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25 pages, 9394 KiB  
Article
Microscale Temperature-Humidity Index (THI) Distribution Estimated at the City Scale: A Case Study in Maebashi City, Gunma Prefecture, Japan
by Kotaro Iizuka, Yuki Akiyama, Minaho Takase, Toshikazu Fukuba and Osamu Yachida
Remote Sens. 2024, 16(17), 3164; https://doi.org/10.3390/rs16173164 - 27 Aug 2024
Viewed by 1140
Abstract
Global warming and climate change are significantly impacting local climates, causing more intense heat during the summer season, which poses risks to individuals with pre-existing health conditions and negatively affects overall human health. While various studies have examined the Surface Urban Heat Island [...] Read more.
Global warming and climate change are significantly impacting local climates, causing more intense heat during the summer season, which poses risks to individuals with pre-existing health conditions and negatively affects overall human health. While various studies have examined the Surface Urban Heat Island (SUHI) phenomenon, these studies often focus on small to large geographic regions using low-to-moderate-resolution data, highlighting general thermal trends across large administrative areas. However, there is a growing need for methods that can detect microscale thermal patterns in environments familiar to urban residents, such as streets and alleys. The temperature-humidity index (THI), which incorporates both temperature and humidity data, serves as a critical measure of human-perceived heat. However, few studies have explored microscale THI variations within urban settings and identified potential THI hotspots at a local level where SUHI effects are pronounced. This research aims to address this gap by estimating THI at a finer resolution scale using data from multiple sensor platforms. We developed a model with the random forest algorithm to assess THI trends at a resolution of 0.5 m, utilizing various variables from different sources, including Landsat 8 land surface temperature (LST), unmanned aerial system (UAS)-derived LST, Sentinel-2 NDVI and NDMI, a wind exposure index, solar radiation modeled from aircraft and UAS-derived Digital Surface Models, and vehicle density and building floor area from social big data. Two models were constructed with different variables: Modelnatural, which includes variables related to only natural factors, and Modelmix, which includes all variables, including anthropogenic factors. The two models were compared to reveal how each source contributes to the model development and SUHI effects. The results show significant improvements, as Modelnatural had a fitting R2 = 0.5846, a root mean square error (RMSE) = 0.5936 and a mean absolute error (MAE) = 0.4294. Moreover, when anthropogenic factors were introduced, Modelmix performed even better, with R2 = 0.9638, RMSE = 0.1751, and MAE = 0.1065 (n = 923). This study contributes to the future of microscale SUHI analysis and offers important insights into urban planning and smart city development. Full article
(This article belongs to the Special Issue Remote Sensing: 15th Anniversary)
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Graphical abstract

Graphical abstract
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<p>Brightness temperature transition of the Tokyo metropolitan area and the surrounding landscape in Japan. Urban areas feature high temperatures, and the surrounding regions exhibit increasing thermal trends because of urban development.</p>
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<p>The UAS utilized in this work (Matrice 210 and Zenmuse-XT2).</p>
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<p>GNSS equipment (F9P) attached to a helmet (<b>left</b>) and a thermohygrometer (<b>right</b>).</p>
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<p>The flight path of the UAS for site 1 and the aerial views of the area. A1 is the main building of the closed junior high school. A2 is the school ground with partial vegetations covering.</p>
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<p>Overview of the study area (Gunma Prefecture, Maebashi City, Japan). Site 1 refers to the UAS survey site, while the whole scene shown on the right indicates the study region of the broad-scale estimation.</p>
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<p>The geographical location of the sampled areas for ground truth and the images from each location. A1: city’s main tree-lined street, A2: residential houses, B1: central station and the surroundings, C1: open built-up area, D1: park, E1: residential houses.</p>
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<p>Overall flowchart of the methods. The main datasets are listed on the far left and each process and usage of each data is shown through the flow. An additional variable is included in the final modeling process and two different models are output: variables containing only natural factors and both natural and anthropogenic factors.</p>
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<p>Ortho mosaicked image of the city and the generated DSM (<b>top</b>), and orthoimage and thermal data of site 1 (<b>bottom</b>). The thermal data at site 1 was observed at approximately 11:00 A.M. local time.</p>
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<p>Ortho mosaicked image of the city and the generated DSM (<b>top</b>), and orthoimage and thermal data of site 1 (<b>bottom</b>). The thermal data at site 1 was observed at approximately 11:00 A.M. local time.</p>
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<p>Explanatory variables for the city modeling. (<b>a</b>) diffuse shortwave solar radiation (Wh/m<sup>2</sup>), (<b>b</b>) direct shortwave solar radiation (Wh/m<sup>2</sup>), (<b>c</b>) total shortwave solar radiation (Wh/m<sup>2</sup>), (<b>d</b>) normalized difference vegetation index (NDVI), (<b>e</b>) normalized difference moisture index (NDMI), (<b>f</b>) wind exposure index (<b>g</b>) building floor area (m<sup>2</sup>), (<b>h</b>) vehicle density (points/m<sup>2</sup>), (<b>i</b>) land surface temperature (LST) from monowindow regression (°C) and (<b>j</b>) LST from the split-window algorithm (°C). LST<sub>SW</sub> is shown for comparison with the proposed LST<sub>MWR</sub>. The stray light effects are suppressed, but the LST values are maintained as in the LST<sub>SW</sub>.</p>
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<p>Explanatory variables for the city modeling. (<b>a</b>) diffuse shortwave solar radiation (Wh/m<sup>2</sup>), (<b>b</b>) direct shortwave solar radiation (Wh/m<sup>2</sup>), (<b>c</b>) total shortwave solar radiation (Wh/m<sup>2</sup>), (<b>d</b>) normalized difference vegetation index (NDVI), (<b>e</b>) normalized difference moisture index (NDMI), (<b>f</b>) wind exposure index (<b>g</b>) building floor area (m<sup>2</sup>), (<b>h</b>) vehicle density (points/m<sup>2</sup>), (<b>i</b>) land surface temperature (LST) from monowindow regression (°C) and (<b>j</b>) LST from the split-window algorithm (°C). LST<sub>SW</sub> is shown for comparison with the proposed LST<sub>MWR</sub>. The stray light effects are suppressed, but the LST values are maintained as in the LST<sub>SW</sub>.</p>
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<p>Relationship between the proposed LST<sub>MWR</sub> and LST<sub>SW</sub>. S.E = standard error.</p>
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<p>THI modeling results are based on the implementation of the random forest regression. The UHI trends within the city can be clearly distinguished at a microscale level (0.5 m resolution).</p>
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<p>Evaluation between the reference set and the modeled result. (<b>a</b>) Model<sub>natural</sub> is the developed model using only natural factors, and (<b>b</b>) Model<sub>mix</sub> includes anthropogenic factors. The R<sup>2</sup> here indicates how well the model fits the 1:1 line.</p>
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<p>The Importance of each variable is explained as the % increase in MSE (<b>top</b>) and mean increase in node purity (<b>bottom</b>). The red lines indicate that the variables are statistically significant (<span class="html-italic">p</span> ≤ 0.05).</p>
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<p>SHapley Additive exPlanations (SHAP) summary plot. The horizontal axis represents SHAP values (influence on THI), with each dot indicating the contribution of a variable at a specific feature value from the samples. The color gradient indicates the absolute value of each variable. The vertical axis lists the variables used in the model, ordered from the most to the least influential at the top.</p>
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29 pages, 6552 KiB  
Article
Sensitivity Analysis of Bogie Wheelbase and Axle Load for Low-Floor Freight Wagons, Based on Wheel Wear
by David S. Pellicer and Emilio Larrodé
Machines 2024, 12(8), 515; https://doi.org/10.3390/machines12080515 - 29 Jul 2024
Viewed by 904
Abstract
This paper shows the usage of a numerical analysis model that enables the calculation of the life of railway wheels used for low-floor freight wagons as a function of its primary operating factors, which allows for carrying out sensitivity analyses. Low-floor wagons are [...] Read more.
This paper shows the usage of a numerical analysis model that enables the calculation of the life of railway wheels used for low-floor freight wagons as a function of its primary operating factors, which allows for carrying out sensitivity analyses. Low-floor wagons are being increasingly used for combined transport applications, and many types of bogies have been proposed to constitute the wagons. Due to the uniqueness of this type of wagon, the bogie configurations in terms of wheelbase and axle load have hardly been analyzed so far. The numerical analysis model used addresses the primary challenges that arise in the vehicle–track interaction and establishes the relations among them. The main aspects of this model have been described in this paper, which has been later used to calculate the life of an ordinary-diameter wheel for several wheelbase and axle load values. This study has been replicated with reduced-diameter wheels, which are commonly used for low-floor wagons. In this way, it is possible to know the evolution of the life depending on the wheelbase and the axle load. The observed behaviors are not so dissimilar for the different types of wheels, and they point out huge increases in wear as the axle load and the wheelbase rise, especially with axle load. The root causes can be explained by the entire understanding of the rolling phenomenon provided by the full analytical work. Full article
(This article belongs to the Section Friction and Tribology)
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Figure 1
<p>Concept described above. Source: own elaboration.</p>
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<p>Illustration of the described conflict. Source: modification of a diagram from [<a href="#B4-machines-12-00515" class="html-bibr">4</a>].</p>
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<p>Flow diagram of the calculation process (algorithm). Source: own elaboration.</p>
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<p>Reference frames definition. Source: own elaboration.</p>
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<p>Wheelset positioning on a narrow curve. Source: own elaboration.</p>
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<p>Tangential forces and torques for a four-wheeled bogie. Source: own elaboration.</p>
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<p>Wheel reprofiling process. Source: own elaboration.</p>
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<p>(<b>a</b>) Placement of the <math display="inline"><semantics> <mrow> <mover accent="true"> <mrow> <mi mathvariant="script">u</mi> </mrow> <mo>¯</mo> </mover> <mover accent="true"> <mrow> <mi mathvariant="script">v</mi> </mrow> <mo>¯</mo> </mover> <mover accent="true"> <mrow> <mi mathvariant="script">w</mi> </mrow> <mo>¯</mo> </mover> </mrow> </semantics></math> reference frame for the bogies considered; (<b>b</b>) position of the wheelsets according to the curve direction; (<b>c</b>) relative positioning of the right wheel and rail at straight sections; (<b>d</b>) relative positioning of the left wheel and rail at straight sections; (<b>e</b>) adjustment between the left flange and rail for wear distribution. Source: own elaboration.</p>
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<p>(<b>a</b>) Diameter–mileage curve for the 920 mm diameter wheel with <span class="html-italic">e</span> = 1.800 m and <span class="html-italic">λ<sub>eje</sub></span> = 13,750 kg; (<b>b</b>) results for the same wheel, but with <span class="html-italic">e</span> = 1.800 m and <span class="html-italic">λ<sub>eje</sub></span> = 22,500 kg; (<b>c</b>) results for the same wheel, but with <span class="html-italic">e</span> = 1.020 m and <span class="html-italic">λ<sub>eje</sub></span> = 18,784 kg; (<b>d</b>) results for the same wheel, but with <span class="html-italic">e</span> = 2.540 m and <span class="html-italic">λ<sub>eje</sub></span> = 18,784 kg.</p>
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<p>(<b>e</b>) Diameter–mileage curve for the 355 mm diameter wheel with <span class="html-italic">e</span> = 1.800 m and <span class="html-italic">λ<sub>eje</sub></span> = 3750 kg; (<b>f</b>) results for the same wheel, but with <span class="html-italic">e</span> = 1.800 m and <span class="html-italic">λ<sub>eje</sub></span> = 5000 kg; (<b>g</b>) results for the same wheel, but with <span class="html-italic">e</span> = 1.365 m and <span class="html-italic">λ<sub>eje</sub></span> = 6996 kg; (<b>h</b>) results for the same wheel, but with <span class="html-italic">e</span> = 2.540 m and <span class="html-italic">λ<sub>eje</sub></span> = 6996 kg.</p>
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<p>(<b>a</b>) Life variation with axle load for 920 and 355 mm wheels; (<b>b</b>) life variation with wheelbase for the same wheels.</p>
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<p>Mean reprofiling span for each scenario.</p>
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<p>(<b>a</b>) Partial uncentering for different <span class="html-italic">r<sub>o</sub></span> and <span class="html-italic">R</span> values; (<b>b</b>) total uncentering for the same values.</p>
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14 pages, 7666 KiB  
Article
Validation of Frontal Crashworthiness Simulation for Low-Entry Type Bus Body According to UNECE R29 Requirements
by Kostyantyn Holenko, Oleksandr Dykha, Eugeniusz Koda, Ivan Kernytskyy, Yuriy Royko, Orest Horbay, Oksana Berezovetska, Vasyl Rys, Ruslan Humenuyk, Serhii Berezovetskyi, Mariusz Żółtowski, Anna Markiewicz and Tomasz Wierzbicki
Appl. Sci. 2024, 14(13), 5595; https://doi.org/10.3390/app14135595 - 27 Jun 2024
Viewed by 843
Abstract
Frontal crash tests are an essential element in assessing vehicle safety. They simulate a collision that occurs when the front of the bus hits another vehicle or an obstacle. In recent years, much attention has been paid to the frontal crash testing of [...] Read more.
Frontal crash tests are an essential element in assessing vehicle safety. They simulate a collision that occurs when the front of the bus hits another vehicle or an obstacle. In recent years, much attention has been paid to the frontal crash testing of city buses, especially after a series of accidents resulting in deaths and injuries. Unlike car manufacturers, most bus bodybuilders do not include deformation zones in their designs. The next two regulations are widely used to assess whether a structure can withstand impact loading: UNECE Regulation No. 29—United Nations Economic Commission for Europe (UNECE R29) and the New Car Assessment Program (NCAP), which is more typical of car crash tests. The main goal of the research is to develop an applicable methodology for a frontal impact simulation on a city bus, considering UNECE R29 requirements for the passenger’s safety and distinctive features of the low-entry body layout. Among the contributions to current knowledge are such research results as: unlike suburban and intercity buses, city buses are characterized by lower stiffness in the event of a frontal collision, and therefore, when developing new models, it is necessary to lay deformation zones (currently absent from most city buses). Maximum deformation values in the bus front part are reached earlier for R29 (137 ms) than for most impacts tested by NCAP (170–230 ms) but have higher values: 577 mm vs. 150–250 mm for the sills tested. Such a short shock absorption time and high deformations indicate a significantly lighter front part of a low-entry and low-floor bus compared with classic layouts. Furthermore, it is unjustified to use the R29 boundary conditions of trucks to attach the bus with chains behind its frontal axe both in natural tests and appropriate finite element simulation—the scheme of fixing the city bus should be accordingly adapted and normatively revised. Full article
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<p>UNECE Regulation No. 29 (UNECE R29) frontal impact safety standards schemes: (<b>a</b>) whole bus body frame model; (<b>b</b>) scheme of the front part.</p>
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<p>UNECE Regulation No. 29 (UNECE R29)—fixation of the vehicle: (<b>a</b>) side view of the model; (<b>b</b>) top view.</p>
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<p>UNECE R29 model of the bus body frame: (<b>a</b>) boundary conditions; (<b>b</b>) FEA mesh.</p>
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<p>Front impact according to UNECE R29: (<b>a</b>) hidden impactor; (<b>b</b>) shown impactor.</p>
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<p>The behavior of the bus body frame front part together with the driver’s position at various moments of impact ((<b>a</b>,<b>b</b>)—35–65 ms, (<b>c</b>)—100 ms, (<b>d</b>)—137 ms).</p>
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<p>The behavior of the bus body frame front part together with the driver’s position at various moments of impact ((<b>a</b>,<b>b</b>)—35–65 ms, (<b>c</b>)—100 ms, (<b>d</b>)—137 ms).</p>
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<p>Control points of the front part of the body for building a matrix of displacements.</p>
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<p>R29 frontal impact at 100 kJ impactor energy: (<b>a</b>) detailed mesh; (<b>b</b>) deformations.</p>
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15 pages, 6302 KiB  
Article
A New Rotary Magnetorheological Damper for a Semi-Active Suspension System of Low-Floor Vehicles
by Yu-Jin Park, Byung-Hyuk Kang and Seung-Bok Choi
Actuators 2024, 13(4), 155; https://doi.org/10.3390/act13040155 - 18 Apr 2024
Cited by 1 | Viewed by 1609
Abstract
This study explores the significance of active suspension systems for vehicles with lower chassis compared to conventional ones, aiming at the development of future automobiles. Conventional linear MR (magnetorheological) dampers were found inadequate in ensuring sufficient vibration control because the vehicle’s chassis becomes [...] Read more.
This study explores the significance of active suspension systems for vehicles with lower chassis compared to conventional ones, aiming at the development of future automobiles. Conventional linear MR (magnetorheological) dampers were found inadequate in ensuring sufficient vibration control because the vehicle’s chassis becomes lowered in the unmanned vehicles or purposed-based vehicles. As an alternative, a rotary type of MR damper is proposed in this work. The proposed damper is designed based on prespecified design parameters through mathematical modeling and magnetic field analyses. Subsequently, a prototype of the rotary MR damper identical to the design is fabricated, and effectiveness is shown through experimental investigations. In configuring the experiments, a proportional-integral (PI) controller is employed for current control to reduce the response time of the damper. The results presented in this work provide useful guidelines to develop a new type of MR damper applicable to various types of future vehicles’ suspension systems with low distance from the tire to the body floor. Full article
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<p>Schematic configuration of the linear MR damper.</p>
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<p>Height from the tire to the body floor: (<b>a</b>) conventional vehicle, (<b>b</b>) future car.</p>
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<p>Configurations of the rotary MR damper: (<b>a</b>) cylinder type, (<b>b</b>) key-home type.</p>
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<p>The schematic for flow direction and pressure drop of the rotary MR damper.</p>
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<p>Non-dimensional flow rate of the rotary MR damper using the parallel plate.</p>
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<p>Magnetic analysis of the rotary MR damper: (<b>a</b>) contour view front, isometric (140 km/A); (<b>b</b>) analysis results between the yield stress and current.</p>
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<p>Simulation of the field-dependent torque of the rotary MR damper.</p>
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<p>Pressure analysis of the rotary MR damper using CFD.</p>
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<p>The prototype of the proposed rotary MR damper: (<b>a</b>) assembled, (<b>b</b>) magnetic circuit core.</p>
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<p>Experimental apparatus for the damping force measurement.</p>
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<p>Damping force experiment results data, with simulation data reapplied with 0.2 m/s 0~3 A: (<b>a</b>) F–D curve for 0.2 m/s, (<b>b</b>) F–V curve for 0.2 m/s.</p>
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<p>Damping characteristics in F–V curve: (<b>a</b>) simulation, (<b>b</b>) measurement.</p>
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<p>PI control block diagram to achieve fast response time of the rotary MR damper.</p>
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19 pages, 5384 KiB  
Article
RBF-Based Integrated Optimization Method of Structural and Turning Parameters for Low-Floor Axle Bridge
by Xiaoke Li, Wenbo Xing, Qianlong Jiang, Zhenzhong Chen, Wenbo Zhao, Yapeng Xu, Yang Cao, Wuyi Ming and Jun Ma
Metals 2024, 14(3), 273; https://doi.org/10.3390/met14030273 - 25 Feb 2024
Viewed by 1238
Abstract
The axle bridge plays a crucial role in the bogie of low-floor light rail vehicles, impacting operational efficiency and fuel economy. To minimize the total cost of the structure and turning of axle bridges, an optimization model of structural and turning parameters was [...] Read more.
The axle bridge plays a crucial role in the bogie of low-floor light rail vehicles, impacting operational efficiency and fuel economy. To minimize the total cost of the structure and turning of axle bridges, an optimization model of structural and turning parameters was built, with the fatigue life, maximum stress, maximum deformation, and maximum main cutting force as constraints. Through orthogonal experiments and multivariate variance analysis, the key design variables which have a significant impact on optimization objectives and constraints (performance responses) were identified. Then the optimal Latin hypercube design and finite element simulation was used to build a Radial Basis Function (RBF) model to approximate the implicit relationship between design variables and performance responses. Finally, a multi-island genetic algorithm was applied to solve the integrated optimization model, resulting in an 8.457% and 1.1% reduction in total cost compared with the original parameters and parameters of sequential optimization, proving the effectiveness of the proposed method. Full article
(This article belongs to the Section Metal Failure Analysis)
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<p>Comparison of sequential and integrated optimization of structural and turning parameters: (<b>a</b>) flowchart of sequential optimization; (<b>b</b>) flowchart of integrated optimization.</p>
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<p>Schematic diagram of axle bridge structure.</p>
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<p>Axle bridge finite element mesh model.</p>
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<p>Nephograms of maximum stress and maximum deformation: (<b>a</b>) stress nephogram; (<b>b</b>) deformation nephogram.</p>
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<p>Fatigue life analysis of axle bridge: (<b>a</b>) fatigue damage nephogram; (<b>b</b>) fatigue life nephogram.</p>
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<p>Parametric modeling process of axle bridge.</p>
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<p>Process of AdvantEdge simulation.</p>
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<p>Design of experiments and optimization process.</p>
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<p>Numerical example.</p>
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<p>Comparison of LHS and OLHS: (<b>a</b>) Latin hypercube Sampling; (<b>b</b>) optimal Latin hypercube sampling.</p>
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<p>Integrated optimization process of axle bridge structure and turning processes.</p>
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<p>Nephogram of maximum stress and deformation: (<b>a</b>) maximum stress nephogram; (<b>b</b>) maximum deformation nephogram.</p>
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<p>Curve of cutting force for precision machining.</p>
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35 pages, 13439 KiB  
Article
The Application of UAVs in the Evaluation of Thermal Comfort Levels in Buildings Equipped with Internal Greenhouses
by Maria Inês Conceição, Eusébio Conceição, António Grilo, Meysam Basiri and Hazim Awbi
Clean Technol. 2023, 5(3), 1080-1114; https://doi.org/10.3390/cleantechnol5030055 - 20 Sep 2023
Viewed by 1808
Abstract
A greenhouse is used to improve thermal comfort (TC) levels for its occupants in winter conditions using solar radiation, which involves low energy consumption. The aim of this research is the application of unmanned aerial vehicles (UAVs) in the evaluation of thermal comfort [...] Read more.
A greenhouse is used to improve thermal comfort (TC) levels for its occupants in winter conditions using solar radiation, which involves low energy consumption. The aim of this research is the application of unmanned aerial vehicles (UAVs) in the evaluation of thermal comfort levels in buildings equipped with internal greenhouses. The new building design is developed numerically, and a building thermal simulator (BTS) numerical model calculates the indoor environmental variables. A new alternative and expeditious method to measure occupants’ comfort levels using UAV technology is applied using a UAV dynamic simulator (UAV DS). The evolution of the measured variables used for evaluating the predicted mean vote (PMV) is compared using the two numerical methodologies: BTS and UAV DS. In the second one, the mean radiant temperature (MRT) measuring methodology, the floor temperature, the lateral walls’ temperatures, the ceiling temperatures, and the air temperature are applied. In the method presented in this paper, a new building design is developed numerically, which includes a central greenhouse equipped with a semispherical dome, four auditoriums distributed around the central greenhouse, occupant distribution, and a ventilation methodology. The building geometry, the solar radiation on transparent surfaces, the TC, and the UAV mission methods are presented. The results show that, in general, the central greenhouse and the ventilation methodologies provide acceptable TC levels. The UAV monitoring mission, which includes two vehicles, provides good environmental variable replication, particularly when the environmental variables present greater variations. In the auditorium and greenhouse, the ceiling and lateral surface temperatures, respectively, can be used as an MRT approximation. The BTS numerical model is also important for developing buildings using renewable energy sources to improve the TC levels. Full article
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<p>View of the three-dimensional passive building equipped with a central greenhouse and four surrounding auditoriums. (<b>a</b>) 3D view, (<b>b</b>) lateral view, and (<b>c</b>) top view.</p>
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<p>Airflow rate (m<sup>3</sup>/s) used in the numerical simulation, in the morning (white) and the afternoon (orange), for the central space (6) and the surrounding auditoriums (2 to 5). X is the east direction, while Y is the north direction.</p>
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<p>System reference frames considered in the UAV DS (<b>a</b>) and measurement application example in the central greenhouse (<b>b</b>).</p>
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<p>Number of transparent surfaces considered in the central space: five levels in the dome (inclined gray surfaces) and one level in the greenhouse (vertical red surfaces). Space is divided into eight sections. X is associated with the east direction, while Y is associated with the north direction.</p>
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<p>Solar radiation of the transparent surfaces (from surface 1 to 45).</p>
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<p>Solar radiation of the transparent surfaces (from surface 46 to 105).</p>
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<p>Solar radiation of the transparent surfaces (from surface 106 to 150).</p>
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<p>Solar radiation of the transparent surfaces (from surface 151 to 210).</p>
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<p>Solar radiation of the transparent surfaces (from surface 211 to 255).</p>
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<p>Solar radiation of the transparent surfaces (from surface 256 to 315).</p>
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<p>Solar radiation of the transparent surfaces (from surface 316 to 360).</p>
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<p>Solar radiation of the transparent surfaces (from 361 to 420).</p>
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<p>Carbon dioxide concentration (CO<sub>2</sub>) from the numerical simulation for spaces 2 and 5 (<b>a</b>) as well as spaces 3 and 4 (<b>b</b>).</p>
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<p>Air temperature (Tair) from the numerical simulation.</p>
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<p>MRT of the surfaces during the numerical simulation.</p>
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<p>PMV during the numerical simulation.</p>
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<p>Total transmitted solar radiation. (<b>a</b>) Percentage of transmitted solar radiation in the different sections as a function of time in the greenhouse. (<b>b</b>) Total transmitted solar radiation in the different sections as a function of time in the greenhouse.</p>
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<p>South-east view of the three-dimensional passive building with a trajectory of the UAV in red color; (<b>a</b>) represents the UAV backward trajectory and (<b>b</b>) represents the UAV forward trajectory.</p>
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<p>Surface temperature measurement locations considering the floor, lateral walls, and ceiling surface temperature as representative for the MRT.</p>
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<p>Evolution of PMV in spaces 2 (<b>a</b>), 3 (<b>b</b>), 4 (<b>c</b>), 5 (<b>d</b>), and 6 (<b>e</b>) with BTS and UAV DS, according to approach B and four different methods.</p>
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<p>Evolution of PMV in spaces 2 (<b>a</b>), 3 (<b>b</b>), 4 (<b>c</b>), 5 (<b>d</b>), and 6 (<b>e</b>) with BTS and UAV DS, according to approach B and four different methods.</p>
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23 pages, 3315 KiB  
Article
A Novel AI Framework for PM Pollution Prediction Applied to a Greek Port City
by Fotios K. Anagnostopoulos, Spyros Rigas, Michalis Papachristou, Ioannis Chaniotis, Ioannis Anastasiou, Christos Tryfonopoulos and Paraskevi Raftopoulou
Atmosphere 2023, 14(9), 1413; https://doi.org/10.3390/atmos14091413 - 7 Sep 2023
Cited by 1 | Viewed by 2614
Abstract
Particulate matter (PM) pollution is a major global concern due to its negative impact on human health. To effectively address this issue, it is crucial to have a reliable and efficient forecasting system. In this study, we propose a framework for predicting particulate [...] Read more.
Particulate matter (PM) pollution is a major global concern due to its negative impact on human health. To effectively address this issue, it is crucial to have a reliable and efficient forecasting system. In this study, we propose a framework for predicting particulate matter concentrations by utilizing publicly available data from low-cost sensors and deep learning. We model the temporal variability through a novel Long Short-Term Memory Neural Network that offers a level of interpretability. The spatial dependence of particulate matter pollution in urban areas is modeled by incorporating characteristics of the urban agglomeration, namely, mean population density and mean floor area ratio. Our approach is general and scalable, as it can be applied to any type of sensor. Moreover, our framework allows for portable sensors, either mounted on vehicles or used by people. We demonstrate its effectiveness through a case study in Greece, where dense urban environments combined with low cost sensor networks is a peculiarity. Specifically, we consider Patras, a Greek port city, where the net PM pollution comes from a variety of sources, including traffic, port activity and domestic heating. Our model achieves a forecasting accuracy comparable to the resolution of the sensors and provides meaningful insights into the results. Full article
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<p>Histogram of concentration data points per PurpleAir PM sensor by sensor identifier (id) (<b>left</b>) and pie chart of the corresponding percentages (<b>right</b>).</p>
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<p>Meteorological (teal) and PM (yellow) sensors locations in Patras, Greece. The horizontal direction from left to right in the image points to the geographical north.</p>
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<p>Schematic representation of any recurrent network unrolled through time, where <math display="inline"><semantics> <msub> <mi mathvariant="bold">x</mi> <mi>t</mi> </msub> </semantics></math> and <math display="inline"><semantics> <msub> <mi mathvariant="bold">h</mi> <mi>t</mi> </msub> </semantics></math> are the input feature vector and hidden state vector at time step <span class="html-italic">t</span>, respectively.</p>
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<p>Averaged feature importance within 60 training runs for the two IMV-LSTM LSTM versions, namely, “full” and “tensor”, used in this work. A prediction window of 24 h and a look-back time window of 48 h were employed. The training parameters and results correspond to line 4 in <a href="#atmosphere-14-01413-t003" class="html-table">Table 3</a>.</p>
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<p>Model evaluation for daily predictions. The prediction window is 7 days and the “auto-regression” data correspond to the previous 7 days. The corresponding RMSE error is ∼18 and the MAE is ∼3. The predicted values are presented with red color, while the observations with blue.</p>
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<p>Feature importance assessment for three models after 25 runs. The corresponding training parameters and quality assessments are presented at <a href="#atmosphere-14-01413-t003" class="html-table">Table 3</a>, corresponding to the line numbers. (<b>Upper panel</b>): Daily prediction model, corresponding to a prediction window of 7 days (line 5). (<b>Middle panel</b>): Daily prediction model, corresponding to a prediction window of 10 days (line 6). (<b>Lower panel</b>): Hourly prediction model (line 3).</p>
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<p>Model evaluation for hourly predictions. The prediction window is 24 h and the “auto-regression” data correspond to the previous 24 h. The corresponding RMSE error is ∼20 and the MAE is ∼3. The predicted values are presented in red, while the real ones are presented in blue.</p>
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<p>The Mean Absolute Error per month and per particular sensor, normalized with the overall mean error, i.e., <math display="inline"><semantics> <mrow> <msub> <mi>σ</mi> <mrow> <mi>i</mi> <mi>j</mi> </mrow> </msub> <mo>/</mo> <msub> <mi>σ</mi> <mrow> <mi>m</mi> <mi>e</mi> <mi>a</mi> <mi>n</mi> </mrow> </msub> </mrow> </semantics></math>, where <span class="html-italic">i</span> runs in ids and <span class="html-italic">j</span> in months for the model numbered 3 in <a href="#atmosphere-14-01413-t003" class="html-table">Table 3</a>.</p>
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34 pages, 21809 KiB  
Article
Auxiliary Power Supply System with Parallel-Connected DC–AC Inverters for Low-Floor Light Rail Vehicle
by Paiwan Kerdtuad, Kunjana Chaiamarit and Supat Kittiratsatcha
Electronics 2023, 12(14), 3117; https://doi.org/10.3390/electronics12143117 - 18 Jul 2023
Viewed by 2940
Abstract
This research proposes a roof-mounted auxiliary power supply (APS) system for 600 VDC low-floor light rail vehicles (LRVs). The proposed APS system consists of five parallel-connected dc–ac inverter modules (modules 1–5). Inverter modules 1 and 2 are three-phase dc–ac inverters for the compressor [...] Read more.
This research proposes a roof-mounted auxiliary power supply (APS) system for 600 VDC low-floor light rail vehicles (LRVs). The proposed APS system consists of five parallel-connected dc–ac inverter modules (modules 1–5). Inverter modules 1 and 2 are three-phase dc–ac inverters for the compressor motors of the air conditioning system, and inverter modules 3 and 4 are three-phase dc–ac inverters for the air pump motors of the air supply system. Inverter module 5 is a single-phase dc–ac inverter for the 220 VAC power supply of onboard electric loads. Simulations and experiments were carried out under variable load torques and output frequencies for modules 1–4 and under full and no resistive loads for module 5. The measured total input current and total input power of the proposed APS system under the full-load condition are 114.36 A and 68.84 kW. The total efficiency of the proposed APS system (modules 1–5) is 97.05%. The proposed APS system is suitable for 600 VDC low-floor LRVs. The novelty of this research lies in the use of five parallel-connected inverter modules, as opposed to the three-phase output transformer or isolated dc–dc converter in the early and conventional APS systems. Specifically, the proposed APS system requires neither a three-phase output transformer nor an isolated dc–dc converter. Full article
(This article belongs to the Section Power Electronics)
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Figure 1
<p>The early APS system with three-phase output transformer for dc trains.</p>
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<p>The isolated dc–dc converter with high-frequency transformer of the conventional APS system for dc trains.</p>
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<p>The proposed APS system for 600 VDC low-floor light rail vehicles.</p>
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<p>The design of the low-floor LRV for the Khon Kaen light rail transit project.</p>
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<p>The 600 VDC overhead contact line for the proposed APS system of the low-floor LRV.</p>
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<p>Connecting diagram of the proposed APS system and onboard electric loads on the low-floor LRV.</p>
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<p>The schematic of temperature control in the passenger room of the LRV.</p>
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<p>The schematic of air pressure control of the air supply system of the LRV.</p>
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<p>Relationship between torque and speed of the VVVF control method of the compressor and air pump motors: (<b>a</b>) torque and speed; (<b>b</b>) stator voltage and frequency.</p>
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<p>Topology of three-phase two-level dc–ac inverter, the direction of phase currents (<math display="inline"><semantics><mrow><msub><mi>i</mi><mi>u</mi></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>i</mi><mi>v</mi></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>i</mi><mi>w</mi></msub></mrow></semantics></math>), and IGBT switches’ status in voltage vectors (<math display="inline"><semantics><mrow><msub><mi>v</mi><mn>0</mn></msub></mrow></semantics></math> -<math display="inline"><semantics><mrow><msub><mi>v</mi><mn>7</mn></msub></mrow></semantics></math>).</p>
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<p>The switching vectors for three-phase two-level dc–ac inverter (vectors <math display="inline"><semantics><mrow><msub><mi>v</mi><mn>0</mn></msub></mrow></semantics></math>–<math display="inline"><semantics><mrow><msub><mi>v</mi><mn>7</mn></msub></mrow></semantics></math>).</p>
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<p>Schematic of three-phase dc–ac inverters and control diagram of the compressor motors of the APS system.</p>
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<p>Schematic of three-phase dc–ac inverters and control diagram of the air pump motors of the APS system.</p>
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<p>Magnitude-control diagram of the single-phase power supply of the proposed APS system.</p>
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<p>The schematic of the proposed APS system for the low-floor LRV.</p>
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<p>The proposed APS system for low-floor LRV consisting of five inverter modules; (<b>a</b>) 3D model; (<b>b</b>) APS system prototype.</p>
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<p>The proposed APS system for low-floor LRV with metal castings and electrical enclosures as per IP65 code: (<b>a</b>) 3D model; (<b>b</b>) APS system prototype with metal castings.</p>
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<p>The experimental setup of the proposed APS system: (<b>a</b>) 600 VDC power supply, APS system, resistive load, and 24 VDC battery; (<b>b</b>) simulated loads #1–#4.</p>
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<p>The schematic of the proposed APS system with the simulated loads.</p>
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<p>The waveforms of the three-phase dc–ac inverters for the compressor motors (modules 1 and 2): (<b>a</b>) simulated <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mi>D</mi><mi>C</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>1</mn><mi>u</mi><mo>−</mo><mi>v</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>1</mn><mi>v</mi><mo>−</mo><mi>w</mi></mrow></msub></mrow></semantics></math>, and <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>1</mn><mi>w</mi><mo>−</mo><mi>u</mi></mrow></msub></mrow></semantics></math>; (<b>b</b>) simulated <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mi>D</mi><mi>C</mi><mn>1</mn></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>1</mn><mi>u</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>1</mn><mi>v</mi></mrow></msub></mrow></semantics></math>, and <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>1</mn><mi>w</mi></mrow></msub></mrow></semantics></math>; (<b>c</b>) measured <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mi>D</mi><mi>C</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>1</mn><mi>u</mi><mo>−</mo><mi>v</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>1</mn><mi>v</mi><mo>−</mo><mi>w</mi></mrow></msub></mrow></semantics></math>, and <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>1</mn><mi>w</mi><mo>−</mo><mi>u</mi></mrow></msub></mrow></semantics></math>; (<b>d</b>) measured <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mi>D</mi><mi>C</mi><mn>1</mn></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>1</mn><mi>u</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>1</mn><mi>v</mi></mrow></msub></mrow></semantics></math>, and <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>1</mn><mi>w</mi></mrow></msub></mrow></semantics></math>; given that <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mi>D</mi><mi>C</mi></mrow></msub></mrow></semantics></math> = 600 V, <math display="inline"><semantics><mrow><msub><mi>f</mi><mi>s</mi></msub></mrow></semantics></math> = 50 Hz, and load torque = 100%.</p>
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<p>The waveforms of the three-phase dc–ac inverters for the compressor motors (modules 1 and 2): (<b>a</b>) simulated <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mi>D</mi><mi>C</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>1</mn><mi>u</mi><mo>−</mo><mi>v</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>1</mn><mi>v</mi><mo>−</mo><mi>w</mi></mrow></msub></mrow></semantics></math>, and <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>1</mn><mi>w</mi><mo>−</mo><mi>u</mi></mrow></msub></mrow></semantics></math>; (<b>b</b>) simulated <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mi>D</mi><mi>C</mi><mn>1</mn></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>1</mn><mi>u</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>1</mn><mi>v</mi></mrow></msub></mrow></semantics></math>, and <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>1</mn><mi>w</mi></mrow></msub></mrow></semantics></math>; (<b>c</b>) measured <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mi>D</mi><mi>C</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>1</mn><mi>u</mi><mo>−</mo><mi>v</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>1</mn><mi>v</mi><mo>−</mo><mi>w</mi></mrow></msub></mrow></semantics></math>, and <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>1</mn><mi>w</mi><mo>−</mo><mi>u</mi></mrow></msub></mrow></semantics></math>; (<b>d</b>) measured <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mi>D</mi><mi>C</mi><mn>1</mn></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>1</mn><mi>u</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>1</mn><mi>v</mi></mrow></msub></mrow></semantics></math>, and <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>1</mn><mi>w</mi></mrow></msub></mrow></semantics></math>; given that <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mi>D</mi><mi>C</mi></mrow></msub></mrow></semantics></math> = 600 V, <math display="inline"><semantics><mrow><msub><mi>f</mi><mi>s</mi></msub></mrow></semantics></math> = 50 Hz, and load torque = 75%.</p>
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<p>The waveforms of the three-phase dc–ac inverters for the compressor motors (modules 1 and 2): (<b>a</b>) simulated <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mi>D</mi><mi>C</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>1</mn><mi>u</mi><mo>−</mo><mi>v</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>1</mn><mi>v</mi><mo>−</mo><mi>w</mi></mrow></msub></mrow></semantics></math>, and <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>1</mn><mi>w</mi><mo>−</mo><mi>u</mi></mrow></msub></mrow></semantics></math>; (<b>b</b>) simulated <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mi>D</mi><mi>C</mi><mn>1</mn></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>1</mn><mi>u</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>1</mn><mi>v</mi></mrow></msub></mrow></semantics></math>, and <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>1</mn><mi>w</mi></mrow></msub></mrow></semantics></math>; (<b>c</b>) measured <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mi>D</mi><mi>C</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>1</mn><mi>u</mi><mo>−</mo><mi>v</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>1</mn><mi>v</mi><mo>−</mo><mi>w</mi></mrow></msub></mrow></semantics></math>, and <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>1</mn><mi>w</mi><mo>−</mo><mi>u</mi></mrow></msub></mrow></semantics></math>; (<b>d</b>) measured <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mi>D</mi><mi>C</mi><mn>1</mn></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>1</mn><mi>u</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>1</mn><mi>v</mi></mrow></msub></mrow></semantics></math>, and <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>1</mn><mi>w</mi></mrow></msub></mrow></semantics></math>; given that <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mi>D</mi><mi>C</mi></mrow></msub></mrow></semantics></math> = 600 V, <math display="inline"><semantics><mrow><msub><mi>f</mi><mi>s</mi></msub></mrow></semantics></math> = 50 Hz, and load torque = 75%.</p>
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<p>The waveforms of the three-phase dc–ac inverters for the compressor motors (modules 1 and 2): (<b>a</b>) simulated <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mi>D</mi><mi>C</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>1</mn><mi>u</mi><mo>−</mo><mi>v</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>1</mn><mi>v</mi><mo>−</mo><mi>w</mi></mrow></msub></mrow></semantics></math>, and <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>1</mn><mi>w</mi><mo>−</mo><mi>u</mi></mrow></msub></mrow></semantics></math>; (<b>b</b>) simulated <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mi>D</mi><mi>C</mi><mn>1</mn></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>1</mn><mi>u</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>1</mn><mi>v</mi></mrow></msub></mrow></semantics></math>, and <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>1</mn><mi>w</mi></mrow></msub></mrow></semantics></math>; (<b>c</b>) measured <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mi>D</mi><mi>C</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>1</mn><mi>u</mi><mo>−</mo><mi>v</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>1</mn><mi>v</mi><mo>−</mo><mi>w</mi></mrow></msub></mrow></semantics></math>, and <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>1</mn><mi>w</mi><mo>−</mo><mi>u</mi></mrow></msub></mrow></semantics></math>; (<b>d</b>) measured <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mi>D</mi><mi>C</mi><mn>1</mn></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>1</mn><mi>u</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>1</mn><mi>v</mi></mrow></msub></mrow></semantics></math>, and <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>1</mn><mi>w</mi></mrow></msub></mrow></semantics></math>; given that <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mi>D</mi><mi>C</mi></mrow></msub></mrow></semantics></math> = 600 V, <math display="inline"><semantics><mrow><msub><mi>f</mi><mi>s</mi></msub></mrow></semantics></math> = 50 Hz, and load torque = 50%.</p>
Full article ">Figure 23
<p>The waveforms of the three-phase dc–ac inverters for the compressor motors (modules 1 and 2): (<b>a</b>) simulated <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mi>D</mi><mi>C</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>1</mn><mi>u</mi><mo>−</mo><mi>v</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>1</mn><mi>v</mi><mo>−</mo><mi>w</mi></mrow></msub></mrow></semantics></math>, and <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>1</mn><mi>w</mi><mo>−</mo><mi>u</mi></mrow></msub></mrow></semantics></math>; (<b>b</b>) simulated <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mi>D</mi><mi>C</mi><mn>1</mn></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>1</mn><mi>u</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>1</mn><mi>v</mi></mrow></msub></mrow></semantics></math>, and <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>1</mn><mi>w</mi></mrow></msub></mrow></semantics></math>; (<b>c</b>) measured <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mi>D</mi><mi>C</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>1</mn><mi>u</mi><mo>−</mo><mi>v</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>1</mn><mi>v</mi><mo>−</mo><mi>w</mi></mrow></msub></mrow></semantics></math>, and <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>1</mn><mi>w</mi><mo>−</mo><mi>u</mi></mrow></msub></mrow></semantics></math>; (<b>d</b>) measured <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mi>D</mi><mi>C</mi><mn>1</mn></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>1</mn><mi>u</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>1</mn><mi>v</mi></mrow></msub></mrow></semantics></math>, and <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>1</mn><mi>w</mi></mrow></msub></mrow></semantics></math>; given that <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mi>D</mi><mi>C</mi></mrow></msub></mrow></semantics></math> = 600 V, <math display="inline"><semantics><mrow><msub><mi>f</mi><mi>s</mi></msub></mrow></semantics></math> = 50 Hz, and load torque = 25%.</p>
Full article ">Figure 24
<p>The measured results of the three-phase dc–ac inverter for the compressor motors (i.e., module 1) under variable load torques (25–100%) and output frequencies (10–50 Hz): (<b>a</b>) dc input current (<math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mi>D</mi><mi>C</mi><mn>1</mn></mrow></msub></mrow></semantics></math>); (<b>b</b>) dc input power (<math display="inline"><semantics><mrow><msub><mi>P</mi><mrow><mi>D</mi><mi>C</mi><mn>1</mn></mrow></msub></mrow></semantics></math> ).</p>
Full article ">Figure 25
<p>The measured results of the three-phase dc–ac inverter for the compressor motors (i.e., modules 1 and 2) under variable load torques (25–100%) and output frequencies (10–50 Hz): (<b>a</b>) dc input current (<math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mi>D</mi><mi>C</mi><mn>1</mn></mrow></msub></mrow></semantics></math> + <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mi>D</mi><mi>C</mi><mn>2</mn></mrow></msub></mrow></semantics></math> ); (<b>b</b>) dc input power (<math display="inline"><semantics><mrow><msub><mi>P</mi><mrow><mi>D</mi><mi>C</mi><mn>1</mn></mrow></msub></mrow></semantics></math> + <math display="inline"><semantics><mrow><msub><mi>P</mi><mrow><mi>D</mi><mi>C</mi><mn>2</mn></mrow></msub></mrow></semantics></math> ).</p>
Full article ">Figure 26
<p>The waveforms of the three-phase dc–ac inverter for the air pump motors (modules 3 and 4): (<b>a</b>) simulated <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mi>D</mi><mi>C</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>3</mn><mi>u</mi><mo>−</mo><mi>v</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>3</mn><mi>v</mi><mo>−</mo><mi>w</mi></mrow></msub></mrow></semantics></math>, and <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mi>w</mi><mo>−</mo><mi>u</mi></mrow></msub></mrow></semantics></math>; (<b>b</b>) simulated <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mi>D</mi><mi>C</mi><mn>3</mn></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>3</mn><mi>u</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>3</mn><mi>v</mi></mrow></msub></mrow></semantics></math>, and <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>3</mn><mi>w</mi></mrow></msub></mrow></semantics></math>; (<b>c</b>) measured <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mi>D</mi><mi>C</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>3</mn><mi>u</mi><mo>−</mo><mi>v</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>3</mn><mi>v</mi><mo>−</mo><mi>w</mi></mrow></msub></mrow></semantics></math>, and <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mi>w</mi><mo>−</mo><mi>u</mi></mrow></msub></mrow></semantics></math>; (<b>d</b>) measured <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mi>D</mi><mi>C</mi><mn>3</mn></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>3</mn><mi>u</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>3</mn><mi>v</mi></mrow></msub></mrow></semantics></math>, and <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>3</mn><mi>w</mi></mrow></msub></mrow></semantics></math>; given that <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mi>D</mi><mi>C</mi></mrow></msub></mrow></semantics></math> = 600 V, <math display="inline"><semantics><mrow><msub><mi>f</mi><mi>s</mi></msub></mrow></semantics></math> = 50 Hz, and load torque = 100%.</p>
Full article ">Figure 27
<p>The waveforms of the three-phase dc–ac inverter for the air pump motors (modules 3 and 4): (<b>a</b>) simulated <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mi>D</mi><mi>C</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>3</mn><mi>u</mi><mo>−</mo><mi>v</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>3</mn><mi>v</mi><mo>−</mo><mi>w</mi></mrow></msub></mrow></semantics></math>, and <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mi>w</mi><mo>−</mo><mi>u</mi></mrow></msub></mrow></semantics></math>; (<b>b</b>) simulated <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mi>D</mi><mi>C</mi><mn>3</mn></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>3</mn><mi>u</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>3</mn><mi>v</mi></mrow></msub></mrow></semantics></math>, and <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>3</mn><mi>w</mi></mrow></msub></mrow></semantics></math>; (<b>c</b>) measured <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mi>D</mi><mi>C</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>3</mn><mi>u</mi><mo>−</mo><mi>v</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>3</mn><mi>v</mi><mo>−</mo><mi>w</mi></mrow></msub></mrow></semantics></math>, and <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mi>w</mi><mo>−</mo><mi>u</mi></mrow></msub></mrow></semantics></math>; (<b>d</b>) measured <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mi>D</mi><mi>C</mi><mn>3</mn></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>3</mn><mi>u</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>3</mn><mi>v</mi></mrow></msub></mrow></semantics></math>, and <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>3</mn><mi>w</mi></mrow></msub></mrow></semantics></math>; given that <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mi>D</mi><mi>C</mi></mrow></msub></mrow></semantics></math> = 600 V, <math display="inline"><semantics><mrow><msub><mi>f</mi><mi>s</mi></msub></mrow></semantics></math> = 50 Hz, and load torque = 75%.</p>
Full article ">Figure 28
<p>The waveforms of the three-phase dc–ac inverter for the air pump motors (modules 3 and 4): (<b>a</b>) simulated <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mi>D</mi><mi>C</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>3</mn><mi>u</mi><mo>−</mo><mi>v</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>3</mn><mi>v</mi><mo>−</mo><mi>w</mi></mrow></msub></mrow></semantics></math>, and <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mi>w</mi><mo>−</mo><mi>u</mi></mrow></msub></mrow></semantics></math>; (<b>b</b>) simulated <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mi>D</mi><mi>C</mi><mn>3</mn></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>3</mn><mi>u</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>3</mn><mi>v</mi></mrow></msub></mrow></semantics></math>, and <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>3</mn><mi>w</mi></mrow></msub></mrow></semantics></math>; (<b>c</b>) measured <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mi>D</mi><mi>C</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>3</mn><mi>u</mi><mo>−</mo><mi>v</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>3</mn><mi>v</mi><mo>−</mo><mi>w</mi></mrow></msub></mrow></semantics></math>, and <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mi>w</mi><mo>−</mo><mi>u</mi></mrow></msub></mrow></semantics></math>; (<b>d</b>) measured <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mi>D</mi><mi>C</mi><mn>3</mn></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mi>D</mi><mi>C</mi><mn>3</mn></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>3</mn><mi>v</mi></mrow></msub></mrow></semantics></math>, and <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>3</mn><mi>w</mi></mrow></msub></mrow></semantics></math>; given that <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mi>D</mi><mi>C</mi></mrow></msub></mrow></semantics></math> = 600 V, <math display="inline"><semantics><mrow><msub><mi>f</mi><mi>s</mi></msub></mrow></semantics></math> = 50 Hz, and load torque = 50%.</p>
Full article ">Figure 29
<p>The waveforms of the three-phase dc–ac inverter for the air pump motors (modules 3 and 4): (<b>a</b>) simulated <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mi>D</mi><mi>C</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>3</mn><mi>u</mi><mo>−</mo><mi>v</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>3</mn><mi>v</mi><mo>−</mo><mi>w</mi></mrow></msub></mrow></semantics></math>, and <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mi>w</mi><mo>−</mo><mi>u</mi></mrow></msub></mrow></semantics></math>; (<b>b</b>) simulated <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mi>D</mi><mi>C</mi><mn>3</mn></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>3</mn><mi>u</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>3</mn><mi>v</mi></mrow></msub></mrow></semantics></math>, and <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>3</mn><mi>w</mi></mrow></msub></mrow></semantics></math>; (<b>c</b>) measured <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mi>D</mi><mi>C</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>3</mn><mi>u</mi><mo>−</mo><mi>v</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>3</mn><mi>v</mi><mo>−</mo><mi>w</mi></mrow></msub></mrow></semantics></math>, and <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mi>w</mi><mo>−</mo><mi>u</mi></mrow></msub></mrow></semantics></math>; (<b>d</b>) measured <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mi>D</mi><mi>C</mi><mn>3</mn></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>3</mn><mi>u</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>3</mn><mi>v</mi></mrow></msub></mrow></semantics></math>, and <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>3</mn><mi>w</mi></mrow></msub></mrow></semantics></math>; given that <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mi>D</mi><mi>C</mi></mrow></msub></mrow></semantics></math> = 600 V, <math display="inline"><semantics><mrow><msub><mi>f</mi><mi>s</mi></msub></mrow></semantics></math> = 50 Hz, and load torque = 25%.</p>
Full article ">Figure 30
<p>The measured results of the three-phase dc–ac inverter for the air pump motors (i.e., module 3) under variable load torques (25–100%) and output frequencies (10–50 Hz): (<b>a</b>) dc input current (<math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mi>D</mi><mi>C</mi><mn>3</mn></mrow></msub></mrow></semantics></math>); (<b>b</b>) dc input power (<math display="inline"><semantics><mrow><msub><mi>P</mi><mrow><mi>D</mi><mi>C</mi><mn>3</mn></mrow></msub></mrow></semantics></math> ).</p>
Full article ">Figure 31
<p>The measured results of the three-phase dc–ac inverter for the air pump motors (i.e., modules 3 and 4) under variable load torques (25–100%) and output frequencies (10–50 Hz): (<b>a</b>) dc input current (<math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mi>D</mi><mi>C</mi><mn>3</mn></mrow></msub></mrow></semantics></math>+<math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mi>D</mi><mi>C</mi><mn>4</mn></mrow></msub></mrow></semantics></math> ); (<b>b</b>) dc input power (<math display="inline"><semantics><mrow><msub><mi>P</mi><mrow><mi>D</mi><mi>C</mi><mn>3</mn></mrow></msub></mrow></semantics></math> +<math display="inline"><semantics><mrow><msub><mi>P</mi><mrow><mi>D</mi><mi>C</mi><mn>4</mn></mrow></msub></mrow></semantics></math> ).</p>
Full article ">Figure 32
<p>The <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mi>D</mi><mi>C</mi></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mi>D</mi><mi>C</mi><mn>5</mn></mrow></msub></mrow></semantics></math>, <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mn>5</mn><mi>s</mi></mrow></msub></mrow></semantics></math>, and <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mn>5</mn><mi>s</mi></mrow></msub></mrow></semantics></math> waveforms of the dc–ac inverter for the single-phase power supply (module 5) given that <math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mi>D</mi><mi>C</mi></mrow></msub></mrow></semantics></math> = 600 VDC and <math display="inline"><semantics><mrow><msub><mi>f</mi><mi>s</mi></msub></mrow></semantics></math> = 50 Hz: (<b>a</b>) full load (simulated; resistive load = 100%); (<b>b</b>) full load (measured); (<b>c</b>) no load (simulated; resistive load = 0%); and (<b>d</b>) no load (measured).</p>
Full article ">Figure 33
<p>The measured total input current of the dc–ac inverters for compressor motors and air pump motors (modules 1–4; <math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mi>D</mi><mi>C</mi><mn>1</mn></mrow></msub></mrow></semantics></math>-<math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mi>D</mi><mi>C</mi><mn>4</mn></mrow></msub></mrow></semantics></math> ) under variable load torques (25–100%) and output frequencies (10–50 Hz), given the overhead contact line voltage (<math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mi>D</mi><mi>C</mi></mrow></msub></mrow></semantics></math> ) of 600 V.</p>
Full article ">Figure 34
<p>The measured total input power of the dc–ac inverters for compressor motors and air pump motors (modules 1–4; <math display="inline"><semantics><mrow><msub><mi>P</mi><mrow><mi>D</mi><mi>C</mi><mn>1</mn></mrow></msub></mrow></semantics></math>-<math display="inline"><semantics><mrow><msub><mi>P</mi><mrow><mi>D</mi><mi>C</mi><mn>4</mn></mrow></msub></mrow></semantics></math> ) under variable load torques (25–100%) and output frequencies (10–50 Hz), given the overhead contact line voltage (<math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mi>D</mi><mi>C</mi></mrow></msub></mrow></semantics></math> ) of 600 V.</p>
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<p>The measured total input current of the dc–ac inverters modules 1–5 (<math display="inline"><semantics><mrow><msub><mi>i</mi><mrow><mi>D</mi><mi>C</mi><mi>T</mi></mrow></msub></mrow></semantics></math>) under variable load torques (25–100%) and output frequencies (10–50 Hz) for modules 1–4 and a resistive load of 100% and output frequency of 50 Hz for module 5, given the overhead contact line voltage (<math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mi>D</mi><mi>C</mi></mrow></msub></mrow></semantics></math> ) of 600 V.</p>
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<p>The measured total input power of the dc–ac inverters modules 1–5 (<math display="inline"><semantics><mrow><msub><mi>P</mi><mrow><mi>D</mi><mi>C</mi><mi>T</mi></mrow></msub></mrow></semantics></math>) under variable load torques (25–100%) and output frequencies (10–50 Hz) for modules 1–4 and a resistive load of 100% and output frequency of 50 Hz for module 5, given the overhead contact line voltage (<math display="inline"><semantics><mrow><msub><mi>v</mi><mrow><mi>D</mi><mi>C</mi></mrow></msub></mrow></semantics></math> ) of 600 V.</p>
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<p>The 600 VDC low-floor LRV with the proposed APS system mounted on the rooftop of car no. 2.</p>
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<p>Low-floor light rail vehicle with the roof-mounted APS system.</p>
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18 pages, 12059 KiB  
Article
Indirect Assessment of Railway Infrastructure Anomalies Based on Passenger Comfort Criteria
by Patricia Silva, Diogo Ribeiro, Pedro Pratas, Joaquim Mendes and Eurico Seabra
Appl. Sci. 2023, 13(10), 6150; https://doi.org/10.3390/app13106150 - 17 May 2023
Viewed by 1607
Abstract
Railways are among the most efficient and widely used mass transportation systems for mid-range distances. To enhance the attractiveness of this type of transport, it is necessary to improve the level of comfort, which is much influenced by the vibration derived from the [...] Read more.
Railways are among the most efficient and widely used mass transportation systems for mid-range distances. To enhance the attractiveness of this type of transport, it is necessary to improve the level of comfort, which is much influenced by the vibration derived from the train motion and wheel-track interaction; thus, railway track infrastructure conditions and maintenance are a major concern. Based on discomfort levels, a methodology capable of detecting railway track infrastructure failures is proposed. During regular passenger service, acceleration and GPS measurements were taken on Alfa Pendular and Intercity trains between Porto (Campanhã) and Lisbon (Oriente) stations. ISO 2631 methodology was used to calculate instantaneous floor discomfort levels. By matching the results for both trains, using GPS coordinates, 12 track section locations were found to require preventive maintenance actions. The methodology was validated by comparing these results with those obtained by the EM 120 track inspection vehicle, for which similar locations were found. The developed system is a complementary condition-based maintenance tool that presents the advantage of being low-cost while not disturbing regular train operations. Full article
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<p>Schematic illustration of railway ballasted infrastructure.</p>
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<p>Typical rail surface faults and EN 13848 track geometry evaluation wavelengths and those capable of affecting passengers’ comfort.</p>
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<p>Detection of rail irregularities based on acceleration measurements (adapted from [<a href="#B35-applsci-13-06150" class="html-bibr">35</a>]).</p>
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<p>AP train bogie: (<b>a</b>) primary suspension; (<b>b</b>) secondary suspension.</p>
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<p>IC bogie: (<b>a</b>) primary suspension; (<b>b</b>) secondary suspension.</p>
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<p>Data acquisition system: (<b>a</b>) 3-axial accelerometer pad; (<b>b</b>) GPS system.</p>
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<p>Experimented vehicles: (<b>a</b>) AP train; (<b>b</b>) IC train.</p>
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<p>Experimented vehicles: (<b>a</b>) AP train; (<b>b</b>) IC train.</p>
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<p>Developed methodology illustration.</p>
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<p>Floor measurement locations: (<b>a</b>) AP train and car measurement locations; (<b>b</b>) IC train and car measurement locations; (<b>c</b>) accelerometer placement on AP (left side) and IC (right side) trains.</p>
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<p>Floor measurement locations: (<b>a</b>) AP train and car measurement locations; (<b>b</b>) IC train and car measurement locations; (<b>c</b>) accelerometer placement on AP (left side) and IC (right side) trains.</p>
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<p>EM 120 track inspection vehicle from IP (adapted from [<a href="#B57-applsci-13-06150" class="html-bibr">57</a>]).</p>
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<p>Instantaneous floor discomfort levels for AP and IC trains (where the red mark identifies a railway track infrastructure abnormality).</p>
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<p>Nothern Line railway track infrastructure maintenance needs identification; detailed zones (left side and right side) are at the laterals.</p>
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35 pages, 145940 KiB  
Article
Multidiscipline Design Optimization for Large-Scale Complex Nonlinear Dynamic System Based on Weak Coupling Interfaces
by Wei Du, Si-Yang Piao, Ming-Wei Piao, Chun-Ge Nie, Peng Dang, Qiu-Ze Li and Yi-Nan Tao
Appl. Sci. 2023, 13(9), 5532; https://doi.org/10.3390/app13095532 - 29 Apr 2023
Viewed by 1898
Abstract
For high-tech manufacturing industries, developing large-scale complex nonlinear dynamic systems must be taken as one of the basic works, formulating problems to be solved, steering system design in a more preferable direction, and making correct strategic decisions. By using effective tools of big [...] Read more.
For high-tech manufacturing industries, developing large-scale complex nonlinear dynamic systems must be taken as one of the basic works, formulating problems to be solved, steering system design in a more preferable direction, and making correct strategic decisions. By using effective tools of big data mining, Dynamic Design Methodology was proposed to establish a technical platform for Multidiscipline Design Optimization such as High-Speed Rolling Stock, including three key technologies: analysis graph of full-vehicle stability properties and variation patterns, improved transaction strategy of flexible body to MBS interface, seamless collaboration with weldline fatigue damage assessments through correct Modal Stress Recovery. By applying the above methodology, a self-adaptive improved solution was formulated with optimal parameter configuration, which is one of the more favorable options for higher-speed bogies. While within a velocity (140–200) km/h at λe < 0.10, car body instability’s influence on ride comfort can be easily improved by using a semi-active vibration reduction technique between inter-vehicles through outer windshields. Comprehensive evaluations show that only under rational conditions of wheel-rail matching, i.e., 0.10 ≥ λeN > λemin and λemin = (0.03–0.06), can this low-cost solution achieve the three goals of low track conicity, optimal route planning, and investment benefit maximization. So, rail vehicle experts are necessary to collaborate and innovate intensively with passenger transportation and steel rail ones. Specifically, by adopting rail grinding treatment, occurrence probability is controlled at 85% and 5% for track conicity of (0.03–0.10) and (0.25–0.35). By optimizing routing planning, operating across dedicated lines of different speed grades can achieve self-cleaning of central hollow tread wear over time. According to the inherent rigid-flex coupling relationship, geometric nonlinearities of worn wheel-rail contact should be avoided as much as possible for HSR practices. Only under weak coupling interfaces in the floor frame can the structural integrity of an aluminum alloy car body be ensured. Full article
(This article belongs to the Section Mechanical Engineering)
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Figure 1
<p>Longitudinal and vertical coupling relationship between running gear and service car body formulated by a mono-bar traction device under influences of wheelset dynamic imbalance. (<b>a</b>) Longitudinal and vertical coupling relationship formulated by mono-bar traction device when the service car body is regarded as a slender beam. (<b>b</b>) Reciprocating longitudinal oscillations of front and rear bogies force traction converter in the equipment cabin under floor frame to occasionally produce vertical coupling resonance. (<b>c</b>) Mono-bar traction device. (<b>d</b>) Traction stiffness curve, equivalent stiffness of which is ca. (8.0–8.5) MN/m per bogie. (<b>e</b>) Traction converter installation hanging frame was cracked thereby. (<b>f</b>) DVA damping technique is implemented incorrectly by using rubber hanging elements, and strong coupling interface to floor frame is then formed.</p>
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<p>Flow chart of large-scale MDO such as HSRS by using dynamic design methodology.</p>
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<p>Influences of track parameters on low wear area of wheel-rail contact and detrimental wear evolution. (<b>a</b>) Two-point contact problem on rail shoulder at one side of gauge corner such as flange root and side wear. (<b>b</b>) Comparison of three typical wheel-rail matching situations for contact point variation on railhead. (<b>c</b>) Two-point contact problem on railhead top with stronger dynamic interaction such as central hollow tread wear in Chinese HSR practices. (<b>d</b>) Comparison of RRD curves for three typical wheel-rail matching situations.</p>
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<p>Primary hunting design default of German ICE3 series bogies prototype and associated negative influences feedback to creepage and wear of corresponding wheels. (<b>a</b>) Template model of ICE3 motor bogies and associated components. (<b>b</b>) Analysis graph of motor vehicle stability properties and variation patterns under the following configuration, i.e., Four ZF Sachs T60 anti-yaw dampers per bogie and radial stiffness of 70 MN/m for both end rubber joints. (<b>c</b>) Analysis graph of motor vehicle stability properties and variation patterns under the following configuration, i.e., Four ZF Sachs T70 anti-yaw dampers per bogie and radial stiffness of 25 MN/m for both end rubber joints. (<b>d</b>) Irrational condition of wheel-rail matching. (<b>e</b>) RCF failure or plastic flow on rail shoulder at one side of gauge corner. (<b>f</b>) Central hollow tread wear under ZF Sachs T60 configuration. (<b>g</b>) Hollow tread wear with dual light band under ZF Sachs T70 configuration. Both tread wear characteristics (<b>f</b>,<b>g</b>) are related to thin flange re-profiling.</p>
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<p>Diagram of anti-roll torsion bar device: (<b>a</b>) Anti-roll torsion bar device with fixed simply supported on bolster; (<b>b</b>) Anti-roll torsion bar device with floating simply supported on bolster.</p>
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<p>Tracking test and measuring results of first fluttering phenomenon produced in service car body when running from Dalian to Harbin. (<b>a</b>) Acceleration measured at hanging points of HP (1–4). (<b>b</b>) HP arrangement of traction converter with dual cooling units (ca.6.6 t). (<b>c</b>) Equipments hanged with side beams in floor frame; (<b>d</b>) Conic rubber hanger with bolt pre-tightening for <span class="html-italic">m</span> ≤ 1250 kg. (<b>e</b>) Wedge rubber hangers with pre-tightening by self-weight for <span class="html-italic">m</span>&gt;1250 kg. (<b>f</b>) Stationary acceleration time history of traction converter hanged under floor frame. (<b>g</b>) Critical acceleration time history with two fluttering phenomena; (<b>h</b>) Nonstationary time history with lateral reciprocating motions of traction converter.</p>
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<p>Rigid-flexible coupling simulation model formulation of trailer TC02/07 based on optical fiber test and analysis results of three acceleration PSD contrast for hanging traction converter, as seen in <a href="#applsci-13-05532-f006" class="html-fig">Figure 6</a>f–h, including starting section I from stationary acceleration time history (<b>a</b>), starting section II from critical acceleration time history (<b>b</b>)and stable section III from critical acceleration time history (<b>c</b>); And two acceleration PSD contrast (<b>d</b>,<b>e</b>) for side beams in floor frame corresponding to (<b>a</b>,<b>b</b>). Between aluminum alloy car body and the external equipments, two main interfaces are constituted with roof interface (<b>f</b>) and floor frame interface (<b>g</b>), and rigid-flex coupling model of trailer TC 02/07 (<b>h</b>) formulated with weak coupling interface of floor frame so as to ensure 30-year service life.</p>
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<p>Formulations of strong coupling interface under floor frame of service car body after replacing with new rubber hanging elements. (<b>a</b>) New V-type rubber hanging elements for traction converter. (<b>b</b>) New Conic rubber hanging elements for traction transformer, toilet collection, etc. (<b>c</b>) Lateral acceleration of traction converter exceeds limit specified in IEC61373–2010 when running speed of (420–480) km/h in tangent line at <span class="html-italic">λ<sub>e</sub></span> = 0.10. (<b>d</b>) Lateral acceleration exceeds limit again when running speed of (380–420) km/h in tangent line with slight central hollow tread wear. Considering strong coupling interface formulated under floor frame, central rhombus modal frequency of service car body is then increased slightly from inherent 8.66 Hz to 9.71 Hz due to corresponding master-slave node constraints (<b>e</b>,<b>f</b>), by which lateral coupling relationship is established with acceleration response of bogie frame lateral vibration, causing traction converter to occasionally generate internal coupling resonance. Meanwhile, 1st lateral bending modal frequency of service car body is then decreased from inherent 17.98 Hz to 14.85 Hz due to generalized mass increase (<b>g</b>,<b>h</b>).</p>
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<p>Lateral coupling resonances in equipment cabin under floor frame and associated influences on fatigue damage of aluminum alloy car body. (<b>a</b>) Rhombus modal coupling resonance in middle of service car body is accompanied by roof twisted modal vibration, ca. 17.40 Hz. (<b>b</b>) Crescent notch effect on one side of pantograph fairing and associated influences on fatigue damage at both ends of transverse weldline. (<b>c</b>) Relationship curve of vehicle speed influence on fatigue life at both ends of transverse weldline, in which roof is twisted and resonant when 450 km/h, and stronger resonance occurs again when 650 km/h. (<b>d</b>–<b>f</b>) Lateral and vertical vibrations of pantograph fairing and associated influences on fatigue life at both ends of transverse weldline when speed of (300–550) km/h. (<b>g</b>–<b>i</b>) Lateral and vertical vibrations of pantograph fairing and associated influences on fatigue life at both ends of transverse weldline when speed of (450–650) km/h.</p>
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<p>Analysis graphs of stability properties and variation patterns for self-adaptive higher-speed bogie with anti-rolling torsion bar devices (in-) active. (<b>a</b>) When <span class="html-italic">λ<sub>e</sub></span> = 0.08–0.35 with anti-rolling torsion bar devices active. (<b>b</b>) When <span class="html-italic">λ<sub>e</sub></span> = 0.08–0.16 with anti-rolling torsion bar devices active. (<b>c</b>) When <span class="html-italic">λ<sub>e</sub></span> = 0.20–0.35 with anti-rolling torsion bar devices active. (<b>d</b>) When <span class="html-italic">λ<sub>e</sub></span> = 0.08–0.35 with anti-rolling torsion bar devices inactive. (<b>e</b>) When <span class="html-italic">λ<sub>e</sub></span> = 0.08–0.15 with anti-rolling torsion bar devices inactive. (<b>f</b>) When <span class="html-italic">λ<sub>e</sub></span> = 0.20–0.35 with anti-rolling torsion bar devices inactive.</p>
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<p>Semi-active damping solutions between inter-vehicles and associated technical implementation. (<b>a</b>) Motor-trailer-motor trainset with relevant parameters. (<b>b</b>) Cracks occur on lower part of outer windshield at both sides. (<b>c</b>) Semi-active damping implementation with stiffness and damping in lateral and vertical directions per constraint point. (<b>d</b>) Principles of pneumatic technique when activated or inactivated.</p>
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<p>Safety and stability assessments of self-adaptive improved motor and trailer vehicles. (<b>a</b>,<b>b</b>) Evaluations of safe speed space of motor vehicle and associated lateral acceleration of bogie frame based on UIC518 or EN14363. (<b>c</b>,<b>d</b>) Evaluations of safe speed space of trailer vehicle and associated lateral acceleration of bogie frame according to concept of limit speed.</p>
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<p>Hunting motion stabilization at low conicity of <span class="html-italic">λ<sub>e</sub></span> = 0.06 when running in tangent lines. (<b>a</b>) Influence of vehicle speed increase on distribution characteristics of wheel wear index. (<b>b</b>,<b>c</b>) Variation patterns of wheel spin and longitudinal creepage when running at 575 km/h, which is maintained with the hypothesis of small creepage and non-spin. (<b>d</b>,<b>e</b>) Left and right wheel unloading rates of 1st wheelset when running at 575 km/h, the maximum value 0.60 has small occurrence probability of ≤5%.</p>
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<p>Concept of limit speed explained as suddenly transition from hunting motion stability to instability hunting oscillation at <span class="html-italic">λ<sub>e</sub></span> = 0.10, which becomes High Creepage Issue. (<b>a</b>) Influence of vehicle speed on distribution characteristics of wheel wear index in tangent line operations. (<b>b</b>) Lateral acceleration PSD of rear bogie frame changes suddenly into forced resonance, ca. 5.6 Hz, when <span class="html-italic">v</span> = 650 km/h. (<b>c</b>,<b>d</b>) High Creepage Issue represented through variation patterns of wheel spin and longitudinal creepage for left and right wheels of 1st wheelset.</p>
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<p>Gradual transition from hunting motion stability to instability hunting oscillation at <span class="html-italic">λ<sub>e</sub></span> = 0.16. (<b>a</b>) Influence of vehicle speed on distribution characteristics of wheel wear index in tangent line operations. (<b>b</b>) Lateral acceleration PSD of rear bogie frame changes gradually into forced resonance, ca. 6.0 Hz, when <span class="html-italic">v</span> = 600 km/h. (<b>c</b>,<b>d</b>) Variation patterns of wheel spin and longitudinal creepage, which is one of main characteristics of stable wear stage at high conicity.</p>
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<p>Central hollow tread wear results occasionally in local conformal or bad contact between worn wheel and rail on some rail sections, which forces bogie frame to produce lateral forced vibration when running in tangent lines. (<b>a</b>,<b>b</b>) Equivalent conicity and RRD curves calculated by slight central hollow tread wear. (<b>c</b>) Travelling wide light band is formed on top surface of railhead while concentrated wear is evolved on wheel tread. (<b>d</b>) Bogie frame thereby generates forced resonance with dominant frequency of ca. 6 Hz and leading frequency is close to or more than 10 Hz. (<b>e</b>) Influence of vehicle speed on lateral acceleration <span class="html-italic">(RMS)</span><sub>2.2<span class="html-italic">σ</span></sub> of bogie frame.</p>
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<p>Self-cleaning of central hollow tread wear can be verified when M-T-M three-car trainset across over dedicated lines of 200 km/h grade, running at 200 km/h in curving negotiation with radius 3000 m, superelevation 150 mm and transition (500–700) m. (<b>a</b>,<b>b</b>) Distribution characteristics of left and right wheel wear index for 1st and 4th wheelsets of front motor vehicle. (<b>c</b>,<b>d</b>) Distribution characteristics of left and right wheel wear index for 1st and 4th wheelsets of middle trailer vehicle. (<b>e</b>,<b>f</b>) Distribution characteristics of left and right wheel wear index for 1st and 4th wheelsets of rear motor vehicle.</p>
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<p>Optimization design of rubber hanging parameters for equipment cabin under floor frame based on weak coupling interface is adopted for service car body system, so as to avoid internal lateral coupling resonance of traction converter as much as possible. (<b>a</b>–<b>c</b>) 1st order lateral bending inherent mode of aluminium alloy car body has evolved into two critical modes, i.e., 1st order lateral bending modes on lower and upper parts of service car body. (<b>d</b>) Safety assessment of lateral vibration for traction converter when running in a tangent line approaching to limit speed of 650 km/h under <span class="html-italic">λ<sub>e</sub></span> = 0.06 according to specified in IEC61373—2010. (<b>e</b>,<b>f</b>) Safety assessment of lateral vibration for traction converter when running in a tangent line with higher speeds of (420–550) km/h and near to limit speed of 650 km/h under <span class="html-italic">λ<sub>e</sub></span> = 0.10. (<b>g</b>) Safety assessment of lateral vibration for traction converter when running in a tangent line with service speeds of (300–380) km/h under <span class="html-italic">λ<sub>e</sub></span> = 0.35. (<b>h</b>) Safety assessment of lateral vibration for traction converter when running in a tangent line with three speed grades of 480/650/780 km/h when considering negative impacts of detrimental wear like central hollow tread wear.</p>
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13 pages, 4495 KiB  
Article
Analysis of Dynamic Characteristics of Low-Floor Train Passing Switch in Facing Direction with Bad Alignment Irregularity Ahead of the Turnout
by Xiaohong Jia, Xinwen Yang and Guangtian Shi
Appl. Sci. 2023, 13(7), 4560; https://doi.org/10.3390/app13074560 - 4 Apr 2023
Viewed by 1414
Abstract
A low-floor train–turnout coupling dynamic model considering bad alignment irregularity ahead of the turnout was established on the basis of a field test in which the dynamic performances of a low-floor train passing through a no. 6 turnout in a rail transit depot [...] Read more.
A low-floor train–turnout coupling dynamic model considering bad alignment irregularity ahead of the turnout was established on the basis of a field test in which the dynamic performances of a low-floor train passing through a no. 6 turnout in a rail transit depot in China had been measured, as well as the line alignment and wheel and rail profiles. There are two types of wheelsets in the low-floor train: integral wheelset and independent wheelset. The model fully considers the coupling effect between the vehicle and the ballast components, and the simulated results are in consistence with measured results in the field test. Based on this, the influences of train speed, the wheel–rail friction coefficient, and the track alignment optimization of the dynamic performance of low-floor trains passing switch in facing direction are analyzed. The main results indicate that eliminating alignment irregularities before the switch can effectively improve the dynamic performance of the integrated wheelset in the switch and the lateral forces of the outer wheels of these two vehicles are reduced by about 80%, the derailment coefficients are reduced by about 70%, the vertical force is reduced by about 10–20% and wheel load is reduced by approximately 30%. Full article
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<p>Two test sections of wheel–rail contact forces.</p>
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<p>Field test of low-floor trains passing n. 6 turnout: (<b>a</b>) The general test configuration; (<b>b</b>) the strain gauges applied on the rail waist.</p>
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<p>A basic module of a 70% low-floor train.</p>
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<p>Two types of bogie models: (<b>a</b>) a bogie with integrated wheelsets; (<b>b</b>) a bogie with the independently rotating wheelsets.</p>
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<p>The MBS dynamic model of the two-module low-floor train.</p>
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<p>The 15 measured profiles of stock and blade rails.</p>
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<p>Measured line alignment: (<b>a</b>) plane and vertical sections of the line; (<b>b</b>) the alignment irregularity on the tangent; (<b>c</b>) geometrical difference between the measured and ideal irregularity along the x-coordinate.</p>
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<p>Wheel–rail contact forces of outer leading wheel of motor 1 and trailer 1: (<b>a</b>) wheel–rail lateral force; (<b>b</b>) wheel–rail vertical force.</p>
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<p>The root mean square value comparison of wheel–rail vertical force of outer wheel: (<b>a</b>) vertical force values at Section 1; (<b>b</b>) vertical force values at Section 2.</p>
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<p>The root mean square value comparison of the wheel–rail lateral force of the outer wheel: (<b>a</b>) lateral force values at Section 1; (<b>b</b>) lateral force values at Section 2.</p>
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<p>Dynamic characteristics of a train passing the tangent and switch under different train speeds. (<b>a</b>) Wheel–rail lateral force; (<b>b</b>) wheel–rail vertical force; (<b>c</b>) derailment coefficient; (<b>d</b>) wheel load reduction; (—) magnitudes in the tangent; (--) magnitudes in the switch.</p>
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<p>Dynamic characteristics of the train passing the tangent and switch under different friction coefficients. (<b>a</b>) Wheel–rail lateral force; (<b>b</b>) wheel–rail vertical force; (<b>c</b>) derailment coefficient; (<b>d</b>) wheel load reduction; (—) magnitudes in the tangent; (--) magnitudes in the switch.</p>
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<p>Dynamic characteristics of the train passing the tangent and switch under different track alignments. (<b>a</b>) Wheel–rail lateral force; (<b>b</b>) wheel–rail vertical force; (<b>c</b>) derailment coefficient; (<b>d</b>) wheel load reduction.</p>
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<p>Dynamic characteristics of the train passing the tangent and switch under different track alignments. (<b>a</b>) Wheel–rail lateral force; (<b>b</b>) wheel–rail vertical force; (<b>c</b>) derailment coefficient; (<b>d</b>) wheel load reduction.</p>
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20 pages, 14723 KiB  
Article
An Affordable Acoustic Measurement Campaign for Early Prototyping Applied to Electric Ducted Fan Units
by Stefan Schoder, Jakob Schmidt, Andreas Fürlinger, Roppert Klaus and Maurerlehner Paul
Fluids 2023, 8(4), 116; https://doi.org/10.3390/fluids8040116 - 31 Mar 2023
Viewed by 2273
Abstract
New innovative green concepts in electrified vertical take-off and landing vehicles are currently emerging as a revolution in urban mobility going into the third dimension (vertically). The high population density of cities makes the market share highly attractive while posing an extraordinary challenge [...] Read more.
New innovative green concepts in electrified vertical take-off and landing vehicles are currently emerging as a revolution in urban mobility going into the third dimension (vertically). The high population density of cities makes the market share highly attractive while posing an extraordinary challenge in terms of community acceptance due to the increasing and possibly noisier commuter traffic. In addition to passenger transport, package deliveries to customers by drones may enter the market. The new challenges associated with this increasing transportation need in urban, rural, and populated areas pose challenges for established companies and startups to deliver low-noise emission products. The article’s objective is to revisit the benefits and drawbacks of an affordable acoustic measurement campaign focused on early prototyping. In the very early phase of product development, available resources are often considerably limited. With this in mind, this article discusses the sound power results using the enveloping surface method in a typically available low-reflection room with a reflecting floor according to DIN EN ISO 3744:2011-02. The method is applied to a subsonic electric ducted fan (EDF) unit of a 1:2 scaled electrified vertical take-off and landing vehicle. The results show that considerable information at low costs can be gained for the early prototyping stage, despite this easy-to-use, easy-to-realize, and non-fine-tuned measurement setup. Furthermore, the limitations and improvements to a possible experimental setup are presented to discuss a potentially more ideal measurement environment. Measurements at discrete operating points and transient measurements across the total operating range were conducted to provide complete information on the EDF’s acoustic behavior. The rotor-self noise and the rotor–stator interaction were identified as primary tonal sound sources, along with the highest broadband noise sources located on the rotor. Based on engineering experience, a first acoustic improvement treatment was also quantified with a sound power level reduction of 4 dB(A). In conclusion, the presented method is a beneficial first measurement campaign to quantify the acoustic properties of an electric ducted fan unit under minimal resources in a reasonable time of several weeks when starting from scratch. Full article
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<p>The visualization of components in a typical single-stage axial-flow EDF unit. Adapted from [<a href="#B5-fluids-08-00116" class="html-bibr">5</a>].</p>
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<p>The device under test during the measurement campaign (<b>right</b>) is one fan of the propulsion assemblies, which are arranged left and right of the fuselage of the APELEON X1 (<b>left</b>).</p>
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<p>Visualization of potential noise reduction measures at an EDF unit.</p>
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<p>Design and placement of absorber linings: (<b>a</b>) placement in EDF; and (<b>b</b>) design of the micro-perforated absorber (MPA).</p>
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<p>Visualization of the microphone positions for the measurements relative to the propulsion test stand. The numbers in the figure describe the positions where a microphone is placed.</p>
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<p>Setup and spatial dimensions of the experimental facility and positioning of the EDF unit on a propulsion test bench inside the measuring room. Adapted from [<a href="#B5-fluids-08-00116" class="html-bibr">5</a>].</p>
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<p>Narrowband <math display="inline"><semantics> <mover> <mrow> <msub> <mi>L</mi> <mi mathvariant="normal">W</mi> </msub> <mo>,</mo> <mi mathvariant="normal">A</mi> </mrow> <mo>¯</mo> </mover> </semantics></math> at different operating points relative to the highest narrowband sound power level in the observed operating range.</p>
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<p><math display="inline"><semantics> <mover> <mrow> <msub> <mi>L</mi> <mi mathvariant="normal">W</mi> </msub> <mo>,</mo> <mi mathvariant="normal">A</mi> </mrow> <mo>¯</mo> </mover> </semantics></math> of the EDF unit, run between neighboring operating points. The scale is selected relative to the highest sound power level in the respective measurement range. The black and red circle mark detailed characteristics in the spectrograms.</p>
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<p>A weighted OSPL of unmodified EDF unit over the operating range.</p>
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<p>Narrowband <math display="inline"><semantics> <mover> <mrow> <msub> <mi>L</mi> <mi mathvariant="normal">W</mi> </msub> <mo>,</mo> <mi mathvariant="normal">A</mi> </mrow> <mo>¯</mo> </mover> </semantics></math> of the electric powertrain with a dismounted axial fan stage operated at four operating points.</p>
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<p><math display="inline"><semantics> <mover> <mrow> <msub> <mi>L</mi> <mi mathvariant="normal">W</mi> </msub> <mo>,</mo> <mi mathvariant="normal">A</mi> </mrow> <mo>¯</mo> </mover> </semantics></math> of the electric powertrain between neighboring operating points relative to the highest sound power level in the respective measurement range. The black circle marks a detail of a crossing characteristic in the spectrogram.</p>
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<p>A weighted OSPL over an operating range of unmodified (•) and modified (<span class="html-italic">▪</span>) and the narrowband <math display="inline"><semantics> <mover> <mrow> <msub> <mi>L</mi> <mi mathvariant="normal">W</mi> </msub> <mo>,</mo> <mi mathvariant="normal">A</mi> </mrow> <mo>¯</mo> </mover> </semantics></math> of the EDF unit at OP3 with unmodified configuration in black and the modified configuration in gray. We attempt to compare the detailed spectra at approximately 9000 Hz, OP2, and 3 (shown here) at 8000 and 10,000 Hz. Comparing these 3 conditions to determine what might explain the reduction of more 4 dB rather than the usual 2 dB.</p>
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<p>LW,A of the modified EDF unit between neighboring operating points relative to the highest sound power level in the respective measurement range. The black and red circle mark detailed characteristics in the spectrograms.</p>
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11 pages, 12255 KiB  
Technical Note
Suitable LiDAR Platform for Measuring the 3D Structure of Mangrove Forests
by Hideyuki Niwa, Hajime Ise and Mahito Kamada
Remote Sens. 2023, 15(4), 1033; https://doi.org/10.3390/rs15041033 - 14 Feb 2023
Cited by 3 | Viewed by 2531
Abstract
Investigating the three-dimensional structure of mangrove forests is critical for their conservation and restoration. However, mangrove forests are difficult to survey in the field, and their 3D structure is poorly understood. Light detection and ranging (LiDAR) is considered an accurate and dependable method [...] Read more.
Investigating the three-dimensional structure of mangrove forests is critical for their conservation and restoration. However, mangrove forests are difficult to survey in the field, and their 3D structure is poorly understood. Light detection and ranging (LiDAR) is considered an accurate and dependable method of measuring the 3D structure of mangrove forests. This study aimed to find a suitable LiDAR platform for obtaining attributes such as breast height diameter and canopy area, as well as for measuring a digital terrain model (DTM), the base data for hydrological analysis. A mangrove forest near the mouth of the Oura River in Aza-Oura, Nago City, Okinawa Prefecture, Japan, was studied. We used data from terrestrial LiDAR scanning “TLS” and unmanned aerial vehicle (UAV) LiDAR scanning “ULS” as well as data merged from TLS and ULS “Merge”. By interpolating point clouds of the ground surface, DTMs of 5 cm × 5 cm were created. DTMs obtained from ULS could not reproduce the heaps of Thalassina anomala or forest floor microtopography compared with those obtained from TLS. Considering that ULS had a few point clouds in the forest, automatic trunk identification could not be used to segment trees. TLS could segment trees by automatically identifying trunks, but the number of trees identified roughly doubled that of the visual identification results. The number of tree crowns identified using TLS and ULS was approximately one quarter of those identified visually, and many of them were larger in area than the visually traced crowns. The accuracy of tree segmentation using the canopy height model (CHM) was low. The number of canopy trees identified using Merge produced the best results, accounting for 61% of the visual identification results. Results of tree segmentation by CHM suggest that combining TLS and ULS measurements may improve tree canopy identification. Although ULS is a promising new technology, its applications are clearly limited, at least in mangrove forests such as the Oura River, where Bruguiera gymnorhiza is dominant. Depending on the application, using different LiDAR platforms, such as airborne LiDAR scanning, UAV LiDAR scanning, and TLS, is important. Merging 3D point clouds acquired by different platforms, as proposed in this study, is an important option in this case. Full article
(This article belongs to the Section Biogeosciences Remote Sensing)
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Graphical abstract

Graphical abstract
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<p>Study location.</p>
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<p>Changes in mangrove forests; comparison of orthomosaic images using UAVs. The red boundary is the validation area (4783 m<sup>2</sup>).</p>
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<p>DTM built from 3D point cloud model. (<b>a</b>): heaps of <span class="html-italic">T. anomala</span>, (<b>b</b>): forest floor microtopography, (<b>c</b>): area where shrub <span class="html-italic">K. obovata</span> was widely dispersed and could not be traversed.</p>
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<p>Simple tidal simulation with water levels varying every 10 cm. Blue indicates flooded areas.</p>
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<p>Outcome of tree segmentation. (<b>a</b>): A view of the forest point clouds (<b>b</b>): The location of identified trees.</p>
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<p>DBH distribution of trees identified through tree segmentation.</p>
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<p>Distribution of canopy area identified through tree segmentation.</p>
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<p>Tree canopies identified through tree segmentation.</p>
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12 pages, 3451 KiB  
Article
Design of an Integrated Controller for a Sweeping Mechanism of a Low-Dust Almond Pickup Machine
by Reza Serajian, Jian-Qiao Sun and Reza Ehsani
Sensors 2023, 23(4), 2046; https://doi.org/10.3390/s23042046 - 11 Feb 2023
Cited by 2 | Viewed by 1549
Abstract
California is the world’s biggest producer and exporter of almonds. Currently, the sweeping of almonds during the harvest creates a significant amount of dust, causing air pollution in the neighboring urban areas. A low-dust sweeping system was designed to reduce the dust during [...] Read more.
California is the world’s biggest producer and exporter of almonds. Currently, the sweeping of almonds during the harvest creates a significant amount of dust, causing air pollution in the neighboring urban areas. A low-dust sweeping system was designed to reduce the dust during the sweeping of almonds in the orchard. The system includes a feedback control system to control the sweeper brushes’ height and their angular velocity by adjusting the forward velocity of the harvester and the brushes’ rotational speeds to avoid any extra overlapping sweeping, which increases dust generation. The governing kinematic equations for sweepers’ angular velocity and vehicle forward speed were derived. The feedback controllers for synchronizing these speeds were designed to optimize brush/dust contact to minimize dust generation. The sweepers’ height controller was also designed to stabilize the gap between the brushes and the orchard floor and track the road trajectory. Controllers were simulated and tuned for a fast response for agricultural applications with less than a second response delay. Results showed that the designed system has acceptable performance and generates low amounts of dust within the acceptable range of California ambient air quality standards. Full article
(This article belongs to the Section Physical Sensors)
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<p>Sweeping mechanism.</p>
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<p>The stationary plane trajectory of the sweeper.</p>
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<p>The plane trajectory of tines’ movement.</p>
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<p>Brush angular velocity and motor input voltage.</p>
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<p>Control system block diagram for front brush angular speed regulation.</p>
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<p>Front brush tracking control response with PID controller.</p>
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<p>Front brush-tracking control response with a PID controller with overshoot and settling time.</p>
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<p>Front brush height control response with a PID controller.</p>
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<p>Control system block diagram for front brushes’ height.</p>
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17 pages, 2849 KiB  
Article
A Fault Tolerant Surveillance System for Fire Detection and Prevention Using LoRaWAN in Smart Buildings
by Abdullah Safi, Zulfiqar Ahmad, Ali Imran Jehangiri, Rohaya Latip, Sardar Khaliq uz Zaman, Muhammad Amir Khan and Rania M. Ghoniem
Sensors 2022, 22(21), 8411; https://doi.org/10.3390/s22218411 - 1 Nov 2022
Cited by 21 | Viewed by 5038
Abstract
In recent years, fire detection technologies have helped safeguard lives and property from hazards. Early fire warning methods, such as smoke or gas sensors, are ineffectual. Many fires have caused deaths and property damage. IoT is a fast-growing technology. It contains equipment, buildings, [...] Read more.
In recent years, fire detection technologies have helped safeguard lives and property from hazards. Early fire warning methods, such as smoke or gas sensors, are ineffectual. Many fires have caused deaths and property damage. IoT is a fast-growing technology. It contains equipment, buildings, electrical systems, vehicles, and everyday things with computing and sensing capabilities. These objects can be managed and monitored remotely as they are connected to the Internet. In the Internet of Things concept, low-power devices like sensors and controllers are linked together using the concept of Low Power Wide Area Network (LPWAN). Long Range Wide Area Network (LoRaWAN) is an LPWAN product used on the Internet of Things (IoT). It is well suited for networks of things connected to the Internet, where terminals send a minute amount of sensor data over large distances, providing the end terminals with battery lifetimes of years. In this article, we design and implement a LoRaWAN-based system for smart building fire detection and prevention, not reliant upon Wireless Fidelity (Wi-Fi) connection. A LoRa node with a combination of sensors can detect smoke, gas, Liquefied Petroleum Gas (LPG), propane, methane, hydrogen, alcohol, temperature, and humidity. We developed the system in a real-world environment utilizing Wi-Fi Lora 32 boards. The performance is evaluated considering the response time and overall network delay. The tests are carried out in different lengths (0–600 m) and heights above the ground (0–2 m) in an open environment and indoor (1st Floor–3rd floor) environment. We observed that the proposed system outperformed in sensing and data transfer from sensing nodes to the controller boards. Full article
(This article belongs to the Section Sensor Networks)
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<p>Proposed F2DPS System.</p>
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<p>MQ2 Gas Sensor.</p>
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<p>Heltec Wi-Fi LoRa 32 V2.</p>
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<p>Dataflow model.</p>
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<p>0-m height and 16, 32, 64 bytes payload size.</p>
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<p>A height of 1-m and 16, 32, 64 bytes payload size.</p>
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<p>A height of 2-m and 16, 32, 64 bytes payload size.</p>
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<p>A height of 0-m and (16, 32, 64) bytes Payload Size.</p>
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<p>1-m height and (16, 32, 64) bytes Payload Size.</p>
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<p>2-m height and 16, 32, 64 bytes Payload Size.</p>
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<p>First Floor with 16, 32, 64 bytes Payload Size.</p>
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<p>Second Floor with 16, 32, 64 bytes Payload Size.</p>
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<p>Third Floor with 16, 32, 64 bytes Payload Size.</p>
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<p>Network Delay Compression Analysis: First Floor with 16, 32, 64 Payload Size.</p>
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<p>Second Floor with 16, 32, 64 Payload Size.</p>
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<p>Third Floor with 16, 32, 64 Payload Size.</p>
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