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shaft</title> <meta name="description" content="Search results for: rotating shaft"> <meta name="keywords" content="rotating shaft"> <meta name="viewport" content="width=device-width, initial-scale=1, minimum-scale=1, maximum-scale=1, user-scalable=no"> <meta charset="utf-8"> <link href="https://cdn.waset.org/favicon.ico" type="image/x-icon" rel="shortcut icon"> <link href="https://cdn.waset.org/static/plugins/bootstrap-4.2.1/css/bootstrap.min.css" rel="stylesheet"> <link href="https://cdn.waset.org/static/plugins/fontawesome/css/all.min.css" rel="stylesheet"> <link href="https://cdn.waset.org/static/css/site.css?v=150220211555" rel="stylesheet"> </head> <body> <header> <div class="container"> <nav class="navbar navbar-expand-lg navbar-light"> <a class="navbar-brand" href="https://waset.org"> <img src="https://cdn.waset.org/static/images/wasetc.png" alt="Open Science Research Excellence" title="Open Science Research Excellence" /> </a> <button class="d-block d-lg-none navbar-toggler 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id="custom-search-input"> <div class="input-group"> <i class="fas fa-search"></i> <input type="text" class="search-query" name="q" placeholder="Author, Title, Abstract, Keywords" value="rotating shaft"> <input type="submit" class="btn_search" value="Search"> </div> </div> </form> </div> </div> <div class="row mt-3"> <div class="col-sm-3"> <div class="card"> <div class="card-body"><strong>Commenced</strong> in January 2007</div> </div> </div> <div class="col-sm-3"> <div class="card"> <div class="card-body"><strong>Frequency:</strong> Monthly</div> </div> </div> <div class="col-sm-3"> <div class="card"> <div class="card-body"><strong>Edition:</strong> International</div> </div> </div> <div class="col-sm-3"> <div class="card"> <div class="card-body"><strong>Paper Count:</strong> 475</div> </div> </div> </div> <h1 class="mt-3 mb-3 text-center" style="font-size:1.6rem;">Search results for: rotating shaft</h1> <div class="card paper-listing mb-3 mt-3"> <h5 class="card-header" style="font-size:.9rem"><span class="badge badge-info">475</span> Performance Analysis of a 6-Phase PMG Exciter with Rotating Thyristor-Controlled Rectification Topologies</h5> <div class="card-body"> <p class="card-text"><strong>Authors:</strong> <a href="https://publications.waset.org/abstracts/search?q=Jonas%20Kristiansen%20N%C3%B8land">Jonas Kristiansen Nøland</a>, <a href="https://publications.waset.org/abstracts/search?q=Karina%20Hjelmervik"> Karina Hjelmervik</a>, <a href="https://publications.waset.org/abstracts/search?q=Urban%20Lundin"> Urban Lundin</a> </p> <p class="card-text"><strong>Abstract:</strong></p> The thyristor bridge rectifier is often used for control of excitation equipment for synchronous generators. However, on the rotating shaft of brushless exciters, the diode bridge rectifier is mostly used. The step response of a conventional brushless rotating excitation system is slow compared to static excitation systems. This paper investigates the performance of different thyristor-controlled rectification topologies applied on the shaft of a 6-phase PMG exciter connected to a synchronous generator. One of the important issues is the steady-state torque ripple produced by the thyristor bridges. <p class="card-text"><strong>Keywords:</strong> <a href="https://publications.waset.org/abstracts/search?q=brushless%20exciters" title="brushless exciters">brushless exciters</a>, <a href="https://publications.waset.org/abstracts/search?q=rotating%20exciters" title=" rotating exciters"> rotating exciters</a>, <a href="https://publications.waset.org/abstracts/search?q=permanent%20magnet%20machines" title=" permanent magnet machines"> permanent magnet machines</a>, <a href="https://publications.waset.org/abstracts/search?q=synchronous%20generators" title=" synchronous generators"> synchronous generators</a> </p> <a href="https://publications.waset.org/abstracts/35257/performance-analysis-of-a-6-phase-pmg-exciter-with-rotating-thyristor-controlled-rectification-topologies" class="btn btn-primary btn-sm">Procedia</a> <a href="https://publications.waset.org/abstracts/35257.pdf" target="_blank" class="btn btn-primary btn-sm">PDF</a> <span class="bg-info text-light px-1 py-1 float-right rounded"> Downloads <span class="badge badge-light">476</span> </span> </div> </div> <div class="card paper-listing mb-3 mt-3"> <h5 class="card-header" style="font-size:.9rem"><span class="badge badge-info">474</span> Linear Dynamic Stability Analysis of a Continuous Rotor-Disk-Blades System</h5> <div class="card-body"> <p class="card-text"><strong>Authors:</strong> <a href="https://publications.waset.org/abstracts/search?q=F.%20Rahimi%20Dehgolan">F. Rahimi Dehgolan</a>, <a href="https://publications.waset.org/abstracts/search?q=S.%20E.%20Khadem"> S. E. Khadem</a>, <a href="https://publications.waset.org/abstracts/search?q=S.%20Bab"> S. Bab</a>, <a href="https://publications.waset.org/abstracts/search?q=M.%20Najafee"> M. Najafee</a> </p> <p class="card-text"><strong>Abstract:</strong></p> Nowadays, using rotating systems like shafts and disks in industrial machines have been increased constantly. Dynamic stability is one of the most important factors in designing rotating systems. In this study, linear frequencies and stability of a coupled continuous flexible rotor-disk-blades system are studied. The Euler-Bernoulli beam theory is utilized to model the blade and shaft. The equations of motion are extracted using the extended Hamilton principle. The equations of motion have been simplified using the Coleman and complex transformations method. The natural frequencies of the linear part of the system are extracted, and the effects of various system parameters on the natural frequencies and decay rates (stability condition) are clarified. It can be seen that the centrifugal stiffening effect applied to the blades is the most important parameter for stability of the considered rotating system. This result highlights the importance of considering this stiffing effect in blades equation. <p class="card-text"><strong>Keywords:</strong> <a href="https://publications.waset.org/abstracts/search?q=rotating%20shaft" title="rotating shaft">rotating shaft</a>, <a href="https://publications.waset.org/abstracts/search?q=flexible%20blades" title=" flexible blades"> flexible blades</a>, <a href="https://publications.waset.org/abstracts/search?q=centrifugal%20stiffness" title=" centrifugal stiffness"> centrifugal stiffness</a>, <a href="https://publications.waset.org/abstracts/search?q=stability" title=" stability"> stability</a> </p> <a href="https://publications.waset.org/abstracts/56540/linear-dynamic-stability-analysis-of-a-continuous-rotor-disk-blades-system" class="btn btn-primary btn-sm">Procedia</a> <a href="https://publications.waset.org/abstracts/56540.pdf" target="_blank" class="btn btn-primary btn-sm">PDF</a> <span class="bg-info text-light px-1 py-1 float-right rounded"> Downloads <span class="badge badge-light">265</span> </span> </div> </div> <div class="card paper-listing mb-3 mt-3"> <h5 class="card-header" style="font-size:.9rem"><span class="badge badge-info">473</span> Numerical Analysis of Effect of Crack Location on the Crack Breathing Behavior</h5> <div class="card-body"> <p class="card-text"><strong>Authors:</strong> <a href="https://publications.waset.org/abstracts/search?q=H.%20M.%20Mobarak">H. M. Mobarak</a>, <a href="https://publications.waset.org/abstracts/search?q=Helen%20Wu"> Helen Wu</a>, <a href="https://publications.waset.org/abstracts/search?q=Keqin%20Xiao"> Keqin Xiao </a> </p> <p class="card-text"><strong>Abstract:</strong></p> In this work, a three-dimensional finite element model was developed to investigate the crack breathing behavior at different crack locations considering the effect of unbalance force. A two-disk rotor with a crack is simulated using ABAQUS. The duration of each crack status (open, closed and partially open/closed) during a full shaft rotation was examined to analyse the crack breathing behavior. Unbalanced shaft crack breathing behavior was found to be different at different crack locations. The breathing behavior of crack along the shaft length is divided into different regions depending on the unbalance force and crack location. The simulated results in this work can be further utilised to obtain the time-varying stiffness matrix of the cracked shaft element under the influence of unbalance force. <p class="card-text"><strong>Keywords:</strong> <a href="https://publications.waset.org/abstracts/search?q=crack%20breathing" title="crack breathing">crack breathing</a>, <a href="https://publications.waset.org/abstracts/search?q=crack%20location" title=" crack location"> crack location</a>, <a href="https://publications.waset.org/abstracts/search?q=slant%20crack" title=" slant crack"> slant crack</a>, <a href="https://publications.waset.org/abstracts/search?q=unbalance%20force" title=" unbalance force"> unbalance force</a>, <a href="https://publications.waset.org/abstracts/search?q=rotating%20shaft" title=" rotating shaft"> rotating shaft</a> </p> <a href="https://publications.waset.org/abstracts/83659/numerical-analysis-of-effect-of-crack-location-on-the-crack-breathing-behavior" class="btn btn-primary btn-sm">Procedia</a> <a href="https://publications.waset.org/abstracts/83659.pdf" target="_blank" class="btn btn-primary btn-sm">PDF</a> <span class="bg-info text-light px-1 py-1 float-right rounded"> Downloads <span class="badge badge-light">272</span> </span> </div> </div> <div class="card paper-listing mb-3 mt-3"> <h5 class="card-header" style="font-size:.9rem"><span class="badge badge-info">472</span> Dependence of Shaft Stiffness on the Crack Location</h5> <div class="card-body"> <p class="card-text"><strong>Authors:</strong> <a href="https://publications.waset.org/abstracts/search?q=H.%20M.%20Mobarak">H. M. Mobarak</a>, <a href="https://publications.waset.org/abstracts/search?q=Helen%20Wu"> Helen Wu</a>, <a href="https://publications.waset.org/abstracts/search?q=Chunhui%20Yang"> Chunhui Yang </a> </p> <p class="card-text"><strong>Abstract:</strong></p> In this study, an analytical model is developed to study crack breathing behavior under the effect of crack location and unbalance force. Crack breathing behavior is determined using effectual bending angle by studying the transient change in closed area of the crack. The status of the crack of a balanced shaft is symmetrical about shaft rotational angle and the duration of each crack status remains unchanged. The global stiffness of the balanced shaft is independent of crack location. Different crack breathing behavior for the unbalanced shaft has been observed. The influence of crack location on the unbalanced shaft stiffness can be divided into three regions. When the crack is located between 0.3L and 0.8335L, where L is the total length of the shaft, the unbalanced shaft is less stiff and when located outside this region it is stiffer than the balanced shaft. It was also found that unbalanced shaft stiffness has a maximum value with a crack at 0.1946L, a minimum value at 0.8053L and same value as balanced shaft at 0.3L and 0.8335L. <p class="card-text"><strong>Keywords:</strong> <a href="https://publications.waset.org/abstracts/search?q=cracked%20shaft" title="cracked shaft">cracked shaft</a>, <a href="https://publications.waset.org/abstracts/search?q=crack%20location" title=" crack location"> crack location</a>, <a href="https://publications.waset.org/abstracts/search?q=shaft%20stiffness" title=" shaft stiffness"> shaft stiffness</a>, <a href="https://publications.waset.org/abstracts/search?q=unbalanced%20force" title=" unbalanced force"> unbalanced force</a> </p> <a href="https://publications.waset.org/abstracts/58562/dependence-of-shaft-stiffness-on-the-crack-location" class="btn btn-primary btn-sm">Procedia</a> <a href="https://publications.waset.org/abstracts/58562.pdf" target="_blank" class="btn btn-primary btn-sm">PDF</a> <span class="bg-info text-light px-1 py-1 float-right rounded"> Downloads <span class="badge badge-light">307</span> </span> </div> </div> <div class="card paper-listing mb-3 mt-3"> <h5 class="card-header" style="font-size:.9rem"><span class="badge badge-info">471</span> Stability of a Self-Excited Machine Due to the Mechanical Coupling </h5> <div class="card-body"> <p class="card-text"><strong>Authors:</strong> <a href="https://publications.waset.org/abstracts/search?q=M.%20Soltan%20Rezaee">M. Soltan Rezaee</a>, <a href="https://publications.waset.org/abstracts/search?q=M.%20R.%20Ghazavi"> M. R. Ghazavi</a>, <a href="https://publications.waset.org/abstracts/search?q=A.%20Najafi"> A. Najafi</a>, <a href="https://publications.waset.org/abstracts/search?q=W.-H.%20Liao"> W.-H. Liao</a> </p> <p class="card-text"><strong>Abstract:</strong></p> Generally, different rods in shaft systems can be misaligned based on the mechanical system usages. These rods can be linked together via U-coupling easily. The system is self-stimulated and may cause instabilities due to the inherent behavior of the coupling. In this study, each rod includes an elastic shaft with an angular stiffness and structural damping. Moreover, the mass of shafts is considered via attached solid disks. The impact of the system architecture and shaft mass on the instability of such mechanism are studied. Stability charts are plotted via a method based on Floquet theory. Eventually, the unstable points have been found and analyzed in detail. The results show that stabilizing the driveline is feasible by changing the system characteristics which include shaft mass and architecture. <p class="card-text"><strong>Keywords:</strong> <a href="https://publications.waset.org/abstracts/search?q=coupling" title="coupling">coupling</a>, <a href="https://publications.waset.org/abstracts/search?q=mechanical%20systems" title=" mechanical systems"> mechanical systems</a>, <a href="https://publications.waset.org/abstracts/search?q=oscillations" title=" oscillations"> oscillations</a>, <a href="https://publications.waset.org/abstracts/search?q=rotating%20shafts" title=" rotating shafts"> rotating shafts</a> </p> <a href="https://publications.waset.org/abstracts/98061/stability-of-a-self-excited-machine-due-to-the-mechanical-coupling" class="btn btn-primary btn-sm">Procedia</a> <a href="https://publications.waset.org/abstracts/98061.pdf" target="_blank" class="btn btn-primary btn-sm">PDF</a> <span class="bg-info text-light px-1 py-1 float-right rounded"> Downloads <span class="badge badge-light">181</span> </span> </div> </div> <div class="card paper-listing mb-3 mt-3"> <h5 class="card-header" style="font-size:.9rem"><span class="badge badge-info">470</span> A Mathematical Model for 3-DOF Rotary Accuracy Measurement Method Based on a Ball Lens</h5> <div class="card-body"> <p class="card-text"><strong>Authors:</strong> <a href="https://publications.waset.org/abstracts/search?q=Hau-Wei%20Lee">Hau-Wei Lee</a>, <a href="https://publications.waset.org/abstracts/search?q=Yu-Chi%20Liu"> Yu-Chi Liu</a>, <a href="https://publications.waset.org/abstracts/search?q=Chien-Hung%20Liu"> Chien-Hung Liu</a> </p> <p class="card-text"><strong>Abstract:</strong></p> A mathematical model is presented for a system that measures rotational errors in a shaft using a ball lens. The geometric optical characteristics of the ball lens mounted on the shaft allows the measurement of rotation axis errors in both the radial and axial directions. The equipment used includes two quadrant detectors (QD), two laser diodes and a ball lens that is mounted on the rotating shaft to be evaluated. Rotational errors in the shaft cause changes in the optical geometry of the ball lens. The resulting deflection of the laser beams is detected by the QDs and their output signals are used to determine rotational errors. The radial and the axial rotational errors can be calculated as explained by the mathematical model. Results from system calibration show that the measurement error is within ±1 m and resolution is about 20 nm. Using a direct drive motor (DD motor) as an example, experimental results show a rotational error of less than 20 m. The most important features of this system are that it does not require the use of expensive optical components, it is small, very easy to set up, and measurements are highly accurate. <p class="card-text"><strong>Keywords:</strong> <a href="https://publications.waset.org/abstracts/search?q=ball%20lens" title="ball lens">ball lens</a>, <a href="https://publications.waset.org/abstracts/search?q=quadrant%20detector" title=" quadrant detector"> quadrant detector</a>, <a href="https://publications.waset.org/abstracts/search?q=axial%20error" title=" axial error"> axial error</a>, <a href="https://publications.waset.org/abstracts/search?q=radial%20error" title=" radial error"> radial error</a> </p> <a href="https://publications.waset.org/abstracts/26125/a-mathematical-model-for-3-dof-rotary-accuracy-measurement-method-based-on-a-ball-lens" class="btn btn-primary btn-sm">Procedia</a> <a href="https://publications.waset.org/abstracts/26125.pdf" target="_blank" class="btn btn-primary btn-sm">PDF</a> <span class="bg-info text-light px-1 py-1 float-right rounded"> Downloads <span class="badge badge-light">473</span> </span> </div> </div> <div class="card paper-listing mb-3 mt-3"> <h5 class="card-header" style="font-size:.9rem"><span class="badge badge-info">469</span> Influence of Angular Position of Unbalanced Force on Crack Breathing Mechanism</h5> <div class="card-body"> <p class="card-text"><strong>Authors:</strong> <a href="https://publications.waset.org/abstracts/search?q=Roselyn%20Zaman">Roselyn Zaman</a>, <a href="https://publications.waset.org/abstracts/search?q=Mobarak%20Hossain"> Mobarak Hossain</a> </p> <p class="card-text"><strong>Abstract:</strong></p> A new mathematical model is developed to study crack breathing behavior considering effect of angular position of unbalanced force at different crack locations. Crack breathing behavior has been determined using effectual bending angle by studying the transient change of the crack area. Different crack breathing behavior of the unbalanced shaft has been observed for different combination of angular position of unbalanced force with crack location except crack locations 0.3L and 0.8335L, where L is the total length of the shaft, where unbalanced shaft behave completely like the balanced shaft. Based on different combination of angular position of unbalanced force with crack location, the stiffness of unbalanced shaft can be divided into three regions. An unbalanced shaft is overall stiffer than a balanced shaft when angular position of unbalance force is between 90° to 270° and crack located between 0.3L and 0.8335L, and it is overall flexible when the crack located in outside this crack region. On the other hand, it is overall flexible when angular position of unbalanced force is between 0° to 90° or 270° to 360° and crack located in middle region and it is overall stiffer for outside this crack region. <p class="card-text"><strong>Keywords:</strong> <a href="https://publications.waset.org/abstracts/search?q=cracked%20shaft" title="cracked shaft">cracked shaft</a>, <a href="https://publications.waset.org/abstracts/search?q=crack%20location" title=" crack location"> crack location</a>, <a href="https://publications.waset.org/abstracts/search?q=shaft%20stiffness" title=" shaft stiffness"> shaft stiffness</a>, <a href="https://publications.waset.org/abstracts/search?q=unbalanced%20force" title=" unbalanced force"> unbalanced force</a>, <a href="https://publications.waset.org/abstracts/search?q=and%20unbalanced%20force%20orientation" title=" and unbalanced force orientation"> and unbalanced force orientation</a> </p> <a href="https://publications.waset.org/abstracts/87582/influence-of-angular-position-of-unbalanced-force-on-crack-breathing-mechanism" class="btn btn-primary btn-sm">Procedia</a> <a href="https://publications.waset.org/abstracts/87582.pdf" target="_blank" class="btn btn-primary btn-sm">PDF</a> <span class="bg-info text-light px-1 py-1 float-right rounded"> Downloads <span class="badge badge-light">268</span> </span> </div> </div> <div class="card paper-listing mb-3 mt-3"> <h5 class="card-header" style="font-size:.9rem"><span class="badge badge-info">468</span> An Acoustical Diagnosis of a Shaft-Wood Phyto-Pathogenic Damage of Sequoiadendron giganteum (Lindl.) Buccholz</h5> <div class="card-body"> <p class="card-text"><strong>Authors:</strong> <a href="https://publications.waset.org/abstracts/search?q=Yuri%20V.%20Plugatar">Yuri V. Plugatar</a>, <a href="https://publications.waset.org/abstracts/search?q=Vladimir%20P.%20Koba"> Vladimir P. Koba</a>, <a href="https://publications.waset.org/abstracts/search?q=Vladimir%20V.%20Papelbu"> Vladimir V. Papelbu</a>, <a href="https://publications.waset.org/abstracts/search?q=Vladimir%20N.%20Gerasimchuk"> Vladimir N. Gerasimchuk</a>, <a href="https://publications.waset.org/abstracts/search?q=Tatjana%20M.%20Sakhno"> Tatjana M. Sakhno</a> </p> <p class="card-text"><strong>Abstract:</strong></p> Using a supersonic shaft–wood tomography, the evaluation of a shaft-wood phyto-pathogenic damage level of Sequoiadendron giganteum (Lindl.) Buccholz was prosecuted. The digital bivariate reflections of the shaft tissue damage were obtained, the characteristics of comparative parameters of the wood-decay degree were given. The investigation results allowed to show up the role of some edaphic factors in their affection on a vital condition and the level of destructive processes while shaft tissue damaging of S.giganteum. It was pinned up that soil consolidation, and hydro-morphication equally make for a phyto-pathogenic damage of plants. While soil consolidation negative acting the shaft-wood damage is located in an underneath of a shaft. In the conditions of an enlarged hydro-morphication a tissue degradation runs less intensively, the destructive processes more active spread in a vertical section of a shaft. The use of a supersonic tomography method gives wide possibilities to diagnose a shaft-wood phyto-pathogenic damage. <p class="card-text"><strong>Keywords:</strong> <a href="https://publications.waset.org/abstracts/search?q=Sequoiadendron%20giganteum%20%28Lindl.%29%20Buccholz" title="Sequoiadendron giganteum (Lindl.) Buccholz">Sequoiadendron giganteum (Lindl.) Buccholz</a>, <a href="https://publications.waset.org/abstracts/search?q=supersonic%20tomography" title=" supersonic tomography"> supersonic tomography</a>, <a href="https://publications.waset.org/abstracts/search?q=diagnosis" title=" diagnosis"> diagnosis</a>, <a href="https://publications.waset.org/abstracts/search?q=phyto-pathogenic%20damage" title=" phyto-pathogenic damage"> phyto-pathogenic damage</a>, <a href="https://publications.waset.org/abstracts/search?q=a%20vital%20condition" title=" a vital condition"> a vital condition</a> </p> <a href="https://publications.waset.org/abstracts/78879/an-acoustical-diagnosis-of-a-shaft-wood-phyto-pathogenic-damage-of-sequoiadendron-giganteum-lindl-buccholz" class="btn btn-primary btn-sm">Procedia</a> <a href="https://publications.waset.org/abstracts/78879.pdf" target="_blank" class="btn btn-primary btn-sm">PDF</a> <span class="bg-info text-light px-1 py-1 float-right rounded"> Downloads <span class="badge badge-light">213</span> </span> </div> </div> <div class="card paper-listing mb-3 mt-3"> <h5 class="card-header" style="font-size:.9rem"><span class="badge badge-info">467</span> Calculation of Stress Intensity Factors in Rotating Disks Containing 3D Semi-Elliptical Cracks</h5> <div class="card-body"> <p class="card-text"><strong>Authors:</strong> <a href="https://publications.waset.org/abstracts/search?q=Mahdi%20Fakoor">Mahdi Fakoor</a>, <a href="https://publications.waset.org/abstracts/search?q=Seyed%20Mohammad%20Navid%20Ghoreishi"> Seyed Mohammad Navid Ghoreishi</a> </p> <p class="card-text"><strong>Abstract:</strong></p> Initiation and propagation of cracks may cause catastrophic failures in rotating disks, and hence determination of fracture parameter in rotating disks under the different working condition is very important issue. In this paper, a comprehensive study of stress intensity factors in rotating disks containing 3D semi-elliptical cracks under the different working condition is investigated. In this regard, after verification of modeling and analytical procedure, the effects of mechanical properties, rotational velocity, and orientation of cracks on Stress Intensity Factors (SIF) in rotating disks under centrifugal loading are investigated. Also, the effects of using composite patch in reduction of SIF in rotating disks are studied. By that way, the effects of patching design variables like mechanical properties, thickness, and ply angle are investigated individually. <p class="card-text"><strong>Keywords:</strong> <a href="https://publications.waset.org/abstracts/search?q=stress%20intensity%20factor" title="stress intensity factor">stress intensity factor</a>, <a href="https://publications.waset.org/abstracts/search?q=semi-elliptical%20crack" title=" semi-elliptical crack"> semi-elliptical crack</a>, <a href="https://publications.waset.org/abstracts/search?q=rotating%20disk" title=" rotating disk"> rotating disk</a>, <a href="https://publications.waset.org/abstracts/search?q=finite%20element%20analysis%20%28FEA%29" title=" finite element analysis (FEA)"> finite element analysis (FEA)</a> </p> <a href="https://publications.waset.org/abstracts/47599/calculation-of-stress-intensity-factors-in-rotating-disks-containing-3d-semi-elliptical-cracks" class="btn btn-primary btn-sm">Procedia</a> <a href="https://publications.waset.org/abstracts/47599.pdf" target="_blank" class="btn btn-primary btn-sm">PDF</a> <span class="bg-info text-light px-1 py-1 float-right rounded"> Downloads <span class="badge badge-light">364</span> </span> </div> </div> <div class="card paper-listing mb-3 mt-3"> <h5 class="card-header" style="font-size:.9rem"><span class="badge badge-info">466</span> Investigation for the Mechanism of Lateral-Torsional Coupled Vibration of the Propulsion Shaft in a Ship</h5> <div class="card-body"> <p class="card-text"><strong>Authors:</strong> <a href="https://publications.waset.org/abstracts/search?q=Hyungsuk%20Han">Hyungsuk Han</a>, <a href="https://publications.waset.org/abstracts/search?q=Soohong%20Jeon"> Soohong Jeon</a>, <a href="https://publications.waset.org/abstracts/search?q=Chungwon%20Lee"> Chungwon Lee</a>, <a href="https://publications.waset.org/abstracts/search?q=YongHoon%20Kim"> YongHoon Kim</a> </p> <p class="card-text"><strong>Abstract:</strong></p> When a rubber mount and flexible coupling are installed on the main engine, high torsional vibration can occur. The root cause of this high torsional vibration can be attributed to the lateral-torsional coupled vibration of the shaft system. Therefore, the lateral-torsional coupled vibration is investigated numerically after approximating the shaft system to a three-degrees-of-freedom Jeffcott rotor. To verify that the high torsional vibration is caused by the lateral-torsional coupled vibration, a test unit that can simulate this lateral-torsional coupled vibration occurring in the propulsion shaft is developed. Performing a vibration test with the test unit, it can be experimentally verified that the high torsional vibration occurring in the propulsion shaft of the particular ship was caused by the lateral-torsional coupled vibration. <p class="card-text"><strong>Keywords:</strong> <a href="https://publications.waset.org/abstracts/search?q=Jeffcott%20rotor" title="Jeffcott rotor">Jeffcott rotor</a>, <a href="https://publications.waset.org/abstracts/search?q=lateral-torsional%20coupled%20vibration" title=" lateral-torsional coupled vibration"> lateral-torsional coupled vibration</a>, <a href="https://publications.waset.org/abstracts/search?q=propulsion%20shaft" title=" propulsion shaft"> propulsion shaft</a>, <a href="https://publications.waset.org/abstracts/search?q=stability" title=" stability"> stability</a> </p> <a href="https://publications.waset.org/abstracts/107458/investigation-for-the-mechanism-of-lateral-torsional-coupled-vibration-of-the-propulsion-shaft-in-a-ship" class="btn btn-primary btn-sm">Procedia</a> <a href="https://publications.waset.org/abstracts/107458.pdf" target="_blank" class="btn btn-primary btn-sm">PDF</a> <span class="bg-info text-light px-1 py-1 float-right rounded"> Downloads <span class="badge badge-light">227</span> </span> </div> </div> <div class="card paper-listing mb-3 mt-3"> <h5 class="card-header" style="font-size:.9rem"><span class="badge badge-info">465</span> Productivity Improvement in the Propeller Shaft Manufacturing Process </h5> <div class="card-body"> <p class="card-text"><strong>Authors:</strong> <a href="https://publications.waset.org/abstracts/search?q=Won%20Jung">Won Jung</a> </p> <p class="card-text"><strong>Abstract:</strong></p> In automotive, propeller shaft is the device for transferring power from engine to axle via transmission, and the slip yoke is one of the main parts in the component. Since the propeller shafts are subject to torsion and shear stress, they need to be strong enough to bear the stress. The purpose of this research is to improve the productivity of slip yoke for automotive propeller shaft. We present how to redesign the component that currently manufactured as a forged single body type. The research was focused on not only reducing processing time but insuring durability of the component simultaneously. <p class="card-text"><strong>Keywords:</strong> <a href="https://publications.waset.org/abstracts/search?q=automotive" title="automotive">automotive</a>, <a href="https://publications.waset.org/abstracts/search?q=propeller%20shaft" title=" propeller shaft"> propeller shaft</a>, <a href="https://publications.waset.org/abstracts/search?q=productivity" title=" productivity"> productivity</a>, <a href="https://publications.waset.org/abstracts/search?q=durability" title=" durability"> durability</a>, <a href="https://publications.waset.org/abstracts/search?q=slip%20yoke" title=" slip yoke"> slip yoke</a> </p> <a href="https://publications.waset.org/abstracts/17015/productivity-improvement-in-the-propeller-shaft-manufacturing-process" class="btn btn-primary btn-sm">Procedia</a> <a href="https://publications.waset.org/abstracts/17015.pdf" target="_blank" class="btn btn-primary btn-sm">PDF</a> <span class="bg-info text-light px-1 py-1 float-right rounded"> Downloads <span class="badge badge-light">378</span> </span> </div> </div> <div class="card paper-listing mb-3 mt-3"> <h5 class="card-header" style="font-size:.9rem"><span class="badge badge-info">464</span> Effect of Size and Soil Characteristic on Contribution of Side and Tip Resistance of the Drilled Shafts Axial Load Carrying Capacity </h5> <div class="card-body"> <p class="card-text"><strong>Authors:</strong> <a href="https://publications.waset.org/abstracts/search?q=Mehrak%20Zargaryaeghoubi">Mehrak Zargaryaeghoubi</a>, <a href="https://publications.waset.org/abstracts/search?q=Masood%20Hajali"> Masood Hajali</a> </p> <p class="card-text"><strong>Abstract:</strong></p> Drilled shafts are the most popular of deep foundations, because they have the capability that one single shaft can easily carry the entire load of a large column from a bridge or tall building. Drilled shaft may be an economical alternative to pile foundations because a pile cap is not needed, which not only reduces that expense, but also provides a rough surface in the border of soil and concrete to carry a more axial load. Due to the larger construction sizes of drilled shafts, they have an excellent axial load carrying capacity. Part of the axial load carrying capacity of the drilled shaft is resisted by the soil below the tip of the shaft which is tip resistance and the other part is resisted by the friction developed around the drilled shaft which is side resistance. The condition at the bottom of the excavation can affect the end bearing capacity of the drilled shaft. Also, type of the soil and size of the drilled shaft can affect the frictional resistance. The main loads applied on the drilled shafts are axial compressive loads. It is important to know how many percent of the maximum applied load will be shed inside friction and how much will be transferred to the base. The axial capacity of the drilled shaft foundation is influenced by the size of the drilled shaft, and soil characteristics. In this study, the effect of the size and soil characteristic will be investigated on the contribution of side resistance and end-bearing capacity. Also, the study presents a three-dimensional finite element modeling of a drilled shaft subjected to axial load using ANSYS. The top displacement and settlement of the drilled shaft are verified with analytical results. The soil profile is considered as Table 1 and for a drilled shaft with 7 ft diameter and 95 ft length the stresses in z-direction are calculated through the length of the shaft. From the stresses in z-direction through the length of the shaft the side resistance can be calculated and with the z-direction stress at the tip, the tip resistance can be calculated. The result of the side and tip resistance for this drilled shaft are compared with the analytical results. <p class="card-text"><strong>Keywords:</strong> <a href="https://publications.waset.org/abstracts/search?q=Drilled%20Shaft%20Foundation" title="Drilled Shaft Foundation">Drilled Shaft Foundation</a>, <a href="https://publications.waset.org/abstracts/search?q=size%20and%20soil%20characteristic" title=" size and soil characteristic"> size and soil characteristic</a>, <a href="https://publications.waset.org/abstracts/search?q=axial%20load%20capacity" title=" axial load capacity"> axial load capacity</a>, <a href="https://publications.waset.org/abstracts/search?q=Finite%20Element" title=" Finite Element"> Finite Element</a> </p> <a href="https://publications.waset.org/abstracts/16215/effect-of-size-and-soil-characteristic-on-contribution-of-side-and-tip-resistance-of-the-drilled-shafts-axial-load-carrying-capacity" class="btn btn-primary btn-sm">Procedia</a> <a href="https://publications.waset.org/abstracts/16215.pdf" target="_blank" class="btn btn-primary btn-sm">PDF</a> <span class="bg-info text-light px-1 py-1 float-right rounded"> Downloads <span class="badge badge-light">379</span> </span> </div> </div> <div class="card paper-listing mb-3 mt-3"> <h5 class="card-header" style="font-size:.9rem"><span class="badge badge-info">463</span> Design and Performance of a Large Diameter Shaft in Old Alluvium</h5> <div class="card-body"> <p class="card-text"><strong>Authors:</strong> <a href="https://publications.waset.org/abstracts/search?q=Tamilmani%20Thiruvengadam">Tamilmani Thiruvengadam</a>, <a href="https://publications.waset.org/abstracts/search?q=Ramasthanan%20Arulampalam"> Ramasthanan Arulampalam</a> </p> <p class="card-text"><strong>Abstract:</strong></p> This project comprises laying approximately 1.8km of 400mm, 1200mm and 2400mm diameter sewer pipes using pipe jacking machines along Mugliston Park, Buangkok Drive, and Buangkok Link. The works include an estimated 14 circular shafts with depth ranging from 10.0 meters to 29.0 meters. Cast in-situ circular shaft will be used for the temporary shaft excavation. The geology is predominantly Backfill and old alluvium with weak material encountered in between. Where there is a very soft clay, F1 material or weak soil is expected, ground improvement will be carried out outside of the shaft followed by cast in-situ concrete ring wall within the improved soil zone. This paper presents the design methodology, analysis and results of temporary shafts for micro TBM launching and constructing permanent manholes. There is also a comparison of instrumentation readings with the analysis predicted values. <p class="card-text"><strong>Keywords:</strong> <a href="https://publications.waset.org/abstracts/search?q=circular%20shaft" title="circular shaft">circular shaft</a>, <a href="https://publications.waset.org/abstracts/search?q=ground%20improvement" title=" ground improvement"> ground improvement</a>, <a href="https://publications.waset.org/abstracts/search?q=old%20alluvium" title=" old alluvium"> old alluvium</a>, <a href="https://publications.waset.org/abstracts/search?q=temporary%20shaft" title=" temporary shaft"> temporary shaft</a> </p> <a href="https://publications.waset.org/abstracts/65270/design-and-performance-of-a-large-diameter-shaft-in-old-alluvium" class="btn btn-primary btn-sm">Procedia</a> <a href="https://publications.waset.org/abstracts/65270.pdf" target="_blank" class="btn btn-primary btn-sm">PDF</a> <span class="bg-info text-light px-1 py-1 float-right rounded"> Downloads <span class="badge badge-light">287</span> </span> </div> </div> <div class="card paper-listing mb-3 mt-3"> <h5 class="card-header" style="font-size:.9rem"><span class="badge badge-info">462</span> Analytical Method for Seismic Analysis of Shaft-Tunnel Junction under Longitudinal Excitations</h5> <div class="card-body"> <p class="card-text"><strong>Authors:</strong> <a href="https://publications.waset.org/abstracts/search?q=Jinghua%20Zhang">Jinghua Zhang</a> </p> <p class="card-text"><strong>Abstract:</strong></p> Shaft-tunnel junction is a typical case of the structural nonuniformity in underground structures. The shaft and the tunnel possess greatly different structural features. Even under uniform excitations, they tend to behave discrepantly. Studies on shaft-tunnel junctions are mainly performed numerically. Shaking table tests are also conducted. Although many numerical and experimental data are obtained, an analytical solution still has great merits of gaining more insights into the shaft-tunnel problem. This paper will try to remedy the situation. Since the seismic responses of shaft-tunnel junctions are very related to directions of the excitations, they are studied in two scenarios: the longitudinal-excitation scenario and the transverse-excitation scenario. The former scenario will be addressed in this paper. Given that responses of the tunnel are highly dependent on the shaft, the analytical solutions would be developed firstly for the vertical shaft. Then, the seismic responses of the tunnel would be discussed. Since vertical shafts bear a resemblance to rigid caissons, the solution proposed in this paper is derived by introducing terms of shaft-tunnel and soil-tunnel interactions into equations originally developed for rigid caissons. The validity of the solution is examined by a validation model computed by finite element method. The mutual influence between the shaft and the tunnel is introduced. The soil-structure interactions are discussed parametrically based on the proposed equations. The shaft-tunnel relative displacement and the soil-tunnel relative stiffness are found to be the most important parameters affecting the magnitudes and distributions of the internal forces of the tunnel. A hinge-joint at the shaft-tunnel junction could significantly reduce the degree of stress concentration compared with a rigid joint. <p class="card-text"><strong>Keywords:</strong> <a href="https://publications.waset.org/abstracts/search?q=analytical%20solution" title="analytical solution">analytical solution</a>, <a href="https://publications.waset.org/abstracts/search?q=longitudinal%20excitation" title=" longitudinal excitation"> longitudinal excitation</a>, <a href="https://publications.waset.org/abstracts/search?q=numerical%20validation" title=" numerical validation "> numerical validation </a>, <a href="https://publications.waset.org/abstracts/search?q=shaft-tunnel%20junction" title=" shaft-tunnel junction "> shaft-tunnel junction </a> </p> <a href="https://publications.waset.org/abstracts/112550/analytical-method-for-seismic-analysis-of-shaft-tunnel-junction-under-longitudinal-excitations" class="btn btn-primary btn-sm">Procedia</a> <a href="https://publications.waset.org/abstracts/112550.pdf" target="_blank" class="btn btn-primary btn-sm">PDF</a> <span class="bg-info text-light px-1 py-1 float-right rounded"> Downloads <span class="badge badge-light">161</span> </span> </div> </div> <div class="card paper-listing mb-3 mt-3"> <h5 class="card-header" style="font-size:.9rem"><span class="badge badge-info">461</span> Analysis of Cyclic Elastic-Plastic Loading of Shaft Based on Kinematic Hardening Model</h5> <div class="card-body"> <p class="card-text"><strong>Authors:</strong> <a href="https://publications.waset.org/abstracts/search?q=Isa%20Ahmadi">Isa Ahmadi</a>, <a href="https://publications.waset.org/abstracts/search?q=Ramin%20Khamedi"> Ramin Khamedi</a> </p> <p class="card-text"><strong>Abstract:</strong></p> In this paper, the elasto-plastic and cyclic torsion of a shaft is studied using a finite element method. The Prager kinematic hardening theory of plasticity with the Ramberg and Osgood stress-strain equation is used to evaluate the cyclic loading behavior of the shaft under the torsional loading. The material of shaft is assumed to follow the non-linear strain hardening property based on the Prager model. The finite element method with C1 continuity is developed and used for solution of the governing equations of the problem. The successive substitution iterative method is used to calculate the distribution of stresses and plastic strains in the shaft due to cyclic loads. The shear stress, effective stress, residual stress and elastic and plastic shear strain distribution are presented in the numerical results. <p class="card-text"><strong>Keywords:</strong> <a href="https://publications.waset.org/abstracts/search?q=cyclic%20loading" title="cyclic loading">cyclic loading</a>, <a href="https://publications.waset.org/abstracts/search?q=finite%20element%20analysis" title=" finite element analysis"> finite element analysis</a>, <a href="https://publications.waset.org/abstracts/search?q=Prager%20kinematic%20hardening%20model" title=" Prager kinematic hardening model"> Prager kinematic hardening model</a>, <a href="https://publications.waset.org/abstracts/search?q=torsion%20of%20shaft" title=" torsion of shaft"> torsion of shaft</a> </p> <a href="https://publications.waset.org/abstracts/10130/analysis-of-cyclic-elastic-plastic-loading-of-shaft-based-on-kinematic-hardening-model" class="btn btn-primary btn-sm">Procedia</a> <a href="https://publications.waset.org/abstracts/10130.pdf" target="_blank" class="btn btn-primary btn-sm">PDF</a> <span class="bg-info text-light px-1 py-1 float-right rounded"> Downloads <span class="badge badge-light">408</span> </span> </div> </div> <div class="card paper-listing mb-3 mt-3"> <h5 class="card-header" style="font-size:.9rem"><span class="badge badge-info">460</span> Failure Analysis of Recoiler Mandrel Shaft Used for Coiling of Rolled Steel Sheet</h5> <div class="card-body"> <p class="card-text"><strong>Authors:</strong> <a href="https://publications.waset.org/abstracts/search?q=Sachin%20Pawar">Sachin Pawar</a>, <a href="https://publications.waset.org/abstracts/search?q=Suman%20Patra"> Suman Patra</a>, <a href="https://publications.waset.org/abstracts/search?q=Goutam%20Mukhopadhyay"> Goutam Mukhopadhyay</a> </p> <p class="card-text"><strong>Abstract:</strong></p> The primary function of a shaft is to transfer power. The shaft can be cast or forged and then machined to the final shape. Manufacturing of ~5 m length and 0.6 m diameter shaft is very critical. More difficult is to maintain its straightness during heat treatment and machining operations, which involve thermal and mechanical loads, respectively. During the machining operation of a such forged mandrel shaft, a deflection of 3-4mm was observed. To remove this deflection shaft was pressed at both ends which led to the development of cracks in it. To investigate the root cause of the deflection and cracking, the sample was cut from the failed shaft. Possible causes were identified with the help of a cause and effect diagram. Chemical composition analysis, microstructural analysis, and hardness measurement were done to confirm whether the shaft meets the required specifications or not. Chemical composition analysis confirmed that the material grade was 42CrMo4. Microstructural analysis revealed the presence of untempered martensite, indicating improper heat treatment. Due to this, ductility and impact toughness values were considerably lower than the specification of the mentioned grade. Residual stress measurement of one more bent shaft manufactured by a similar route was done by portable X-ray diffraction(XRD) technique. For better understanding, measurements were done at twelve different locations along the length of the shaft. The occurrence of a high amount of undesirable tensile residual stresses close to the Ultimate Tensile Strength(UTS) of the material was observed. Untempered martensitic structure, lower ductility, lower impact strength, and presence of a high amount of residual stresses all confirmed the improper tempering heat treatment of the shaft. Tempering relieves the residual stresses. Based on the findings of this study, stress-relieving heat treatment was done to remove the residual stresses and deflection in the shaft successfully. <p class="card-text"><strong>Keywords:</strong> <a href="https://publications.waset.org/abstracts/search?q=residual%20stress" title="residual stress">residual stress</a>, <a href="https://publications.waset.org/abstracts/search?q=mandrel%20shaft" title=" mandrel shaft"> mandrel shaft</a>, <a href="https://publications.waset.org/abstracts/search?q=untempered%20martensite" title=" untempered martensite"> untempered martensite</a>, <a href="https://publications.waset.org/abstracts/search?q=portable%20XRD" title=" portable XRD"> portable XRD</a> </p> <a href="https://publications.waset.org/abstracts/107065/failure-analysis-of-recoiler-mandrel-shaft-used-for-coiling-of-rolled-steel-sheet" class="btn btn-primary btn-sm">Procedia</a> <a href="https://publications.waset.org/abstracts/107065.pdf" target="_blank" class="btn btn-primary btn-sm">PDF</a> <span class="bg-info text-light px-1 py-1 float-right rounded"> Downloads <span class="badge badge-light">112</span> </span> </div> </div> <div class="card paper-listing mb-3 mt-3"> <h5 class="card-header" style="font-size:.9rem"><span class="badge badge-info">459</span> Failure Analysis and Fatigue Life Estimation of a Shaft of a Rotary Draw Bending Machine </h5> <div class="card-body"> <p class="card-text"><strong>Authors:</strong> <a href="https://publications.waset.org/abstracts/search?q=B.%20Engel">B. Engel</a>, <a href="https://publications.waset.org/abstracts/search?q=Sara%20Salman%20Hassan%20Al-Maeeni"> Sara Salman Hassan Al-Maeeni </a> </p> <p class="card-text"><strong>Abstract:</strong></p> Human consumption of the Earth's resources increases the need for a sustainable development as an important ecological, social, and economic theme. Re-engineering of machine tools, in terms of design and failure analysis, is defined as steps performed on an obsolete machine to return it to a new machine with the warranty that matches the customer requirement. To understand the future fatigue behavior of the used machine components, it is important to investigate the possible causes of machine parts failure through design, surface, and material inspections. In this study, the failure modes of the shaft of the rotary draw bending machine are inspected. Furthermore, stress and deflection analysis of the shaft subjected to combined torsion and bending loads are carried out by an analytical method and compared with a finite element analysis method. The theoretical fatigue strength, correction factors, and fatigue life sustained by the shaft before damaged are estimated by creating a stress-cycle (S-N) diagram. In conclusion, it is seen that the shaft can work in the second life, but it needs some surface treatments to increase the reliability and fatigue life. <p class="card-text"><strong>Keywords:</strong> <a href="https://publications.waset.org/abstracts/search?q=failure%20analysis" title="failure analysis">failure analysis</a>, <a href="https://publications.waset.org/abstracts/search?q=fatigue%20life" title=" fatigue life"> fatigue life</a>, <a href="https://publications.waset.org/abstracts/search?q=FEM%20analysis" title=" FEM analysis"> FEM analysis</a>, <a href="https://publications.waset.org/abstracts/search?q=shaft" title=" shaft"> shaft</a>, <a href="https://publications.waset.org/abstracts/search?q=stress%20analysis" title=" stress analysis"> stress analysis</a> </p> <a href="https://publications.waset.org/abstracts/79871/failure-analysis-and-fatigue-life-estimation-of-a-shaft-of-a-rotary-draw-bending-machine" class="btn btn-primary btn-sm">Procedia</a> <a href="https://publications.waset.org/abstracts/79871.pdf" target="_blank" class="btn btn-primary btn-sm">PDF</a> <span class="bg-info text-light px-1 py-1 float-right rounded"> Downloads <span class="badge badge-light">301</span> </span> </div> </div> <div class="card paper-listing mb-3 mt-3"> <h5 class="card-header" style="font-size:.9rem"><span class="badge badge-info">458</span> Shaft Friction of Bored Pile Socketed in Weathered Limestone in Qatar</h5> <div class="card-body"> <p class="card-text"><strong>Authors:</strong> <a href="https://publications.waset.org/abstracts/search?q=Thanawat%20Chuleekiat">Thanawat Chuleekiat</a> </p> <p class="card-text"><strong>Abstract:</strong></p> Socketing of bored piles in rock is always seen as a matter of debate on construction sites between consultants and contractors. The socketing depth normally depends on the type of rock, depth at which the rock is available below the pile cap and load carrying capacity of the pile. In this paper, the review of field load test data of drilled shaft socketed in weathered limestone conducted using conventional static pile load test and dynamic pile load test was made to evaluate a unit shaft friction for the bored piles socketed in weathered limestone (weak rock). The borehole drilling data were also reviewed in conjunction with the pile test result. In addition, the back-calculated unit shaft friction was reviewed against various empirical methods for bored piles socketed in weak rock. The paper concludes with an estimated ultimate unit shaft friction from the case study in Qatar for preliminary design. <p class="card-text"><strong>Keywords:</strong> <a href="https://publications.waset.org/abstracts/search?q=piled%20foundation" title="piled foundation">piled foundation</a>, <a href="https://publications.waset.org/abstracts/search?q=weathered%20limestone" title=" weathered limestone"> weathered limestone</a>, <a href="https://publications.waset.org/abstracts/search?q=shaft%20friction" title=" shaft friction"> shaft friction</a>, <a href="https://publications.waset.org/abstracts/search?q=rock%20socket" title=" rock socket"> rock socket</a>, <a href="https://publications.waset.org/abstracts/search?q=pile%20load%20test" title=" pile load test"> pile load test</a> </p> <a href="https://publications.waset.org/abstracts/92705/shaft-friction-of-bored-pile-socketed-in-weathered-limestone-in-qatar" class="btn btn-primary btn-sm">Procedia</a> <a href="https://publications.waset.org/abstracts/92705.pdf" target="_blank" class="btn btn-primary btn-sm">PDF</a> <span class="bg-info text-light px-1 py-1 float-right rounded"> Downloads <span class="badge badge-light">180</span> </span> </div> </div> <div class="card paper-listing mb-3 mt-3"> <h5 class="card-header" style="font-size:.9rem"><span class="badge badge-info">457</span> Design and Analysis of a Laminated Composite Automotive Drive Shaft</h5> <div class="card-body"> <p class="card-text"><strong>Authors:</strong> <a href="https://publications.waset.org/abstracts/search?q=Hossein%20Kh.%20Bisheh">Hossein Kh. Bisheh</a>, <a href="https://publications.waset.org/abstracts/search?q=Nan%20Wu"> Nan Wu</a> </p> <p class="card-text"><strong>Abstract:</strong></p> Advanced composite materials have a great importance in engineering structures due to their high specific modulus and strength and low weight. These materials can be used in design and fabrication of automotive drive shafts to reduce the weight of the structure. Hence, an optimum design of a composite drive shaft satisfying the design criteria, can be an appropriate substitution of metallic drive shafts. The aim of this study is to design and analyze a composite automotive drive shaft with high specific strength and low weight satisfying the design criteria. Tsai-Wu criterion is chosen as the failure criterion. Various designs with different lay-ups and materials are investigated based on the design requirements and finally, an optimum design satisfying the design criteria is chosen based on the weight and cost considerations. The results of this study indicate that if the weight is the main concern, a shaft made of Carbon/Epoxy can be a good option, and if the cost is a more important parameter, a hybrid shaft made of aluminum and Carbon/Epoxy can be considered. <p class="card-text"><strong>Keywords:</strong> <a href="https://publications.waset.org/abstracts/search?q=Bending%20natural%20frequency" title="Bending natural frequency">Bending natural frequency</a>, <a href="https://publications.waset.org/abstracts/search?q=Composite%20drive%20shaft" title=" Composite drive shaft"> Composite drive shaft</a>, <a href="https://publications.waset.org/abstracts/search?q=Peak%20torque" title=" Peak torque"> Peak torque</a>, <a href="https://publications.waset.org/abstracts/search?q=Torsional%20buckling" title=" Torsional buckling"> Torsional buckling</a> </p> <a href="https://publications.waset.org/abstracts/96457/design-and-analysis-of-a-laminated-composite-automotive-drive-shaft" class="btn btn-primary btn-sm">Procedia</a> <a href="https://publications.waset.org/abstracts/96457.pdf" target="_blank" class="btn btn-primary btn-sm">PDF</a> <span class="bg-info text-light px-1 py-1 float-right rounded"> Downloads <span class="badge badge-light">232</span> </span> </div> </div> <div class="card paper-listing mb-3 mt-3"> <h5 class="card-header" style="font-size:.9rem"><span class="badge badge-info">456</span> Natural Frequency Analysis of a Porous Functionally Graded Shaft System</h5> <div class="card-body"> <p class="card-text"><strong>Authors:</strong> <a href="https://publications.waset.org/abstracts/search?q=Natural%20Frequency%20Analysis%20of%20a%20Porous%20Functionally%20Graded%20Shaft%20System">Natural Frequency Analysis of a Porous Functionally Graded Shaft System</a> </p> <p class="card-text"><strong>Abstract:</strong></p> The vibration characteristics of a functionally graded (FG) rotor model having porosities and micro-voids is investigated using three-dimensional finite element analysis. The FG shaft is mounted with a steel disc located at the midspan. The shaft ends are supported on isotropic bearings. The FG material is composed of a metallic (stainless-steel) and ceramic phase (zirconium oxide) as its constituent phases. The layer wise material property variation is governed by power law. Material property equations are developed for the porosity modelling. Python code is developed to assign the material properties to each layer including the effect of porosities. ANSYS commercial software is used to extract the natural frequencies and whirl frequencies for the FG shaft system. The obtained results show the influence of porosity volume fraction and power-law index, on the vibration characteristics of the ceramic-based FG shaft system. <p class="card-text"><strong>Keywords:</strong> <a href="https://publications.waset.org/abstracts/search?q=Finite%20element%20method" title="Finite element method">Finite element method</a>, <a href="https://publications.waset.org/abstracts/search?q=Functionally%20graded%20material" title=" Functionally graded material"> Functionally graded material</a>, <a href="https://publications.waset.org/abstracts/search?q=Porosity%20volume%20fraction" title=" Porosity volume fraction"> Porosity volume fraction</a>, <a href="https://publications.waset.org/abstracts/search?q=Power%20law" title=" Power law"> Power law</a> </p> <a href="https://publications.waset.org/abstracts/123449/natural-frequency-analysis-of-a-porous-functionally-graded-shaft-system" class="btn btn-primary btn-sm">Procedia</a> <a href="https://publications.waset.org/abstracts/123449.pdf" target="_blank" class="btn btn-primary btn-sm">PDF</a> <span class="bg-info text-light px-1 py-1 float-right rounded"> Downloads <span class="badge badge-light">205</span> </span> </div> </div> <div class="card paper-listing mb-3 mt-3"> <h5 class="card-header" style="font-size:.9rem"><span class="badge badge-info">455</span> Vibration Control of a Horizontally Supported Rotor System by Using a Radial Active Magnetic Bearing</h5> <div class="card-body"> <p class="card-text"><strong>Authors:</strong> <a href="https://publications.waset.org/abstracts/search?q=Vishnu%20A.">Vishnu A.</a>, <a href="https://publications.waset.org/abstracts/search?q=Ashesh%20Saha"> Ashesh Saha</a> </p> <p class="card-text"><strong>Abstract:</strong></p> The operation of high-speed rotating machinery in industries is accompanied by rotor vibrations due to many factors. One of the primary instability mechanisms in a rotor system is the centrifugal force induced due to the eccentricity of the center of mass away from the center of rotation. These unwanted vibrations may lead to catastrophic fatigue failure. So, there is a need to control these rotor vibrations. In this work, control of rotor vibrations by using a 4-pole Radial Active Magnetic Bearing (RAMB) as an actuator is analysed. A continuous rotor system model is considered for the analysis. Several important factors, like the gyroscopic effect and rotary inertia of the shaft and disc, are incorporated into this model. The large deflection of the shaft and the restriction to axial motion of the shaft at the bearings result in nonlinearities in the system governing equation. The rotor system is modeled in such a way that the system dynamics can be related to the geometric and material properties of the shaft and disc. The mathematical model of the rotor system is developed by incorporating the control forces generated by the RAMB. A simple PD controller is used for the attenuation of system vibrations. An analytical expression for the amplitude and phase equations is derived using the Method of Multiple Scales (MMS). Analytical results are verified with the numerical results obtained using an ‘ode’ solver in-built into MATLAB Software. The control force is found to be effective in attenuating the system vibrations. The multi-valued solutions leading to the jump phenomenon are also eliminated with a proper choice of control gains. Most interestingly, the shape of the backbone curves can also be altered for certain values of control parameters. <p class="card-text"><strong>Keywords:</strong> <a href="https://publications.waset.org/abstracts/search?q=rotor%20dynamics" title="rotor dynamics">rotor dynamics</a>, <a href="https://publications.waset.org/abstracts/search?q=continuous%20rotor%20system%20model" title=" continuous rotor system model"> continuous rotor system model</a>, <a href="https://publications.waset.org/abstracts/search?q=active%20magnetic%20bearing" title=" active magnetic bearing"> active magnetic bearing</a>, <a href="https://publications.waset.org/abstracts/search?q=PD%20controller" title=" PD controller"> PD controller</a>, <a href="https://publications.waset.org/abstracts/search?q=method%20of%20multiple%20scales" title=" method of multiple scales"> method of multiple scales</a>, <a href="https://publications.waset.org/abstracts/search?q=backbone%20curve" title=" backbone curve"> backbone curve</a> </p> <a href="https://publications.waset.org/abstracts/162558/vibration-control-of-a-horizontally-supported-rotor-system-by-using-a-radial-active-magnetic-bearing" class="btn btn-primary btn-sm">Procedia</a> <a href="https://publications.waset.org/abstracts/162558.pdf" target="_blank" class="btn btn-primary btn-sm">PDF</a> <span class="bg-info text-light px-1 py-1 float-right rounded"> Downloads <span class="badge badge-light">79</span> </span> </div> </div> <div class="card paper-listing mb-3 mt-3"> <h5 class="card-header" style="font-size:.9rem"><span class="badge badge-info">454</span> Fatigue Life Estimation Using N-Code for Drive Shaft of Passenger Vehicle</h5> <div class="card-body"> <p class="card-text"><strong>Authors:</strong> <a href="https://publications.waset.org/abstracts/search?q=Tae%20An%20Kim">Tae An Kim</a>, <a href="https://publications.waset.org/abstracts/search?q=Hyo%20Lim%20Kang"> Hyo Lim Kang</a>, <a href="https://publications.waset.org/abstracts/search?q=Hye%20Won%20Han"> Hye Won Han</a>, <a href="https://publications.waset.org/abstracts/search?q=Seung%20Ho%20Han"> Seung Ho Han</a> </p> <p class="card-text"><strong>Abstract:</strong></p> The drive shaft of passenger vehicle has its own function such as transmitting the engine torque from the gearbox and differential gears to the wheels. It must also compensate for all variations in angle or length resulting from manoeuvring and deflection for perfect synchronization between joints. Torsional fatigue failures occur frequently at the connection parts of the spline joints in the end of the drive shaft. In this study, the fatigue life of a drive shaft of passenger vehicle was estimated by using the finite element analysis. A commercial software of n-Code was applied under twisting load conditions, i.e. 0~134kgf•m and 0~188kgf•m, in which the shear strain range-fatigue life relationship considering Signed Shear method, Smith-Watson-Topper equation, Neuber-Hoffman Seeger method, size sensitivity factor and surface roughness effect was taken into account. The estimated fatigue life was verified by a twisting load test of the real drive shaft in a test rig. (Human Resource Training Project for Industry Matched R & D, KIAT, N036200004). <p class="card-text"><strong>Keywords:</strong> <a href="https://publications.waset.org/abstracts/search?q=drive%20shaft" title="drive shaft">drive shaft</a>, <a href="https://publications.waset.org/abstracts/search?q=fatigue%20life%20estimation" title=" fatigue life estimation"> fatigue life estimation</a>, <a href="https://publications.waset.org/abstracts/search?q=passenger%20vehicle" title=" passenger vehicle"> passenger vehicle</a>, <a href="https://publications.waset.org/abstracts/search?q=shear%20strain%20range-fatigue%20life%20relationship" title=" shear strain range-fatigue life relationship"> shear strain range-fatigue life relationship</a>, <a href="https://publications.waset.org/abstracts/search?q=torsional%20fatigue%20failure" title=" torsional fatigue failure"> torsional fatigue failure</a> </p> <a href="https://publications.waset.org/abstracts/75855/fatigue-life-estimation-using-n-code-for-drive-shaft-of-passenger-vehicle" class="btn btn-primary btn-sm">Procedia</a> <a href="https://publications.waset.org/abstracts/75855.pdf" target="_blank" class="btn btn-primary btn-sm">PDF</a> <span class="bg-info text-light px-1 py-1 float-right rounded"> Downloads <span class="badge badge-light">275</span> </span> </div> </div> <div class="card paper-listing mb-3 mt-3"> <h5 class="card-header" style="font-size:.9rem"><span class="badge badge-info">453</span> Effect of Installation Method on the Ratio of Tensile to Compressive Shaft Capacity of Piles in Dense Sand</h5> <div class="card-body"> <p class="card-text"><strong>Authors:</strong> <a href="https://publications.waset.org/abstracts/search?q=A.%20C.%20Galvis-Castro">A. C. Galvis-Castro</a>, <a href="https://publications.waset.org/abstracts/search?q=R.%20D.%20Tovar"> R. D. Tovar</a>, <a href="https://publications.waset.org/abstracts/search?q=R.%20Salgado"> R. Salgado</a>, <a href="https://publications.waset.org/abstracts/search?q=M.%20Prezzi"> M. Prezzi </a> </p> <p class="card-text"><strong>Abstract:</strong></p> It is generally accepted that the shaft capacity of piles in the sand is lower for tensile loading that for compressive loading. So far, very little attention has been paid to the role of the influence of the installation method on the tensile to compressive shaft capacity ratio. The objective of this paper is to analyze the effect of installation method on the tensile to compressive shaft capacity of piles in dense sand as observed in tests on half-circular model pile tests in a half-circular calibration chamber with digital image correlation (DIC) capability. Model piles are either monotonically jacked, jacked with multiple strokes or pre-installed into the dense sand samples. Digital images of the model pile and sand are taken during both the installation and loading stages of each test and processed using the DIC technique to obtain the soil displacement and strain fields. The study provides key insights into the mobilization of shaft resistance in tensile and compressive loading for both displacement and non-displacement piles. <p class="card-text"><strong>Keywords:</strong> <a href="https://publications.waset.org/abstracts/search?q=digital%20image%20correlation" title="digital image correlation">digital image correlation</a>, <a href="https://publications.waset.org/abstracts/search?q=piles" title=" piles"> piles</a>, <a href="https://publications.waset.org/abstracts/search?q=sand" title=" sand"> sand</a>, <a href="https://publications.waset.org/abstracts/search?q=shaft%20resistance" title=" shaft resistance"> shaft resistance</a> </p> <a href="https://publications.waset.org/abstracts/73964/effect-of-installation-method-on-the-ratio-of-tensile-to-compressive-shaft-capacity-of-piles-in-dense-sand" class="btn btn-primary btn-sm">Procedia</a> <a href="https://publications.waset.org/abstracts/73964.pdf" target="_blank" class="btn btn-primary btn-sm">PDF</a> <span class="bg-info text-light px-1 py-1 float-right rounded"> Downloads <span class="badge badge-light">272</span> </span> </div> </div> <div class="card paper-listing mb-3 mt-3"> <h5 class="card-header" style="font-size:.9rem"><span class="badge badge-info">452</span> Prediction of the Torsional Vibration Characteristics of a Rotor-Shaft System Using Its Scale Model and Scaling Laws</h5> <div class="card-body"> <p class="card-text"><strong>Authors:</strong> <a href="https://publications.waset.org/abstracts/search?q=Jia-Jang%20Wu">Jia-Jang Wu</a> </p> <p class="card-text"><strong>Abstract:</strong></p> This paper presents the scaling laws that provide the criteria of geometry and dynamic similitude between the full-size rotor-shaft system and its scale model, and can be used to predict the torsional vibration characteristics of the full-size rotor-shaft system by manipulating the corresponding data of its scale model. The scaling factors, which play fundamental roles in predicting the geometry and dynamic relationships between the full-size rotor-shaft system and its scale model, for torsional free vibration problems between scale and full-size rotor-shaft systems are firstly obtained from the equation of motion of torsional free vibration. Then, the scaling factor of external force (i.e., torque) required for the torsional forced vibration problems is determined based on the Newton’s second law. Numerical results show that the torsional free and forced vibration characteristics of a full-size rotor-shaft system can be accurately predicted from those of its scale models by using the foregoing scaling factors. For this reason, it is believed that the presented approach will be significant for investigating the relevant phenomenon in the scale model tests. <p class="card-text"><strong>Keywords:</strong> <a href="https://publications.waset.org/abstracts/search?q=torsional%20vibration" title="torsional vibration">torsional vibration</a>, <a href="https://publications.waset.org/abstracts/search?q=full-size%20model" title=" full-size model"> full-size model</a>, <a href="https://publications.waset.org/abstracts/search?q=scale%20model" title=" scale model"> scale model</a>, <a href="https://publications.waset.org/abstracts/search?q=scaling%20laws" title=" scaling laws"> scaling laws</a> </p> <a href="https://publications.waset.org/abstracts/13992/prediction-of-the-torsional-vibration-characteristics-of-a-rotor-shaft-system-using-its-scale-model-and-scaling-laws" class="btn btn-primary btn-sm">Procedia</a> <a href="https://publications.waset.org/abstracts/13992.pdf" target="_blank" class="btn btn-primary btn-sm">PDF</a> <span class="bg-info text-light px-1 py-1 float-right rounded"> Downloads <span class="badge badge-light">396</span> </span> </div> </div> <div class="card paper-listing mb-3 mt-3"> <h5 class="card-header" style="font-size:.9rem"><span class="badge badge-info">451</span> Developing an Intelligent Table Tennis Ball Machine with Human Play Simulation for Technical Training</h5> <div class="card-body"> <p class="card-text"><strong>Authors:</strong> <a href="https://publications.waset.org/abstracts/search?q=Chen-Chi%20An">Chen-Chi An</a>, <a href="https://publications.waset.org/abstracts/search?q=Jun-Yi%20He"> Jun-Yi He</a>, <a href="https://publications.waset.org/abstracts/search?q=Cheng-Han%20Hsieh"> Cheng-Han Hsieh</a>, <a href="https://publications.waset.org/abstracts/search?q=Chen-Ching%20Ting"> Chen-Ching Ting</a> </p> <p class="card-text"><strong>Abstract:</strong></p> This research has successfully developed an intelligent table tennis ball machine with human play simulate all situations of human play to take the service. It is well known; an excellent ball machine can help the table tennis coach to provide more efficient teaching, also give players the good technical training and entertainment. An excellent ball machine should be able to service all balls based on human play simulation due to the conventional competitions are today all taken place for people. In this work, two counter-rotating wheels are used to service the balls, where changing the absolute rotating speeds of the two wheels and the differences of rotating speeds between the two wheels can adjust the struck forces and the rotating speeds of the ball. The relationships between the absolute rotating speed of the two wheels and the struck forces of the ball as well as the differences rotating speeds between the two wheels and the rotating speeds of the ball are experimentally determined for technical development. The outlet speed, the ejected distance, and the rotating speed of the ball were measured by changing the absolute rotating speeds of the two wheels in terms of a series of differences in rotating speed between the two wheels for calibration of the ball machine; where the outlet speed and the ejected distance of the ball were further converted to the struck forces of the ball. In process, the balls serviced by the intelligent ball machine were based on the received calibration curves with help of the computer. Experiments technically used photosensitive devices to detect the outlet and rotating speed of the ball. Finally, this research developed some teaching programs for technical training using three ball machines and received more efficient training. <p class="card-text"><strong>Keywords:</strong> <a href="https://publications.waset.org/abstracts/search?q=table%20tennis" title="table tennis">table tennis</a>, <a href="https://publications.waset.org/abstracts/search?q=ball%20machine" title=" ball machine"> ball machine</a>, <a href="https://publications.waset.org/abstracts/search?q=human%20play%20simulation" title=" human play simulation"> human play simulation</a>, <a href="https://publications.waset.org/abstracts/search?q=counter-rotating%20wheels" title=" counter-rotating wheels"> counter-rotating wheels</a> </p> <a href="https://publications.waset.org/abstracts/49530/developing-an-intelligent-table-tennis-ball-machine-with-human-play-simulation-for-technical-training" class="btn btn-primary btn-sm">Procedia</a> <a href="https://publications.waset.org/abstracts/49530.pdf" target="_blank" class="btn btn-primary btn-sm">PDF</a> <span class="bg-info text-light px-1 py-1 float-right rounded"> Downloads <span class="badge badge-light">429</span> </span> </div> </div> <div class="card paper-listing mb-3 mt-3"> <h5 class="card-header" style="font-size:.9rem"><span class="badge badge-info">450</span> Mixed Mode Fracture Analyses Using Finite Element Method of Edge Cracked Heavy Spinning Annulus Pulley</h5> <div class="card-body"> <p class="card-text"><strong>Authors:</strong> <a href="https://publications.waset.org/abstracts/search?q=Bijit%20Kalita">Bijit Kalita</a>, <a href="https://publications.waset.org/abstracts/search?q=K.%20V.%20N.%20Surendra"> K. V. N. Surendra</a> </p> <p class="card-text"><strong>Abstract:</strong></p> Rotating disk is one of the most indispensable parts of a rotating machine. Rotating disk has found many applications in the diverging field of science and technology. In this paper, we have taken into consideration the problem of a heavy spinning disk mounted on a rotor system acted upon by boundary traction. Finite element modelling is used at various loading condition to determine the mixed mode stress intensity factors. The effect of combined shear and normal traction on the boundary is incorporated in the analysis under the action of gravity. The variation near the crack tip is characterized in terms of the stress intensity factor (SIF) with an aim to find the SIF for a wide range of parameters. The results of the finite element analyses carried out on the compressed disk of a belt pulley arrangement using fracture mechanics concepts are shown. A total of hundred cases of the problem are solved for each of the variations in loading arc parameter and crack orientation using finite element models of the disc under compression. All models were prepared and analyzed for the uncracked disk, disk with a single crack at different orientation emanating from shaft hole as well as for a disc with pair of cracks emerging from the same center hole. Curves are plotted for various loading conditions. Finally, crack propagation paths are determined using kink angle concepts. <p class="card-text"><strong>Keywords:</strong> <a href="https://publications.waset.org/abstracts/search?q=crack-tip%20deformations" title="crack-tip deformations">crack-tip deformations</a>, <a href="https://publications.waset.org/abstracts/search?q=static%20loading" title=" static loading"> static loading</a>, <a href="https://publications.waset.org/abstracts/search?q=stress%20concentration" title=" stress concentration"> stress concentration</a>, <a href="https://publications.waset.org/abstracts/search?q=stress%20intensity%20factor" title=" stress intensity factor"> stress intensity factor</a> </p> <a href="https://publications.waset.org/abstracts/105294/mixed-mode-fracture-analyses-using-finite-element-method-of-edge-cracked-heavy-spinning-annulus-pulley" class="btn btn-primary btn-sm">Procedia</a> <a href="https://publications.waset.org/abstracts/105294.pdf" target="_blank" class="btn btn-primary btn-sm">PDF</a> <span class="bg-info text-light px-1 py-1 float-right rounded"> Downloads <span class="badge badge-light">143</span> </span> </div> </div> <div class="card paper-listing mb-3 mt-3"> <h5 class="card-header" style="font-size:.9rem"><span class="badge badge-info">449</span> A Rotating Facility with High Temporal and Spatial Resolution Particle Image Velocimetry System to Investigate the Turbulent Boundary Layer Flow</h5> <div class="card-body"> <p class="card-text"><strong>Authors:</strong> <a href="https://publications.waset.org/abstracts/search?q=Ruquan%20You">Ruquan You</a>, <a href="https://publications.waset.org/abstracts/search?q=Haiwang%20Li"> Haiwang Li</a>, <a href="https://publications.waset.org/abstracts/search?q=Zhi%20Tao"> Zhi Tao</a> </p> <p class="card-text"><strong>Abstract:</strong></p> A time-resolved particle image velocimetry (PIV) system is developed to investigate the boundary layer flow with the effect of rotating Coriolis and buoyancy force. This time-resolved PIV system consists of a 10 Watts continuous laser diode and a high-speed camera. The laser diode is able to provide a less than 1mm thickness sheet light, and the high-speed camera can capture the 6400 frames per second with 1024×1024 pixels. The whole laser and the camera are fixed on the rotating facility with 1 radius meters and up to 500 revolutions per minute, which can measure the boundary flow velocity in the rotating channel with and without ribs directly at rotating conditions. To investigate the effect of buoyancy force, transparent heater glasses are used to provide the constant thermal heat flux, and then the density differences are generated near the channel wall, and the buoyancy force can be simulated when the channel is rotating. Due to the high temporal and spatial resolution of the system, the proper orthogonal decomposition (POD) can be developed to analyze the characteristic of the turbulent boundary layer flow at rotating conditions. With this rotating facility and PIV system, the velocity profile, Reynolds shear stress, spatial and temporal correlation, and the POD modes of the turbulent boundary layer flow can be discussed. <p class="card-text"><strong>Keywords:</strong> <a href="https://publications.waset.org/abstracts/search?q=rotating%20facility" title="rotating facility">rotating facility</a>, <a href="https://publications.waset.org/abstracts/search?q=PIV" title=" PIV"> PIV</a>, <a href="https://publications.waset.org/abstracts/search?q=boundary%20layer%20flow" title=" boundary layer flow"> boundary layer flow</a>, <a href="https://publications.waset.org/abstracts/search?q=spatial%20and%20temporal%20resolution" title=" spatial and temporal resolution"> spatial and temporal resolution</a> </p> <a href="https://publications.waset.org/abstracts/100655/a-rotating-facility-with-high-temporal-and-spatial-resolution-particle-image-velocimetry-system-to-investigate-the-turbulent-boundary-layer-flow" class="btn btn-primary btn-sm">Procedia</a> <a href="https://publications.waset.org/abstracts/100655.pdf" target="_blank" class="btn btn-primary btn-sm">PDF</a> <span class="bg-info text-light px-1 py-1 float-right rounded"> Downloads <span class="badge badge-light">180</span> </span> </div> </div> <div class="card paper-listing mb-3 mt-3"> <h5 class="card-header" style="font-size:.9rem"><span class="badge badge-info">448</span> Effect of CSL Tube Type on the Drilled Shaft Axial Load Carrying Capacity </h5> <div class="card-body"> <p class="card-text"><strong>Authors:</strong> <a href="https://publications.waset.org/abstracts/search?q=Ali%20Motevalli">Ali Motevalli</a>, <a href="https://publications.waset.org/abstracts/search?q=Shahin%20Nayyeri%20Amiri"> Shahin Nayyeri Amiri</a> </p> <p class="card-text"><strong>Abstract:</strong></p> Cross-Hole Sonic Logging (CSL) is a common type of Non-Destructive Testing (NDT) method, which is currently used to check the integrity of placed drilled shafts. CSL evaluates the integrity of the concrete inside the cage and between the access tubes based on propagation of ultrasonic waves between two or more access tubes. A number of access tubes are installed inside the reinforcing cage prior to concrete placement as guides for sensors. The access tubes can be PVC or steel galvanized based on ASTM6760. The type of the CSL tubes can affect the axial strength of the drilled shaft. The objective of this study is to compare the amount of axial load capacity of drilled shafts due to using a different type of CSL tubes inside the caging. To achieve this, three (3) large-scale drilled shaft samples were built and tested using a hydraulic actuator at the Florida International University’s (FIU) Titan America Structures and Construction Testing (TASCT) laboratory. During the static load test, load-displacement curves were recorded by the data acquisition system (MegaDAC). Three drilled shaft samples were built to evaluate the effect of the type of the CSL tube on the axial load capacity in drilled shaft foundations. <p class="card-text"><strong>Keywords:</strong> <a href="https://publications.waset.org/abstracts/search?q=drilled%20shaft%20foundations" title="drilled shaft foundations">drilled shaft foundations</a>, <a href="https://publications.waset.org/abstracts/search?q=axial%20load%20capacity" title=" axial load capacity"> axial load capacity</a>, <a href="https://publications.waset.org/abstracts/search?q=cage" title=" cage"> cage</a>, <a href="https://publications.waset.org/abstracts/search?q=PVC" title=" PVC"> PVC</a>, <a href="https://publications.waset.org/abstracts/search?q=galvanized%20tube" title=" galvanized tube"> galvanized tube</a>, <a href="https://publications.waset.org/abstracts/search?q=CSL%20tube" title=" CSL tube"> CSL tube</a> </p> <a href="https://publications.waset.org/abstracts/16073/effect-of-csl-tube-type-on-the-drilled-shaft-axial-load-carrying-capacity" class="btn btn-primary btn-sm">Procedia</a> <a href="https://publications.waset.org/abstracts/16073.pdf" target="_blank" class="btn btn-primary btn-sm">PDF</a> <span class="bg-info text-light px-1 py-1 float-right rounded"> Downloads <span class="badge badge-light">403</span> </span> </div> </div> <div class="card paper-listing mb-3 mt-3"> <h5 class="card-header" style="font-size:.9rem"><span class="badge badge-info">447</span> Value Addition of Quinoa (Chenopodium Quinoa Willd.) Using an Indigenously Developed Saponin Removal Machine</h5> <div class="card-body"> <p class="card-text"><strong>Authors:</strong> <a href="https://publications.waset.org/abstracts/search?q=M.A.%20Ali">M.A. Ali</a>, <a href="https://publications.waset.org/abstracts/search?q=M.%20Matloob"> M. Matloob</a>, <a href="https://publications.waset.org/abstracts/search?q=A.%20Sahar"> A. Sahar</a>, <a href="https://publications.waset.org/abstracts/search?q=M.%20Yamin"> M. Yamin</a>, <a href="https://publications.waset.org/abstracts/search?q=M.%20Imran"> M. Imran</a>, <a href="https://publications.waset.org/abstracts/search?q=Y.A.%20Yusof"> Y.A. Yusof</a> </p> <p class="card-text"><strong>Abstract:</strong></p> Quinoa (Chenopodium quinoa Willd.) is known as pseudocereal was originated in South America's Andes. Quinoa is a good source of protein, amino acids, micronutrients and bioactive components. The lack of gluten makes it suitable for celiac patients. Saponins, the leading ant-nutrient, are found in the pericarp, which adheres to the seed and transmits the bitter flavor to the quinoa grain. It is found in varying amounts in quinoa from 0.1% to 5%. This study was planned to design an indigenous machine to remove saponin from quinoa grains at the farm level to promote entrepreneurship. The machine consisted of a feeding hopper, rotating shaft, grooved stone, perforated steel cylinder, V-belts, pulleys, electric motor and mild steel angle iron and sheets. The motor transmitted power to the shaft with a belt drive. The shaft on which the grooved stone was attached rotated inside the perforated cylinder having a clearance of 2 mm and was removed saponin by an abrasion mechanism. The saponin-removed quinoa was then dipped in water to determine the presence of saponin as it produced foam in water and data were statistically analyzed. The results showed that the raw seed feeding rate of 25 g/s and milling time of 135 s completely removed saponin from seeds with minimum grain losses of 2.85% as compared to the economic analysis of the machine showed that its break-even point was achieved after one and half months with 18,000 s and a production capacity of 33 g/s. <p class="card-text"><strong>Keywords:</strong> <a href="https://publications.waset.org/abstracts/search?q=quinoa%20seeds" title="quinoa seeds">quinoa seeds</a>, <a href="https://publications.waset.org/abstracts/search?q=saponin" title=" saponin"> saponin</a>, <a href="https://publications.waset.org/abstracts/search?q=abrasion%20mechanism" title=" abrasion mechanism"> abrasion mechanism</a>, <a href="https://publications.waset.org/abstracts/search?q=stone%20polishing" title=" stone polishing"> stone polishing</a>, <a href="https://publications.waset.org/abstracts/search?q=indigenous%20machine" title=" indigenous machine"> indigenous machine</a> </p> <a href="https://publications.waset.org/abstracts/169734/value-addition-of-quinoa-chenopodium-quinoa-willd-using-an-indigenously-developed-saponin-removal-machine" class="btn btn-primary btn-sm">Procedia</a> <a href="https://publications.waset.org/abstracts/169734.pdf" target="_blank" class="btn btn-primary btn-sm">PDF</a> <span class="bg-info text-light px-1 py-1 float-right rounded"> Downloads <span class="badge badge-light">72</span> </span> </div> </div> <div class="card paper-listing mb-3 mt-3"> <h5 class="card-header" style="font-size:.9rem"><span class="badge badge-info">446</span> Optimization of Tolerance Grades of a Bearing and Shaft Assembly in a Washing Machine with Regard to Fatigue Life</h5> <div class="card-body"> <p class="card-text"><strong>Authors:</strong> <a href="https://publications.waset.org/abstracts/search?q=M.%20Cangi">M. Cangi</a>, <a href="https://publications.waset.org/abstracts/search?q=T.%20Dolar"> T. Dolar</a>, <a href="https://publications.waset.org/abstracts/search?q=C.%20Ersoy"> C. Ersoy</a>, <a href="https://publications.waset.org/abstracts/search?q=Y.%20E.%20Aydogdu"> Y. E. Aydogdu</a>, <a href="https://publications.waset.org/abstracts/search?q=A.%20I.%20Aydeniz"> A. I. Aydeniz</a>, <a href="https://publications.waset.org/abstracts/search?q=A.%20Mugan"> A. Mugan</a> </p> <p class="card-text"><strong>Abstract:</strong></p> The drum is one of the critical parts in a washing machine in which the clothes are washed and spin by the rotational movement. It is activated by the drum shaft which is attached to an electric motor and subjected to dynamic loading. Being one of the critical components, failures of the drum require costly repairs of dynamic components. In this study, tolerance bands between the drum shaft and its two bearings were examined to develop a relationship between the fatigue life of the shaft and the interaction tolerances. Optimization of tolerance bands was completed in consideration of the fatigue life of the shaft as the cost function. The following methodology is followed: multibody dynamic model of a washing machine was constructed and used to calculate dynamic loading on the components. Then, these forces were used in finite element analyses to calculate the stress field in critical components which was used for fatigue life predictions. The factors affecting the fatigue life were examined to find optimum tolerance grade for a given test condition. Numerical results were verified by experimental observations. <p class="card-text"><strong>Keywords:</strong> <a href="https://publications.waset.org/abstracts/search?q=fatigue%20life" title="fatigue life">fatigue life</a>, <a href="https://publications.waset.org/abstracts/search?q=finite%20element%20analysis" title=" finite element analysis"> finite element analysis</a>, <a href="https://publications.waset.org/abstracts/search?q=tolerance%20analysis" title=" tolerance analysis"> tolerance analysis</a>, <a href="https://publications.waset.org/abstracts/search?q=optimization" title=" optimization"> optimization</a> </p> <a href="https://publications.waset.org/abstracts/90903/optimization-of-tolerance-grades-of-a-bearing-and-shaft-assembly-in-a-washing-machine-with-regard-to-fatigue-life" class="btn btn-primary btn-sm">Procedia</a> <a href="https://publications.waset.org/abstracts/90903.pdf" target="_blank" class="btn btn-primary btn-sm">PDF</a> <span class="bg-info text-light px-1 py-1 float-right rounded"> Downloads <span class="badge badge-light">157</span> </span> </div> </div> <ul class="pagination"> <li class="page-item disabled"><span class="page-link">&lsaquo;</span></li> <li class="page-item active"><span class="page-link">1</span></li> <li class="page-item"><a class="page-link" href="https://publications.waset.org/abstracts/search?q=rotating%20shaft&page=2">2</a></li> <li class="page-item"><a class="page-link" href="https://publications.waset.org/abstracts/search?q=rotating%20shaft&page=3">3</a></li> <li class="page-item"><a class="page-link" href="https://publications.waset.org/abstracts/search?q=rotating%20shaft&page=4">4</a></li> <li class="page-item"><a class="page-link" href="https://publications.waset.org/abstracts/search?q=rotating%20shaft&page=5">5</a></li> <li class="page-item"><a class="page-link" href="https://publications.waset.org/abstracts/search?q=rotating%20shaft&page=6">6</a></li> <li class="page-item"><a class="page-link" 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