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MODAL SPACE (modal + space)

Distribution by Scientific Domains
Engineering100%

Selected Abstracts

MODAL SPACE: What is the Difference Between all the Mode Indicator Functions?

EXPERIMENTAL TECHNIQUES, Issue 2 2007
What Do They all Do?
No abstract is available for this article. [source]

MODAL SPACE: Is There Any Problem Running a Modal Test to 2 KHz but Only Analyzing up to 500 Hz?

EXPERIMENTAL TECHNIQUES, Issue 4 2006
Pete Avitabile
No abstract is available for this article. [source]

Analyzing dynamic performance of stressed power systems in vicinity of instability by modal series method

EUROPEAN TRANSACTIONS ON ELECTRICAL POWER, Issue 8 2009
Ali H. Naghshbandy
Abstract Highly stressed power systems exhibit complex dynamic behaviors such as inter-area oscillations when subjected to large disturbances. In such conditions, nonlinear effects have dominant role in determining dynamic response of the systems. In this paper by using modal series method, dynamic behaviors of the stressed power systems in severe conditions and near instability have been studied. Also two measures, mode dominance measure (MDM) and most perturbed machine factor (MPF) have been introduced. They determine the most dominant modes and identify the most perturbed generators when the system is subjected to a given fault. Contribution factors have been used to show the links between identified modes and machines from the analysis. Time domain simulation has been helped for validation of the results. By using similarity transformation, state variables have been represented in modal space and utilized to check the results. The studies are carried out on the IEEE 50-generator test system which demonstrates a wide range of dynamic characteristics at different loading levels and fault scenarios. Copyright © 2008 John Wiley & Sons, Ltd. [source]

Optimal vibration control of continuous structures by FEM: Part I,the optimality equations

INTERNATIONAL JOURNAL FOR NUMERICAL METHODS IN BIOMEDICAL ENGINEERING, Issue 12 2002
W. Szyszkowski
Abstract The governing equations of the problem of optimal vibration control of continuous linear structures are derived in the form of a set of fourth-order ordinary differential equations in the time domain. The equations decouple in the modal space and become suitable for handling by the FEM technique with the time domain subdivided into ,finite time' elements of class C1. It is demonstrated that the standard beam element with cubic Hermitian interpolation functions, routinely used in a static analysis of beams, can conveniently be substituted for the required ,finite time' element. Copyright © 2002 John Wiley & Sons, Ltd. [source]