol00000/130036/APPFile/AS-JAM#130036
Journal of Applied Mechanics MONTH 2013, Vol. 00 / 000000-9
10. PROOF COPY [JAM-12-1185]
References
[1] Hyer, M. W., Anderson, W. J., and Scott, R. A., 1976, “Non-linear Vibrations
340 of Three-Layer Beams With Viscoelastic Cores. I. Theory,” J. Sound Vib.,
341 46(1), pp. 121–136.
[2] Hyer, M. W., Anderson, W. J., and Scott, R. A., 1978, “Non-linear Vibrations
342 of Three-Layer Beams With Viscoelastic Cores. II. Experiment,” J. Sound Vib.,
343 61(1), pp. 25–30.
[3] Li, J., Chen, Y., and Hua, H., 2008, “Exact Dynamic Stiffness Matrix of a Tim-
344 oshenko Three-Beam System,” Int. J. Mech. Sci., 50, pp. 1023–1034.
[4] Kelly, G. S., and Srinivas, S., 2009, “Free Vibrations of Elastically Connected
345 Stretched Beams,” J. Sound Vib., 326, pp. 883–893.
[5] Jacques, N., Daya, E. M., and Potier-Ferry, M., 2010, “Nonlinear Vibration of
346 Viscoelastic Sandwich Beams by the Harmonic Balance and Finite Element
347 Methods,” J. Sound Vib., 329(20), pp. 4251–4265.
[6] Stojanovic´, V., Kozic´, P., and Janevski, G., 2013, “Exact Closed–Form Solu-
348 tions for the Natural Frequencies and Stability of Elastically Connected Multi-
349 ple Beam System Using Timoshenko and High Order Shear Deformation
350 Theory”, J. Sound Vib., 332, pp. 563–576.
[7] Matsunaga, H., 1996, “Buckling Instabilities of Thick Elastic Beams Subjected
351 to Axial Stresses,” Comput. Struct., 59, pp. 859–868.
[8] Faruk, F. C., 2009, “Dynamic Analysis of Beams on Viscoelastic Foundation,”
352 Eur. J. of Mech. A/Solids, 28, pp. 469–476.
[9] Ma, X., Butterworth, J. W., and Clifton G. C., 2009, “Static Analysis of an Infi-
353 nite Beam Resting on a Tensionless Pasternak Foundation,” Eur. J. Mech. A/
354 Solids, 28, pp. 697–703.
[10] Zhang, Q. Y., Lu, Y., Wang, L. S., and Liu, X., 2008, “Vibration and Buckling
355 of a Double–Beam System Under Compressive Axial Loading,” J. Sound Vib.,
356 318, pp. 341–352.
[11] Arnold, L., Doyle, M. M., and Sri Namachchivaya, N., 1997, “Small Noise
357Expansion of Moment Lyapunov Exponents for Two-Dimensional Systems,”
358Dyn. Stab. Syst., 12(3), pp. 187–211.
[12] Khasminskii, R., and Moshchuk, N., 1998, “Moment Lyapunov Exponent and
359Stability Index for Linear Conservative System With Small Random
360Perturbation,” SIAM J. Appl. Math., 58(1), pp. 245–256.
[13] Kozic´, P., Janevski, G., and Pavlovic´, R., 2010, “Moment Lyapunov Exponents
361and Stochastic Stability of a Double-Beam System Under Compressive Axial
362Loading,” Int. J. Solids Struct., 47, pp. 1435–1442.
[14] Xie, W.-C., 2001, “Moment Lyapunov Exponents of a Two-Dimensional Sys-
363tem Under Real-Noise Excitation,” J. Sound Vib., 239(1), pp. 139–155.
[15] Sri Namachchivaya, N., and Van Roessel, H. J., 2004, “Stochastic Stability of
364Coupled Oscillators in Resonance: A Perturbation Approach,” ASME J. Appl.
365Mech., 71, pp. 759–767.
[16] Sri Namachchivaya, N., Van Roessel, H. J., and Talwar, S., 1994,
366“Maximal Lyapunov Exponent and Almost–Sure Stability for Coupled Two-
367Degree of Freedom Stochastic Systems,” ASME J. Appl. Mech., 61, pp.
368446–452.
[17] Wedig, W., 1988, “Lyapunov Exponent of Stochastic Systems and Related
369Bifurcation Problem,” Stochastic Structural Dynamics - Progress in Theory
370and Applications, S. T. Ariaratnam, G. I. Schue¨ller, and I. Elishakoff, eds.,
371Elsevier Applied Science, London, pp. 315–327.
[18] Ariaratnam, S. T., Tam, D. S. F., and Xie, W.-C., 1991, “Lyapunov Exponents
372and Stochastic Stability of Coupled Linear Systems Under White Noise
373Excitation,” Probab. Eng. Mech., 6–2, pp. 51–56.
[19] Xie, W.-C., 2006, “Moment Lyapunov Exponents of a Two-Dimensional Sys-
374tem Under Both Harmonic and White Noise Parametric Excitations,” J. Sound
375Vib., 289, pp. 171–191.
J_ID: JAM DOI: 10.1115/1.4023519 Date: 9-February-13 Stage: Page: 10 Total Pages: 11
ID: sambasivamt Time: 12:11 I Path: S:/3b2/JAM#/Vol00000/130036/APPFile/AS-JAM#130036
000000-10 / Vol. 00, MONTH 2013 Transactions of the ASME