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18 pages, 824 KiB  
Article
Anti-Disturbance Target Tracking Control of Auxiliary Unmanned Ground Vehicles for Physical Education
by Lei Liu and Wei Yin
Electronics 2024, 13(23), 4620; https://doi.org/10.3390/electronics13234620 - 22 Nov 2024
Abstract
The auxiliary unmanned ground vehicle (AUGV) for physical education can significantly enhance the continuity and safety of training and competitions. However, obstacles and area boundary constraints present substantial challenges to the efficiency of the AUGV. This paper proposes an anti-disturbance target tracking control [...] Read more.
The auxiliary unmanned ground vehicle (AUGV) for physical education can significantly enhance the continuity and safety of training and competitions. However, obstacles and area boundary constraints present substantial challenges to the efficiency of the AUGV. This paper proposes an anti-disturbance target tracking control strategy for AUGV, enabling rapid tracking of out-of-bounds balls. In the guidance layer, we design safety constraints based on the exponentially stabilizing control Lyapunov function (ES-CLF) position constraint and control barrier function (CBF), and solve the expected convergence velocity guidance law through quadratic programming. Additionally, the expected motion direction of AUGV is determined using the expected combined velocity. In the control layer, we employ a nonlinear tracking differentiators (NLTD) to achieve finite-time estimation of the derivative of the guidance velocity signal, and observed the model parameter uncertainty and external environmental disturbances through a fixed time disturbance observer. Finally, a fixed-time control strategy is developed to achieve precise target tracking. Stability analysis and simulation results confirm the effectiveness of the proposed AUGV target tracking control strategy and the safety collision avoidance method. Full article
(This article belongs to the Section Systems & Control Engineering)
22 pages, 5596 KiB  
Article
Design and Rapid Prototyping of Deformable Rotors for Amphibious Navigation in Water and Air
by Chengrong Du and Dongbiao Zhao
Machines 2024, 12(12), 837; https://doi.org/10.3390/machines12120837 - 22 Nov 2024
Viewed by 90
Abstract
This paper aims to report the design of a mechanism to drive a propeller to deform between an aerial and one aquatic shape. This mechanism can realize the deformation of blade angle, radius, blade twist angle distribution and blade section thickness. Inspired by [...] Read more.
This paper aims to report the design of a mechanism to drive a propeller to deform between an aerial and one aquatic shape. This mechanism can realize the deformation of blade angle, radius, blade twist angle distribution and blade section thickness. Inspired by the Kresling origami structure and utilizing its rotation-folding motion characteristics, a propeller hub structure with variable blade angle is designed. A blade deformation unit (S-unit) with extensional-torsional kinematic characteristics is designed through the motion analysis of a spherical four-bar mechanism. A rib support structure fixed to the linkages of the s-unit is designed to achieve the change in blade section thickness. Based on motion analysis, the coordinate transformation method has been used to establish the relationship between propeller shape and deformation mechanism. The deformation of blade extension, blade twist distribution, and blade section thickness are analyzed. The deformation ability of the proposed structure can be verified then by kinematic simulation and rapid prototyping based on 3-D printing. It is proved that the proposed mechanism is applicable to deformable propeller design. The rapid prototype testing validates the stable motion of the mechanism. However, due to the relatively large self-weight of the structure, the blade has a slight deformation. In the subsequent work, the structural strength issue needs to be emphasized. Full article
(This article belongs to the Section Machine Design and Theory)
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Figure 1
<p>Mechanism schematics of Kresling origami and modified Kresling origami. (<b>a</b>) Kresling origami (<b>b</b>) modified Kresling origami.</p>
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<p>Geometric schematic of the Kresling structure.</p>
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<p>Mechanism schematics of spherical 4-bar mechanism. (<b>a</b>) 3-D geometrical model schematic. (<b>b</b>) Mechanism brief schematics.</p>
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<p>Mechanism schematic of the propeller hub.</p>
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<p>Mechanism schematics of a Kresling hub. (<b>a</b>) Hub shape a, (<b>b</b>) hub shape b, (<b>c</b>) hub shape c, and (<b>d</b>) hub shape d.</p>
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<p>Mechanism schematic of serial connected s-units.</p>
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<p>Schematic diagram of serial connected s-units deformation. (<b>a</b>) top view of aerial shape. (<b>b</b>) side view of aerial shape. (<b>c</b>) top view of aquatic shape. (<b>d</b>) side view of aquatic shape.</p>
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<p>Schematic diagram of blade section deformation. (<b>a</b>) Aerial shape. (<b>b</b>) Aquatic shape.</p>
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<p>Schematic diagram of deformation driving mechanism.</p>
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<p>Deformation of the deformation driving mechanism. (<b>a</b>) Top view of aerial shape. (<b>b</b>) Side view of aerial shape. (<b>c</b>) Top view of aquatic shape. (<b>d</b>) Side view of aquatic shape.</p>
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<p>Schematic diagram of coordinate system.</p>
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<p>Data graph of extensional ratio.</p>
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<p>Schematic diagram of torsional deformation.</p>
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<p>Data graph of torsional deformation.</p>
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<p>Schematic diagram of thickness variation.</p>
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<p>Schematic diagram of design specifications.</p>
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<p>Schematic diagram of the layout of drive points.</p>
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<p>Mechanism shape of different <math display="inline"><semantics> <msub> <mi>θ</mi> <mi>s</mi> </msub> </semantics></math>. (<b>a</b>) <math display="inline"><semantics> <mrow> <msub> <mi>θ</mi> <mi>s</mi> </msub> <mo>=</mo> <mn>57.377</mn> </mrow> </semantics></math>. (<b>b</b>) <math display="inline"><semantics> <mrow> <msub> <mi>θ</mi> <mi>s</mi> </msub> <mo>=</mo> <mn>85.823</mn> </mrow> </semantics></math>. (<b>c</b>) <math display="inline"><semantics> <mrow> <msub> <mi>θ</mi> <mi>s</mi> </msub> <mo>=</mo> <mn>96.235</mn> </mrow> </semantics></math>. (<b>d</b>) <math display="inline"><semantics> <mrow> <msub> <mi>θ</mi> <mi>s</mi> </msub> <mo>=</mo> <mn>107.142</mn> </mrow> </semantics></math>. (<b>e</b>) <math display="inline"><semantics> <mrow> <msub> <mi>θ</mi> <mi>s</mi> </msub> <mo>=</mo> <mn>118.312</mn> </mrow> </semantics></math>. (<b>f</b>) <math display="inline"><semantics> <mrow> <msub> <mi>θ</mi> <mi>s</mi> </msub> <mo>=</mo> <mn>130.298</mn> </mrow> </semantics></math>.</p>
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<p>Data graph of attack angle distribution.</p>
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<p>Data comparison chart of extension ratio.</p>
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<p>Data comparison chart of attack angle distribution.</p>
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<p>Mechanism shape of different <math display="inline"><semantics> <msub> <mi>θ</mi> <mi>s</mi> </msub> </semantics></math>. (<b>a</b>) Aerial shape mesh structure. (<b>b</b>) Aquatic shape mesh structure.</p>
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<p>Stress distribution diagram. (<b>a</b>) Aerial shape stress distribution. (<b>b</b>) Aquatic shape stress distribution.</p>
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<p>Parts of propeller morphing mechanism. (<b>a</b>) Parts of equilateral unit BC linkage and oblique symmetric unit AD linkage. (<b>b</b>) Parts of equilateral unit DC linkage and oblique symmetric unit AB linkage. (<b>c</b>) Parts of upper half rib structure. (<b>d</b>) Parts of lower half rib structure.</p>
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<p>Propeller morphing mechanism. (<b>a</b>) Aerial shape of the mechanism. (<b>b</b>) Aquatic shape of the mechanism.</p>
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23 pages, 5837 KiB  
Article
Mechanical Design, Analysis, and Dynamics Simulation of a Cable-Driven Wearable Flexible Exoskeleton System
by Xuetong Jin, Wenqian Ding, Mathias Baumert, Yan Wei, Qinglin Li, Wei Yang and Yuqiao Yan
Technologies 2024, 12(12), 238; https://doi.org/10.3390/technologies12120238 - 21 Nov 2024
Viewed by 314
Abstract
As a new development direction in exoskeleton research, wearable flexible exoskeleton systems are highly favored for their freedom of movement, flexibility, lightweight design, and comfortable wearability. These systems are gradually becoming the preferred choice for rehabilitation therapy, and enhancing physical performance. In this [...] Read more.
As a new development direction in exoskeleton research, wearable flexible exoskeleton systems are highly favored for their freedom of movement, flexibility, lightweight design, and comfortable wearability. These systems are gradually becoming the preferred choice for rehabilitation therapy, and enhancing physical performance. In this thesis, based on existing research in wearable flexible exoskeletons, we aim to design a lightweight wearable upper limb rehabilitation exoskeleton that meets the needs of stroke patients with a high likelihood of upper limb impairment. The system should provide sufficient flexibility for comfortable and convenient use while minimizing the weight to reduce the user’s burden during wear. Our proposed lightweight wearable flexible exoskeleton assists users in achieving rehabilitation exercises for both the shoulder (external/internal rotation) and forearm (flexion/extension) movements. The system consists of a flexible fabric section connecting the torso–shoulder–upper arm, a flexible fabric section for the forearm, and a back-mounted actuation device. The fabric sections primarily consist of elastic textile materials with a few rigid components. Emphasizing lightweight design, we strive to minimize the exoskeleton’s weight, ensuring optimal user comfort. The actuation device connects to the fabric sections via tensioned wires, driven by a motor to induce arm movement during rehabilitation exercises. To enhance safety and prevent secondary upper limb injuries due to exoskeleton malfunction, we incorporate a physical limiter retricting the exoskeleton’s range of motion. Additionally, we include tension-adjustment mechanisms and cushioning springs to improve the feasibility of this wearable flexible exoskeleton. After completing the structural design, this paper conducted a basic static and kinematic analysis of the exoskeleton system to provide theoretical support. Additionally, the feasibility and effectiveness of the exoskeleton system design were verified through dynamic simulations. Full article
(This article belongs to the Section Assistive Technologies)
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<p>Conceptual design of lightweight upper limb wearable rehabilitation exoskeleton.</p>
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<p>U-shaped bearing for adjusting wire tension.</p>
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<p>Conceptual design of lightweight upper limb wearable rehabilitation exoskeleton: three views and tension-adjustable structure with ropes.</p>
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<p>Design of limiter structure.</p>
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<p>Schematic diagram of the driving system.</p>
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<p>The kinematic analysis diagram 1 of the upper arm’s external/internal rotation concerning the shoulder joint.</p>
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<p>The kinematic analysis diagram 2 of the upper arm’s angle of external/internal rotation concerning the shoulder joint.</p>
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<p>The kinematic analysis diagram 1 of the forearm’s flexion/extension movements concerning the elbow joint.</p>
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<p>The kinematic analysis diagram 2 of the forearm’s flexion/extension movements concerning the elbow joint.</p>
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<p>The force analysis diagram of the upper arm’s external/internal rotation movements concerning the shoulder joint.</p>
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<p>The force analysis diagram of the forearm’s flexion/extension movements concerning the elbow joint.</p>
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<p>Positioning diagram for limiter.</p>
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<p>The relationship curves of angular velocity/angular acceleration of the shoulder joint with respect to time in the simulation of shoulder joint internal/external rotation.</p>
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<p>The relationship curves of angular velocity/angular acceleration of the elbow joint with respect to time in the simulation of elbow joint flexion/extension.</p>
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<p>(<b>a</b>): The relationship curves of angular velocity/angular acceleration of the shoulder joint with respect to time in compound movements. (<b>b</b>): The relationship curves of angular velocity/angular acceleration of the elbow joint with respect to time in compound movements.</p>
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<p>Modeling and visualization of lightweight wearable rehabilitation exoskeleton.</p>
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19 pages, 5999 KiB  
Article
Automated Pipeline for Robust Cat Activity Detection Based on Deep Learning and Wearable Sensor Data
by Md Ariful Islam Mozumder, Tagne Poupi Theodore Armand, Rashadul Islam Sumon, Shah Muhammad Imtiyaj Uddin and Hee-Cheol Kim
Sensors 2024, 24(23), 7436; https://doi.org/10.3390/s24237436 - 21 Nov 2024
Viewed by 230
Abstract
The health, safety, and well-being of household pets such as cats has become a challenging task in previous years. To estimate a cat’s behavior, objective observations of both the frequency and variability of specific behavior traits are required, which might be difficult to [...] Read more.
The health, safety, and well-being of household pets such as cats has become a challenging task in previous years. To estimate a cat’s behavior, objective observations of both the frequency and variability of specific behavior traits are required, which might be difficult to come by in a cat’s ordinary life. There is very little research on cat activity and cat disease analysis based on real-time data. Although previous studies have made progress, several key questions still need addressing: What types of data are best suited for accurately detecting activity patterns? Where should sensors be strategically placed to ensure precise data collection, and how can the system be effectively automated for seamless operation? This study addresses these questions by pointing out whether the cat should be equipped with a sensor, and how the activity detection system can be automated. Magnetic, motion, vision, audio, and location sensors are among the sensors used in the machine learning experiment. In this study, we collect data using three types of differentiable and realistic wearable sensors, namely, an accelerometer, a gyroscope, and a magnetometer. Therefore, this study aims to employ cat activity detection techniques to combine data from acceleration, motion, and magnetic sensors, such as accelerometers, gyroscopes, and magnetometers, respectively, to recognize routine cat activity. Data collecting, data processing, data fusion, and artificial intelligence approaches are all part of the system established in this study. We focus on One-Dimensional Convolutional Neural Networks (1D-CNNs) in our research, to recognize cat activity modeling for detection and classification. Such 1D-CNNs have recently emerged as a cutting-edge approach for signal processing-based systems such as sensor-based pet and human health monitoring systems, anomaly identification in manufacturing, and in other areas. Our study culminates in the development of an automated system for robust pet (cat) activity analysis using artificial intelligence techniques, featuring a 1D-CNN-based approach. In this experimental research, the 1D-CNN approach is evaluated using training and validation sets. The approach achieved a satisfactory accuracy of 98.9% while detecting the activity useful for cat well-being. Full article
(This article belongs to the Special Issue Advances in Sensing-Based Animal Biomechanics)
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<p>Housing, monitoring, and husbandry environment of the cats.</p>
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<p>Wearable sensors with internal features.</p>
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<p>Data collection procedure. (<b>A</b>) Server room for real-time monitoring and storing data, (<b>B</b>) sensor device, (<b>C</b>) sensor device on the cat’s neck, (<b>D</b>) cat living space, including surveillance cameras, (<b>E</b>) transferring sensor data to the server.</p>
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<p>Data distribution of activity detection.</p>
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<p>Samples of bio-signals from the wearable devices on the cats.</p>
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<p>The deep learning model architecture of our experimental research work.</p>
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<p>Classification of the five activities.</p>
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<p>The complete process of the automated pipeline.</p>
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<p>Confusion matrix without normalization using the test dataset.</p>
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<p>Confusion matrix with normalization using the test dataset.</p>
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<p>Accuracy graph for the validation and training.</p>
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<p>Loss graph for the validation and training.</p>
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<p>Receiver operating characteristic (ROC) curves and AUCs for each class.</p>
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18 pages, 4337 KiB  
Article
A Comparison of the Quasi-Steady Assumption with Unsteady Effects on Tower Galloping Analysis
by Zihang Yang, Yangzhao Liu, Ying Chang and Kaoshan Dai
Buildings 2024, 14(12), 3707; https://doi.org/10.3390/buildings14123707 - 21 Nov 2024
Viewed by 206
Abstract
Traditional tower galloping theory is founded on the quasi-steady assumption, which has inherent limitations. By treating tower galloping as a single-degree-of-freedom crosswind bending flutter problem and introducing flutter derivatives into the expression of the crosswind aerodynamic force acting on the tower, the unsteady [...] Read more.
Traditional tower galloping theory is founded on the quasi-steady assumption, which has inherent limitations. By treating tower galloping as a single-degree-of-freedom crosswind bending flutter problem and introducing flutter derivatives into the expression of the crosswind aerodynamic force acting on the tower, the unsteady effects induced by motion can be incorporated into the analysis of tower galloping. An actual chamfered square cross-section tower was used as the research subject, and static tests and flutter derivative identification tests were performed on tower segment models without any modifications and with two types of aerodynamic measures: added arc-shaped fairings and vertical fin plates. Predictions of the aerodynamic damping of the tower structure were made and compared based on two different galloping theories: one under the quasi-steady assumption and the other considering unsteady effects. Experimental results indicate that both theories lead to the same conclusion about the galloping stability of the chamfered square tower. The original cross-section tower exhibited significant galloping instability problems, but the addition of arc-shaped fairings or vertical fin plates effectively improved its galloping stability performance. The predicted results of the tower’s aerodynamic damping based on the two different galloping theories differed by at most 34% at dimensionless wind speeds below 25. However, some differences were observed, and these differences between the two theories were noticeably affected by the magnitude of the dimensionless wind speed. Full article
(This article belongs to the Section Building Structures)
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Figure 1
<p>Schematic diagram of the crosswind aerodynamic force on the tower column based on quasi-steady theories.</p>
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<p>Schematic diagram of the crosswind aerodynamic force on the tower column taking account of unsteady effects.</p>
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<p>Cross-section drawing of sectional model for the tower column and definition of wind direction in tests.</p>
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<p>Section model suspended in wind tunnel.</p>
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<p>Test results of aerodynamic force coefficients for the tower column.</p>
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<p>Test results of galloping coefficients for the tower column.</p>
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<p>Sketch map of aerodynamic modifications.</p>
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<p>Comparison of aerodynamic force coefficients for the tower column before and after installing aerodynamic modifications.</p>
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<p>Comparison of galloping coefficients for the tower column before and after installing aerodynamic modifications.</p>
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<p>Vertically free vibration decay curves of the sectional model system under different test wind speeds.</p>
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<p>Flutter derivative <math display="inline"><semantics> <mrow> <msubsup> <mi>H</mi> <mn>1</mn> <mo>*</mo> </msubsup> </mrow> </semantics></math> versus reduced wind speed for the tower column without taking any measures.</p>
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<p>Comparison of flutter derivative <math display="inline"><semantics> <mrow> <msubsup> <mi>H</mi> <mn>1</mn> <mo>*</mo> </msubsup> </mrow> </semantics></math> versus reduced wind speed with and without aerodynamic measures.</p>
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<p>Crosswind bending damp ratio of the sectional model system versus reduced wind speed.</p>
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<p>Comparison results of aerodynamic damping predicted by two different galloping theories.</p>
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27 pages, 7577 KiB  
Article
Design and Experiment of Obstacle Avoidance Mower in Orchard
by Yi Yang, Yichuan He, Zhihui Tang and Hong Zhang
Agriculture 2024, 14(12), 2099; https://doi.org/10.3390/agriculture14122099 - 21 Nov 2024
Viewed by 189
Abstract
In order to solve the problem of mowing between plants in Xinjiang trunk orchards, an obstacle avoidance mower suitable for trunk orchard planting mode was designed. The whole structure, working principle and main parameter design of the obstacle avoidance mower are introduced. The [...] Read more.
In order to solve the problem of mowing between plants in Xinjiang trunk orchards, an obstacle avoidance mower suitable for trunk orchard planting mode was designed. The whole structure, working principle and main parameter design of the obstacle avoidance mower are introduced. The finite element analysis and kinematic analysis of the cutter are carried out on the premise of using a Y-shaped cutter and its arrangement, and the condition that the inter-row mower does not leak is determined. Through the modal analysis of the frame, the range of the first six natural frequencies of the frame is determined and compared with the frequency of the main excitation source of the machine to determine the rationality of the frame design. On the premise of simplifying the inter-plant obstacle avoidance mechanism into a two-dimensional model for kinematics analysis, the motion parameters of the key components of the machine were determined. At the same time, the virtual kinematics simulation single-factor test of the designed inter-plant obstacle avoidance device was carried out with the help of ADAMS 2020 software. Through the reduction in and calculation of the motion trajectory of the simulation test, it was finally determined that the forward speed of the machine, the elastic coefficient of the reset spring and the compression speed of the hydraulic cylinder were the main influencing factors of the inter-plant obstacle avoidance mower. The orthogonal test was designed and the optimal solution of the three test factors was determined. The optimal solution is taken for further field test verification. The results show that when the tractor forward speed is 1.5 km∙h−1, the hydraulic cylinder compression speed is 225 mm∙s−1, and the elastic coefficient of the reset spring is 29 N∙mm−1, the average leakage rate between the orchard plants is 7.64%, and the obstacle avoidance pass rate is 100%. The working stability is strong and meets the design requirements. Full article
(This article belongs to the Section Agricultural Technology)
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Figure 1
<p>The overall structure diagram of the orchard inter-plant obstacle avoidance mower. 1: Suspension device; 2: hydraulic oil tank; 3: transmission belt shell; 4: belt pulley drive shaft; 5: cylindrical guide rail; 6: cooling fan; 7: frame; 8: lawn mower roller; 9: lawn mower; 10: telescopic rod; 11: hydraulic directional valve; 12: obstacle avoidance disc; 13: obstacle avoidance rod; 14: spring; 15: obstacle avoidance disc bracket; 16: inter-row mower; 17: protective disc; 18: pressing roller; 19: stent; 20: gear box.</p>
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<p>Transmission system diagram of mower. 1. Mowing roller. 2. Hydraulic pump. 3. Transfer box. 4. Transmission shaft. 5. Drive pulley. 6. Drive pulley. 7. Belt. 8. Input shaft.</p>
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<p>The arrangement of pins on the roller shaft. (<b>a</b>) Helix arrangement. (<b>b</b>) Symmetrical arrangement. (<b>c</b>) Interlaced arrangement. (<b>d</b>) Symmetrical staggered arrangement.</p>
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<p>Cutter meshing diagram.</p>
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<p>Cutter statics simulation results. (<b>a</b>) Equivalent elastic deformation cloud diagram of cutter. (<b>b</b>) Cutter displacement deformation cloud map. (<b>c</b>) Cutter stress deformation cloud diagram.</p>
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<p>Cutter trajectory diagram.</p>
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<p>Three-dimensional model of frame.</p>
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<p>Frame finite element model.</p>
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<p>Frame of the first six-order modal analysis diagram.</p>
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<p>Automatic obstacle avoidance device between plants. 1. Hydraulic motor. 2. Cutterhead. 3. Connecting shaft. 4. Breakthrough rod. 5. Control valve. 6. Connecting plate. 7. Cylinder.</p>
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<p>Motion diagram of automatic obstacle avoidance device between plants. 1. Cutterhead. 2. Cutterhead connecting plate. 3. Connecting plate. 4. Hydraulic cylinder. Note: N is the position of the cutter head under the compression state of the hydraulic cylinder; n′ is the position of the cutter head in the elongation state of the hydraulic cylinder; R is the radius of the cutter head and the length of the hydraulic cylinder in the compressed state; l<sub>1</sub> is the length of the hydraulic cylinder in compression state. <math display="inline"><semantics> <mrow> <msubsup> <mrow> <mi mathvariant="normal">l</mi> </mrow> <mrow> <mn>1</mn> </mrow> <mrow> <mo>´</mo> </mrow> </msubsup> </mrow> </semantics></math> the length of the hydraulic cylinder in the telescopic state; L is the distance between the position of the hydraulic cylinder and the connecting plate; l<sub>3</sub> is the position of both ends of the connecting plate; l<sub>4</sub> is the distance between the midpoint of the cutter connection plate of the cutter head; l<sub>5</sub> is the distance between the center of the cutter head in the two middle states; l<sub>6</sub> is the distance between the two connection points in two states; l<sub>7</sub> is the distance between point O and E′; l<sub>8</sub> is the distance between two points of DE; l<sub>9</sub> is the distance between EE′; <math display="inline"><semantics> <mrow> <mi>α</mi> </mrow> </semantics></math> is the angle between OA and AB; <math display="inline"><semantics> <mrow> <msub> <mrow> <mi>α</mi> </mrow> <mrow> <mn>1</mn> </mrow> </msub> </mrow> </semantics></math> is the angle between BA and B′A; θ<sub>1</sub> is the angle between OA and OB. θ<sub>2</sub> is the angle between OA and OB′; <math display="inline"><semantics> <mrow> <msub> <mrow> <mi>α</mi> </mrow> <mrow> <mn>2</mn> </mrow> </msub> </mrow> </semantics></math> is the angle between OD and OB; <math display="inline"><semantics> <mrow> <msub> <mrow> <mi>α</mi> </mrow> <mrow> <mn>3</mn> </mrow> </msub> </mrow> </semantics></math> is the angle between OD′ and OB′; <math display="inline"><semantics> <mrow> <msub> <mrow> <mi>α</mi> </mrow> <mrow> <mn>4</mn> </mrow> </msub> </mrow> </semantics></math> is the angle between OB and OB′; <math display="inline"><semantics> <mrow> <msub> <mrow> <mi>α</mi> </mrow> <mrow> <mn>5</mn> </mrow> </msub> </mrow> </semantics></math> is the angle between OD and OB′; <math display="inline"><semantics> <mrow> <msub> <mrow> <mi>α</mi> </mrow> <mrow> <mn>6</mn> </mrow> </msub> </mrow> </semantics></math> is the angle between OD and OD′; <math display="inline"><semantics> <mrow> <msub> <mrow> <mi>α</mi> </mrow> <mrow> <mn>7</mn> </mrow> </msub> </mrow> </semantics></math> is the angle between OE and OD; <math display="inline"><semantics> <mrow> <msub> <mrow> <mi>α</mi> </mrow> <mrow> <mn>8</mn> </mrow> </msub> </mrow> </semantics></math> is the angle between D′ D and OD; and h is the vertical distance between the center of the cutter head in the two states.</p>
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<p>Simulation model of obstacle avoidance mowing device between plants. 1. Grassland 2. Pear tree. 3. Pear tree spacing. 4. Rack. 5. Barrier plate. 6. Barrier rod.</p>
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<p>Constraint relationship diagram of obstacle avoidance mower between orchard plants. 1. Obstacle avoidance disc drive. 2. Fixed pair. 3. Rotating pair. 4. Axis rotation drive.</p>
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<p>Model validation information.</p>
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<p>Simulation operation process of obstacle avoidance lawn mower in orchard. Note: (<b>a</b>): inter-row mowing operation stage; (<b>b</b>): obstacle avoidance rod touch tree stage; (<b>c</b>): inter-row obstacle avoidance stage; (<b>d</b>): obstacle avoidance end stage.</p>
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<p>Area of cutter cutting area.</p>
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<p>The influence curve of various factors on the working efficiency of the inter-plant obstacle avoidance mower. (<b>a</b>) The relationship between the forward speed of the machine and the leakage cutting rate. (<b>b</b>) The relationship between the compression speed of hydraulic cylinder and the leakage cutting rate. (<b>c</b>) Relationship between elastic coefficient of reset spring and leakage cutting rate. (<b>d</b>) The relationship between cutter diameter and leakage cutting rate.</p>
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<p>Effects of interaction of various factors on the rate of missing cutting between plants. (<b>a</b>) The interaction of AC on missing cutting G1 between plants. (<b>b</b>) The interaction of BC on missing cutting G1 between plants. (<b>c</b>) The interaction of AB on missing cutting G1 between plants.</p>
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<p>Optimal parameter combination configuration diagram.</p>
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<p>(<b>a</b>) Test site. (<b>b</b>) Obstacle avoidance mower prototype.</p>
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<p>Field test verification. (<b>a</b>) Before mowing operation. (<b>b</b>) After mowing operation (between rows). (<b>c</b>) After mowing operation (between plants).</p>
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20 pages, 6819 KiB  
Article
Analysis and Experimentation on the Motion Characteristics of a Dragon Fruit Picking Robot Manipulator
by Kairan Lou, Zongbin Wang, Bin Zhang, Qiu Xu, Wei Fu, Yang Gu and Jinyi Liu
Agriculture 2024, 14(11), 2095; https://doi.org/10.3390/agriculture14112095 - 20 Nov 2024
Viewed by 255
Abstract
Due to the complex growth positions of dragon fruit and the difficulty in robotic picking, this paper proposes a six degrees of freedom dragon fruit picking robot and investigates the manipulator’s motion characteristics to address the adaptive motion issues of the picking manipulator. [...] Read more.
Due to the complex growth positions of dragon fruit and the difficulty in robotic picking, this paper proposes a six degrees of freedom dragon fruit picking robot and investigates the manipulator’s motion characteristics to address the adaptive motion issues of the picking manipulator. Based on the agronomic characteristics of dragon fruit cultivation, the structural design of the robot and the dimensions of its manipulator were determined. A kinematic model of the dragon fruit picking robot based on screw theory was established, and the workspace of the manipulator was analyzed using the Monte Carlo method. Furthermore, a dynamic model of the manipulator based on the Kane equation was constructed. Performance experiments under trajectory and non-trajectory planning showed that trajectory planning significantly reduced power consumption and peak torque. Specifically, Joint 3’s power consumption decreased by 62.28%, and during the picking, placing, and resetting stages, the peak torque of Joint 4 under trajectory planning was 10.14 N·m, 12.57 N·m, and 16.85 N·m, respectively, compared to 12.31 N·m, 15.69 N·m, and 22.13 N·m under non-trajectory planning. This indicated that the manipulator operates with less impact and smoother motion under trajectory planning. Comparing the dynamic model simulation and actual testing, the maximum absolute error in the joint torques was −2.76 N·m, verifying the correctness of the dynamic equations. Through field picking experiments, it was verified that the machine’s picking success rate was 66.25%, with an average picking time of 42.4 s per dragon fruit. The manipulator operated smoothly during each picking process. In the study, the dragon fruit picking manipulator exhibited good stability, providing the theoretical foundation and technical support for intelligent dragon fruit picking. Full article
(This article belongs to the Section Agricultural Technology)
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<p>Cultivation model and picking method in a dragon fruit orchard. (<b>a</b>) Cultivation mode; (<b>b</b>) Picking method.</p>
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<p>Dragon fruit picking robot joint motion directions and three-dimensional structure diagram. 1. Tracked chassis; 2. Manipulator base; 3. Joint 1; 4. Link 1; 5. Joint 2; 6. Joint 3; 7. Joint 4; 8. Joint 5; 9. Joint 6; 10. Link 2; 11. Link 3; 12. Link 4; 13. Link 5; 14. Vision system; 15. End effector; 16. Motor; 17. Coupling; 18. Screw mechanism; 19. Linkage mechanism; 20. Picking bucket.</p>
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<p>The initial position of the manipulator.</p>
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<p>Schematic diagram of the manipulator.</p>
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<p>Schematic diagram of the manipulator. 1. Robot body; 2. Host computer; 3. 36 V lithium-ion battery; 4. Lower level controller; 5. Depth camera.</p>
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<p>Dragon fruit picking robot workspace composite diagram. (<b>a</b>) Three-dimensional workspace; (<b>b</b>) <span class="html-italic">xoy</span> projection plane; (<b>c</b>) <span class="html-italic">xoz</span> projection plane; (<b>d</b>) <span class="html-italic">yoz</span> projection plane.</p>
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<p>Joint 3 to Joint 6 average power consumption per second. (<b>a</b>) Joint 3; (<b>b</b>) Joint 4; (<b>c</b>) Joint 5; (<b>d</b>) Joint 6.</p>
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<p>Joint 4 velocity and torque curves for each stage. (<b>a</b>) The p1 stage rotational speed; (<b>b</b>) The p2 stage rotational speed; (<b>c</b>) The p3 stage rotational speed; (<b>d</b>) The p1 stage torque; (<b>e</b>) The p2 stage torque; (<b>f</b>) The p3 stage torque.</p>
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<p>Torque variation curves of joints during the p3 stage. (<b>a</b>) Torque based on experimental platform; (<b>b</b>) Torque based on MATLAB simulation and its error chart.</p>
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<p>Field testing of dragon fruit picking robot. (<b>a</b>) Object recognition; (<b>b</b>) Moving towards the picking position; (<b>c</b>) Shearing and twisting; (<b>d</b>) Fruit picking.</p>
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19 pages, 3522 KiB  
Article
The Relationship Between Spin Crossover (SCO) Behaviors, Cation and Ligand Motions, and Intermolecular Interactions in a Series of Anionic SCO Fe(III) Complexes with Halogen-Substituted Azobisphenolate Ligands
by Mai Hirota, Suguru Murata, Takahiro Sakurai, Hitoshi Ohta and Kazuyuki Takahashi
Molecules 2024, 29(22), 5473; https://doi.org/10.3390/molecules29225473 - 20 Nov 2024
Viewed by 368
Abstract
To investigate the halogen substitution effect on the anionic spin crossover (SCO) complexes, azobisphenolate ligands with 5,5′-dihalogen substituents from fluorine to iodine were synthesized, and their anionic FeIII complexes 1F, 1Cl, 1Br, and 1I were isolated. The temperature dependence [...] Read more.
To investigate the halogen substitution effect on the anionic spin crossover (SCO) complexes, azobisphenolate ligands with 5,5′-dihalogen substituents from fluorine to iodine were synthesized, and their anionic FeIII complexes 1F, 1Cl, 1Br, and 1I were isolated. The temperature dependence of magnetic susceptibility and crystal structure revealed that 1F, 1Cl, and 1Br are all isostructural and exhibit SCO with the rotational motion of the cation and ligands, whereas 1I shows incomplete SCO. Note that 1Cl and 1Br showed irreversible and reversible cooperative SCO transitions, respectively. Short intermolecular contacts between the FeIII complex anions were found despite Coulomb repulsions for all the complexes. The topological analysis of the electron density distributions revealed the existence of X···X halogen bonds, C–H···X, C–H···N, and C–H···O hydrogen bonds, and C–H···π interactions are evident. The dimensionality of intermolecular interactions is suggested to be responsible for the cooperative SCO transitions in 1Cl and 1Br, whereas the disorder due to the freezing of ligand rotations in 1Cl is revealed to inhibit the SCO cooperativity. Full article
(This article belongs to the Special Issue Exclusive Feature Papers in Inorganic Chemistry, 2nd Edition)
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Graphical abstract

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<p>Structural formula of 2,2′-azobisphenol <b>H<sub>2</sub>L<sup>X</sup></b> (<b>a</b>); (TMA)[Fe<sup>III</sup>(<b>L<sup>X</sup></b>)<sub>2</sub>] <b>1X</b> [TMA = tetramethylammonium cation] (<b>b</b>).</p>
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<p>The <span class="html-italic">χ</span><sub>M</sub><span class="html-italic">T</span> vs. <span class="html-italic">T</span> product for the Fe(III) complexes <b>1X</b>.</p>
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<p>ORTEP drawings of 50% probability with selected atomic numbering for the asymmetric unit. (<b>a</b>) <b>1F</b> at 90 K; (<b>b</b>) <b>1I</b> at 90 K. See text for the occupancy of the TMA cation.</p>
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<p>(<b>a</b>) Two-dimensional molecular network of the [Fe(<b>L<sup>Br</sup></b>)<sub>2</sub>]<sup>−</sup> anions in <b>1Br</b> along the <span class="html-italic">a</span> axis at 90 K. (<b>b</b>) Molecular arrangement between two-dimensional networks in <b>1Br</b> along the <span class="html-italic">b</span> axis at 90 K. Letters P–V with or without a prime are a label of the [Fe(<b>L<sup>X</sup></b>)<sub>2</sub>]<sup>−</sup> anion molecules with fractional coordinates described in the text and <a href="#molecules-29-05473-t003" class="html-table">Table 3</a>. Dot lines indicate selected intermolecular short contacts between the central reference [Fe(<b>L<sup>X</sup></b>)<sub>2</sub>]<sup>−</sup> anion molecule and the labeled one.</p>
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<p>(<b>a</b>) Two-dimensional molecular network of [Fe(<b>L<sup>I</sup></b>)<sub>2</sub>]<sup>−</sup> anions in <b>1I</b> at 90 K. (<b>b</b>) Molecular arrangement between two-dimensional networks in <b>1I</b> along the <span class="html-italic">c</span> axis at 90 K. Letters P–V with or without a prime are a label of the [Fe(<b>L<sup>I</sup></b>)<sub>2</sub>]<sup>−</sup> anion molecules with fractional coordinates described in the text and <a href="#molecules-29-05473-t004" class="html-table">Table 4</a>. Dot lines indicate selected intermolecular short contacts between the central reference [Fe(<b>L<sup>I</sup></b>)<sub>2</sub>]<sup>−</sup> anion molecule and the labeled one.</p>
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<p>Synthesis of halogen-substituted azp ligands (<b>H<sub>2</sub>L<sup>X</sup></b>). * The yields of <b>4Cl</b> and <b>H<sub>2</sub>L<sup>Cl</sup></b> in the literature [<a href="#B43-molecules-29-05473" class="html-bibr">43</a>] were 41% and 56%, respectively.</p>
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17 pages, 8959 KiB  
Review
Laboratory Assessment of Manual Wheelchair Propulsion
by Bartosz Wieczorek and Maciej Sydor
Appl. Sci. 2024, 14(22), 10737; https://doi.org/10.3390/app142210737 - 20 Nov 2024
Viewed by 198
Abstract
Self-propelled manual wheelchairs offer several advantages over electric wheelchairs, including promoting physical activity and requiring less maintenance due to their simple design. While theoretical analyses provide valuable insights, laboratory testing remains the most reliable method for evaluating and improving the efficiency of manual [...] Read more.
Self-propelled manual wheelchairs offer several advantages over electric wheelchairs, including promoting physical activity and requiring less maintenance due to their simple design. While theoretical analyses provide valuable insights, laboratory testing remains the most reliable method for evaluating and improving the efficiency of manual wheelchair drives. This article reviews and analyzes the laboratory methods for assessing the efficiency of wheelchair propulsion documented in the scientific literature: (1) A wheelchair dynamometer that replicates real-world driving scenarios, quantifies the wheelchair’s motion characteristics, and evaluates the physical exertion required for propulsion. (2) Simultaneous measurements of body position, motion, and upper limb EMG data to analyze biomechanics. (3) A method for determining the wheelchair’s trajectory based on data from the dynamometer. (4) Measurements of the dynamic center of mass (COM) of the human–wheelchair system to assess stability and efficiency; and (5) data analysis techniques for parameterizing large datasets and determining the COM. The key takeaways include the following: (1) manual wheelchairs offer benefits over electric ones but require customization to suit individual user biomechanics; (2) the necessity of laboratory-based ergometer testing for optimizing propulsion efficiency and safety; (3) the feasibility of replicating real-world driving scenarios in laboratory settings; and (4) the importance of efficient data analysis techniques for interpreting biomechanical studies. Full article
(This article belongs to the Section Biomedical Engineering)
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<p>Subsystems of a manual wheelchair (<span class="html-italic">Freeasy</span> model, manufactured by Cosmotech, Gliwice, Poland; source: own study).</p>
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<p>Information flow diagram for wheelchair propulsion biomechanics study on the stationary roller dynamometer (source: [<a href="#B34-applsci-14-10737" class="html-bibr">34</a>]).</p>
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<p>View of the stationary roller dynamometer with details of the most essential elements (own study): 1—support frame, 2—strain gauges, 3—weighing pan, 4—linear guides, 5—clamping system, 6—traction rollers, 7—BLDC motor, 8—encoder.</p>
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<p>Wheelchair secured to the stationary roller dynamometer (source: own study): (<b>A</b>)—traction rollers, (<b>B</b>)—weight-scale lever, (<b>C</b>)—safety pin, (<b>D</b>)—clamps securing the wheelchair frame, (<b>E</b>)—lever arm height adjuster, (<b>F</b>)—fastened wheelchair frame.</p>
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<p>Stroke patterns of the wheelchair propulsion (based on the methodology outlined in [<a href="#B35-applsci-14-10737" class="html-bibr">35</a>]).</p>
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<p>Measurement apparatus used in the study: (<b>a</b>)—camera, (<b>b</b>)—illuminating lamp, (<b>c</b>)—boom, (<b>d</b>)—AruCo marker, (<b>e</b>)—EMG device (source: [<a href="#B42-applsci-14-10737" class="html-bibr">42</a>]).</p>
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<p>Relative error (<b>A</b>) and number of detection points (<b>B</b>) as a function of marker speed (adapted from [<a href="#B45-applsci-14-10737" class="html-bibr">45</a>]).</p>
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<p>Determination of the turning radius <span class="html-italic">R</span>, using the trapezoid method based on known values of left wheel speed <span class="html-italic">v</span><sub>L</sub>, right wheel speed <span class="html-italic">v</span><sub>P</sub>, and wheelbase <span class="html-italic">L</span> (source: [<a href="#B47-applsci-14-10737" class="html-bibr">47</a>]).</p>
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<p>The partitioning of the wheelchair trajectory into trapezoidal segments (source: [<a href="#B47-applsci-14-10737" class="html-bibr">47</a>]): (<b>A</b>)—distance covered in the first iteration, (<b>B</b>)—distance covered in the second iteration, (<b>C</b>)—a combination of distances covered in the analyzed iterations, (<b>D</b>)—trajectory determined based on the specified iterations.</p>
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<p>Schematic diagram of the test stand with the reactions determined using strain gauge scales in four measurement planes (source: [<a href="#B34-applsci-14-10737" class="html-bibr">34</a>]).</p>
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<p>Schematic diagrams of the beams showing the position of the center of mass (COM) of the person in the wheelchair on each of the four measurement planes (source: [<a href="#B34-applsci-14-10737" class="html-bibr">34</a>]).</p>
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<p>Schematic diagram of the method for determining the position of the center of mass (COM) in the XY plane (source: [<a href="#B34-applsci-14-10737" class="html-bibr">34</a>]).</p>
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<p>Schematic illustration of the method of replacing an arbitrary set of points (<b>a</b>) with an ellipse defining the area of points on the analyzed plane (<b>b</b>) (source: [<a href="#B57-applsci-14-10737" class="html-bibr">57</a>]).</p>
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22 pages, 7322 KiB  
Article
Design and Parameter Optimization of a Rigid–Flexible Coupled Rod Tooth Threshing Device for Ratoon Rice Based on MBD-DEM
by Weijian Liu, Xuegeng Chen and Shan Zeng
Agriculture 2024, 14(11), 2083; https://doi.org/10.3390/agriculture14112083 - 19 Nov 2024
Viewed by 285
Abstract
To solve the problem of the high loss rate of threshing devices during the mechanical harvesting of ratoon rice, we propose a method using the principle of rigid–flexible coupling in this paper to reduce losses. Through analysis of the forces and collisions on [...] Read more.
To solve the problem of the high loss rate of threshing devices during the mechanical harvesting of ratoon rice, we propose a method using the principle of rigid–flexible coupling in this paper to reduce losses. Through analysis of the forces and collisions on ratoon rice grains during the threshing process, it has been confirmed that changing the structure and materials of the threshing contact components can effectively reduce grain loss. A rigid–flexible coupling rod tooth was designed, and the overall structural parameters of the device were determined based on force analysis results and dimensional boundary conditions. The MBD-DEM coupling method was used to simulate the threshing process, and the force conditions of the threshing rod teeth and threshing drum were obtained. The influence of the feeding amount and of the flexible body thickness on the crushing of ratoon rice grains was analyzed. In order to obtain the device’s optimal parameter combination, a three-factor quadratic regression orthogonal rotation combination experiment was conducted with drum speed, flexible body thickness, and rod tooth length as experimental factors. The optimization results showed that when the drum speed, flexible body thickness, and rod tooth length were 684 r/min, 3.86 mm, and 72.7 mm, respectively, the crushing rate, entrainment loss rate, and uncleaned rate were 1.260%, 2.132%, and 1.241%, respectively. The bench test showed that it is feasible to use the MBD–DEM coupling method to measure the motion and force of ratoon rice. The rigid–flexible coupling threshing device can reduce the grain crushing rate while ensuring grain cleanliness. Compared with traditional threshing devices, the crushing rate and entrainment loss rate of the rigid–flexible coupling threshing device were reduced by 55.7% and 27.5%, respectively. The research results can provide a reference for the design of threshing devices for ratoon rice harvesters. Full article
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<p>Schematic diagram of grain stress. (<b>a</b>) Ratoon rice grains in contact with rod teeth; (<b>b</b>) ratoon rice grains with no contact with the rod teeth. Note: <span class="html-italic">s</span><sub>1</sub> is the shear force of the stem on ratoon rice grains, N; <span class="html-italic">p</span><sub>1</sub> is the pressure exerted by the stem on the ratoon rice grains, N; <span class="html-italic">ox</span><sub>1</sub><span class="html-italic">y</span><sub>1</sub> is the floating coordinate system; <span class="html-italic">n</span><sub>1</sub> is the impact force of the rod teeth on the grain, N; <span class="html-italic">n</span><sub>1</sub><span class="html-italic">x</span> is a component of <span class="html-italic">n</span><sub>1</sub> in the direction of <span class="html-italic">x</span><sub>1</sub>, N; <span class="html-italic">n</span><sub>1<span class="html-italic">y</span></sub> is a component of <span class="html-italic">n</span>1 in the direction of <span class="html-italic">y</span><sub>1</sub>, N; <span class="html-italic">q</span><sub>2</sub> is the interaction force between adjacent grains, N; <span class="html-italic">q</span><sub>2<span class="html-italic">x</span></sub> is a component of <span class="html-italic">q</span><sub>2</sub> in the direction of <span class="html-italic">x</span><sub>1</sub>, N; <span class="html-italic">q</span><sub>2<span class="html-italic">y</span></sub> is a component of <span class="html-italic">q</span><sub>2</sub> in the direction of <span class="html-italic">y</span><sub>1</sub>, N; <span class="html-italic">s<sub>n</sub></span> is the shear force of the stem on ratoon rice grains, N; <span class="html-italic">t<sub>n</sub></span> is the tensile force of the stem on the grain, N; <span class="html-italic">ox<sub>n</sub>y<sub>n</sub></span> is the floating coordinate system; <span class="html-italic">q<sub>n</sub></span><sub>−1</sub> is the pressure from the ratoon rice grains below, N; <span class="html-italic">q</span><sub>(<span class="html-italic">n</span>−1)<span class="html-italic">x</span></sub> is a component of <span class="html-italic">q<sub>n</sub></span><sub>−1</sub> in the direction of <span class="html-italic">x<sub>n</sub></span>, N; <span class="html-italic">q</span><sub>(<span class="html-italic">n</span>−1)<span class="html-italic">y</span></sub> is a component of <span class="html-italic">q</span><span class="html-italic"><sub>n</sub></span><sub>−1</sub> in the direction of <span class="html-italic">y<sub>n</sub></span>, N; <span class="html-italic">q<sub>n+</sub></span><sub>1</sub> is the pressure from the ratoon rice grains above, N; <span class="html-italic">q</span><sub>(<span class="html-italic">n</span>+1)<span class="html-italic">x</span></sub> is a component of <span class="html-italic">q<sub>n+</sub></span><sub>1</sub> in the direction of <span class="html-italic">x<sub>n</sub></span>, N; <span class="html-italic">q</span><sub>(<span class="html-italic">n</span>+1)<span class="html-italic">y</span></sub> is a component of <span class="html-italic">q<sub>n+</sub></span><sub>1</sub> in the direction of <span class="html-italic">y<sub>n</sub></span>, N.</p>
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<p>Simplified model of stress on ratoon rice grains during collision. Note: <span class="html-italic">v</span><sub>0</sub> is the initial velocity when the ratoon rice grain collides with the rod teeth, m·s<sup>−1</sup>; <span class="html-italic">c</span> is the damping coefficient of the system, N·s ·m<sup>−1</sup>; <span class="html-italic">k</span> is the stiffness coefficient of the rod teeth, N·m<sup>−1</sup>; <span class="html-italic">k</span><sub>0</sub> is the stiffness coefficient of the ratoon rice grains, N·m<sup>−1</sup>; <span class="html-italic">m</span> is the mass of the ratoon rice grains, g; <span class="html-italic">y</span><sub>0</sub> is the initial point of collision; and <span class="html-italic">y</span> is the initial velocity direction of ratoon rice grains.</p>
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<p>Overall structure of the device. (1) Transmission structure; (2) motor; (3) motor adjustment bracket; (4) splice box; (5) threshing drum; (6) flow guide; (7) concave screen; (8) threshing rod teeth. (<b>a</b>) Three-dimensional model of threshing device; (<b>b</b>) Two-dimensional model of threshing device.</p>
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<p>The structure diagram of threshing device. (1) Fender; (2) spiral feeding device; (3) rigid-flexible coupling rod teeth; (4) spoke rod; (5) spoke plate; (6) drum shaft.</p>
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<p>Analysis of stress on rice plants. Note: <span class="html-italic">d</span> is the front section’s diameter, mm; <span class="html-italic">L</span> is the length of the screw feed head, mm; <span class="html-italic">D</span> is the diameter of the rear end, mm; <span class="html-italic">v<sub>x</sub></span> is the axial feeding speed of rice plants, kg/s; and <span class="html-italic">T<sub>x</sub></span> is the axial thrust.</p>
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<p>The structure diagrams of three rod teeth. (<b>a</b>) Rigid–flexible coupling teeth; (<b>b</b>) flexible teeth; (<b>c</b>) rigid teeth.</p>
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<p>Structure diagram of the threshing device cover plate.</p>
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<p>Structure diagram of concave plate sieve.</p>
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<p>Model establishment. (<b>a</b>) Ratooning rice plants; (<b>b</b>) ratoon rice plant EDEM model.</p>
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<p>Threshing process simulation. (<b>a</b>) Ratoon rice plants have just entered the threshing device. (<b>b</b>) Threshing device is filled with material. Note: the blue color in the figure represents ratoon rice grains, and the yellow color represents straw.</p>
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<p>The impact force on the rod teeth. Note: rigid rod teeth: black line; flexible rod teeth: blue line; rigid–flexible coupling rod teeth: red line.</p>
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<p>Distribution of ratoon rice grains in the collection box.</p>
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<p>Force fluctuation diagram of rod teeth.</p>
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<p>Force fluctuation diagram of rod teeth under different flexible body thicknesses.</p>
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<p>Threshing performance test. (1) Threshing drum. (2) Bench. (3) Motor. (4) Conveyor. (5) Motor inverter. (6) Conveyor belt inverter.</p>
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<p>Effects of interactive factors on the crushing rate. (<b>a</b>) The interaction between drum speed and rod tooth length. (<b>b</b>) The interaction between drum speed and flexible body thickness. (<b>c</b>) The interaction between rod tooth length and flexible body thickness.</p>
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18 pages, 6972 KiB  
Article
The Design and Experimental Research on a High-Frequency Rotary Directional Valve
by Shunming Hua, Siqiang Liu, Zhuo Qiu, Xiaojun Wang, Xuechang Zhang and Huijuan Zhang
Processes 2024, 12(11), 2600; https://doi.org/10.3390/pr12112600 - 19 Nov 2024
Viewed by 257
Abstract
A directional valve is a core component of the electro-hydraulic shakers in fatigue testing machines, controlling the cylinder or motor that drives the piston for reciprocating linear or rotary motion. In this article, a high-speed rotating directional valve with a symmetrical flow channel [...] Read more.
A directional valve is a core component of the electro-hydraulic shakers in fatigue testing machines, controlling the cylinder or motor that drives the piston for reciprocating linear or rotary motion. In this article, a high-speed rotating directional valve with a symmetrical flow channel layout is designed to optimize the force on the valve core of the directional valve. A comparative analysis is conducted on the flow capacity of valve ports with different shapes. A steady-state hydrodynamic mathematical model is established for the valve core, the theoretical analysis results of which are verified through a Computational Fluid Dynamics (CFD) simulation of the fluid domain inside the directional valve. A prototype of the rotatory directional valve is designed and manufactured, and an experimental platform is built to measure the hydraulic force acting on the valve core to verify the performance of the valve. The displacement curves at different commutation frequencies are also obtained. The experimental results show that the symmetrical flow channel layout can significantly optimize the hydraulic force during the movement of the valve core. Under a pressure of 1 MPa, the hydraulic cylinder driven by the prototype can achieve a sinusoidal curve output with a maximum frequency of 60 Hz and an amplitude of 2.5 mm. The innovation of this design lies in the creation of a directional valve with a symmetric flow channel layout. The feasibility of the design is verified through modeling, simulation, and experimentation, and it significantly optimizes the hydraulic forces acting on the spool. It provides us with the possibility to further improve the switching frequency of hydraulic valves and has important value in engineering applications. Full article
(This article belongs to the Section Manufacturing Processes and Systems)
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<p>Structure of rotary directional valve.</p>
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<p>Valve port shapes.</p>
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<p>Relationship between circular orifice area and valve core angle.</p>
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<p>Relationship between triangle orifice area and valve core angle.</p>
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<p>Relationship between square orifice area and valve core angle.</p>
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<p>The average flow area of the valve port and its ratio to the maximum flow area.</p>
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<p>Fluid domain division.</p>
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<p>Mesh quality test results.</p>
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<p>Cloud diagrams of the valve port velocity with different port openings. (<b>a</b>) The inlet I is used as the pressure inlet. (<b>b</b>) The inlet II is used as the pressure inlet.</p>
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<p>Vector diagrams of liquid flow at different valve openings. (<b>a</b>) The inlet I is used as the pressure inlet. (<b>b</b>) The inlet II is used as the pressure inlet.</p>
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<p>Jet angle and spool torque at different rotation angles. (<b>a</b>) Jet angle curves. (<b>b</b>) Spool torque curves.</p>
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<p>Hydraulic simulation system diagram.</p>
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<p>System flow rate and cylinder amplitude at different commutation frequencies.</p>
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<p>Flow rate and cylinder amplitude at different pressures.</p>
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<p>Flow rate and cylinder amplitude at different loads.</p>
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<p>Test platform. (<b>a</b>) Overview of experimental system. (<b>b</b>) Prototype and sensors.</p>
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<p>Hydraulic cylinder displacement curves at different commutation frequencies.</p>
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<p>The relationship between the steady-state hydraulic torque and the spool rotation angle.</p>
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<p>The torque of the spool at different pressures.</p>
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30 pages, 8578 KiB  
Article
Around-Body Versus On-Body Motion Sensing: A Comparison of Efficacy Across a Range of Body Movements and Scales
by Katelyn Rohrer, Luis De Anda, Camila Grubb, Zachary Hansen, Jordan Rodriguez, Greyson St Pierre, Sara Sheikhlary, Suleyman Omer, Binh Tran, Mehrail Lawendy, Farah Alqaraghuli, Chris Hedgecoke, Youssif Abdelkeder, Rebecca C. Slepian, Ethan Ross, Ryan Chung and Marvin J. Slepian
Bioengineering 2024, 11(11), 1163; https://doi.org/10.3390/bioengineering11111163 - 19 Nov 2024
Viewed by 346
Abstract
Motion is vital for life. Currently, the clinical assessment of motion abnormalities is largely qualitative. We previously developed methods to quantitatively assess motion using visual detection systems (around-body) and stretchable electronic sensors (on-body). Here we compare the efficacy of these methods across predefined [...] Read more.
Motion is vital for life. Currently, the clinical assessment of motion abnormalities is largely qualitative. We previously developed methods to quantitatively assess motion using visual detection systems (around-body) and stretchable electronic sensors (on-body). Here we compare the efficacy of these methods across predefined motions, hypothesizing that the around-body system detects motion with similar accuracy as on-body sensors. Six human volunteers performed six defined motions covering three excursion lengths, small, medium, and large, which were analyzed via both around-body visual marker detection (MoCa version 1.0) and on-body stretchable electronic sensors (BioStamp version 1.0). Data from each system was compared as to the extent of trackability and comparative efficacy between systems. Both systems successfully detected motions, allowing quantitative analysis. Angular displacement between systems had the highest agreement efficiency for the bicep curl and body lean motion, with 73.24% and 65.35%, respectively. The finger pinch motion had an agreement efficiency of 36.71% and chest abduction/adduction had 45.55%. Shoulder abduction/adduction and shoulder flexion/extension motions had the lowest agreement efficiencies with 24.49% and 26.28%, respectively. MoCa was comparable to BioStamp in terms of angular displacement, though velocity and linear speed output could benefit from additional processing. Our findings demonstrate comparable efficacy for non-contact motion detection to that of on-body sensor detection, and offers insight as to the best system selection for specific clinical uses based on the use-case of the desired motion being analyzed. Full article
(This article belongs to the Special Issue Biomechanics and Motion Analysis)
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<p>Outlined steps for recording the runs for both MoCa and BioStamp. The procedure covers the setting up of the area for recording the data transformation into graphs.</p>
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<p>Locations of MoCa markers per six predefined motions: (<b>a</b>) finger pinch movement, (<b>b</b>) bicep curl movement, (<b>c</b>) chest abduction/adduction movement, (<b>d</b>) shoulder abduction/adduction movement, (<b>e</b>) shoulder flexion/extension movement, and (<b>f</b>) body lean movement. Sequential images outline the complete movement excursion per motion with variously colored MoCa markers indicating marker positions.</p>
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<p>Location of BioStamp placement per motion categorized by excursion length (small, medium, and large). Small movements require two stamps: (<b>a</b>) index finger and (<b>b</b>) thumb. Medium movements require three stamps placed on (<b>c</b>) biceps, (<b>d</b>) brachioradialis, and (<b>e</b>) distal anterior forearm. Large movements require the most stamps with stamps placed on the (<b>f</b>) medial deltoid, (<b>g</b>) the cervical spine, (<b>h</b>) mid-thoracic spine, (<b>i</b>) triceps, and (<b>j</b>) biceps femoris.</p>
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<p>Complete data conversion process, from raw MoCa data to the final endpoint variables, subplots (<b>a–d</b>) representing data from the same trial. (<b>a</b>) Positional tracking of individual MoCa markers on the hand, elbow, and shoulder. (<b>b</b>) Angular displacement calculated by applying the cosine function to the angles formed by the markers. (<b>c</b>) Angular velocity derived from the original angles. (<b>d</b>) Linear speed calculated from positional data.</p>
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<p>Full data conversion steps from obtaining raw BioStamp data into the final endpoint variables subplots (<b>a</b>–<b>d</b>) are from the same trial. (<b>a</b>) Marker tracking collected along the X, Y, and Z axes in pixels. (<b>b</b>) Angular displacement obtained through further integration. (<b>c</b>) Angular velocity integrated from BioStamp’s output acceleration data. (<b>d</b>) Linear speed obtained from acceleration output using 3-dimensional Pythagorean theorem.</p>
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<p>MoCa−captured angular displacement for all six motions: (<b>a</b>) finger pinch, (<b>b</b>) bicep curl, (<b>c</b>) chest abduction/adduction, (<b>d</b>) shoulder flexion/extension, (<b>e</b>) shoulder abduction/adduction, and (<b>f</b>) body lean.</p>
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<p>BioStamp−captured angular displacement for all six motions: (<b>a</b>) finger pinch, (<b>b</b>) bicep curl, (<b>c</b>) chest abduction/adduction, (<b>d</b>) shoulder flexion/extension, (<b>e</b>) shoulder abduction/adduction, and (<b>f</b>) body lean.</p>
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<p>Average maximum angular displacement per motion categorized by motion size: (<b>a</b>) small, (<b>b</b>) medium, and (<b>c</b>) large. MoCa (blue) and BioStamp (orange) are compared side by side.</p>
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<p>Bland−Altman plots of angular displacement between MoCa and BioStamp per motion categorized by motion size: small, medium, and large. (<b>a</b>) Bland−Altman plot of finger pinch movement. (<b>b</b>) Bland−Altman plot of bicep curl movement. (<b>c</b>) Bland−Altman plot of chest abduction/adduction movement. (<b>d</b>) Bland−Altman plot of shoulder flexion/extension movement. (<b>e</b>) Bland−Altman plot of shoulder abduction/adduction movement. (<b>f</b>) Bland−Altman plot of body lean movement.</p>
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<p>Bland−Altman plots of angular velocity between MoCa and BioStamp per motion categorized by motion size: small, medium, and large. (<b>a</b>) Bland−Altman plot of finger pinch movement with the 5% percentile of differences denoted by the red line, and the 95% percentile of differences denoted by green line. (<b>b</b>) Bland−Altman plot of bicep curl movement with the 5% percentile of differences denoted by the red line, and the 95% percentile of differences denoted by green line. (<b>c</b>) Bland−Altman plot of chest abduction/adduction movement, with the linear regression shown in red, the lower limit of agreement in yellow, and the upper limit of agreement in green. (<b>d</b>) Bland−Altman plot of shoulder flexion/extension movement, with the linear regression shown in red, the lower limit of agreement in yellow, and the upper limit of agreement in green. (<b>e</b>) Bland–Altman plot of shoulder abduction/adduction movement. (<b>f</b>) Bland−Altman plot of body lean movement, with the linear regression shown in red, the lower limit of agreement in yellow, and the upper limit of agreement in green.</p>
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<p>Bland−Altman plots of between MoCa and BioStamp per motion categorized by motion size: small, medium, and large. Blue points indicate single measurement pairs between MoCa and BioStamp. The red line indicates the linear regression, with the lower limit of agreement in yellow, and the upper limit of agreement in green. (<b>a</b>) Bland–Altman plot of the finger pinch movement. (<b>b</b>) Bland–Altman plot of the bicep curl movement. (<b>c</b>) Bland–Altman plot of the chest abduction/adduction movement. (<b>d</b>) Bland–Altman plot of the shoulder flexion/extension movement. (<b>e</b>) Bland–Altman plot of the shoulder abduction/adduction movement (<b>f</b>) Bland–Altman plot of the body lean movement.</p>
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<p>Agreement efficiency (%) for each motion, grouped by motion size categories, small, medium, and large.</p>
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<p>Bland−Altman plot between MoCa and BioStamp across endpoint variables. (<b>a</b>) Bland–Altman plot of angular displacement values. (<b>b</b>) Bland−Altman plot of linear speed values. (<b>c</b>) Bland–Altman plot of angular velocity values.</p>
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<p>(<b>a</b>) Pearson correlation coefficients for angular displacement between MoCa and BioStamp across all predefined motions. (<b>b</b>) Pearson correlation coefficients for angular velocity between MoCa and BioStamp across all motions. (<b>c</b>) Pearson correlation coefficients for linear speed between MoCa and BioStamp across all motions. (<b>d</b>) Average Pearson correlation coefficients for MoCa versus BioStamp across three metrics: angular displacement, angular velocity, and linear speed.</p>
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<p>Comparison between slow (orange) and fast (teal) runs. (<b>A</b>) Average angular displacement comparison. (<b>B</b>) Average angular velocity comparison. (<b>C</b>) Average linear speed comparison. (<b>D</b>) Pearson correlation coefficients for angular displacement, angular velocity, and linear speed.</p>
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11 pages, 4326 KiB  
Article
Simulation of Small-Break Loss-of-Coolant Accident Using the RELAP5 Code with an Improved Wall Drag Partition Model for Bubbly Flow
by Young Hwan Lee, Nam Kyu Ryu and Byoung Jae Kim
Energies 2024, 17(22), 5777; https://doi.org/10.3390/en17225777 - 19 Nov 2024
Viewed by 276
Abstract
The RELAP5 code is a computational tool designed for transient simulations of light water reactor coolant systems under hypothesized accident conditions. The original wall drag partition model in the RELAP5 code has a problem in that the bubble velocity is predicted to be [...] Read more.
The RELAP5 code is a computational tool designed for transient simulations of light water reactor coolant systems under hypothesized accident conditions. The original wall drag partition model in the RELAP5 code has a problem in that the bubble velocity is predicted to be faster than the water velocity in the fully developed flow in a constant-area channel. The wall drag partition model, based on the wetted perimeter concept, proves insufficient for accurately modeling bubbly flows. In this study, the wall drag partition model was modified to account for the physical motion of fluid particles. After that, the modified RELAP5 code was applied to predict the SBLOCA of a full-scale nuclear power plant. Considering the SBLOCA scenario, the behavior change in the loop seal clearing phenomenon was clearly shown in the analysis by the model change. Upon the termination of natural circulation, the loop seals were cleared, allowing the steam trapped within the system to discharge through the break. The modified model was confirmed to have an impact at this time. It mainly affected the timing and shape of the loop seal clearing and delayed the overall progress of the accident. It was observed that the flow rate of the bubbly phase decreased as the modified model accounted for wall friction during dispersed flow in the horizontal section, impacting the two-phase flow behavior at the conclusion of the natural circulation phase. Full article
(This article belongs to the Section B4: Nuclear Energy)
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<p>Nodding diagram of the horizontal channel.</p>
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<p>Water and bubble velocities when the original wall drag model was used.</p>
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<p>Water and bubble velocities when the modified wall drag model was used.</p>
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<p>Schematic of APR1400.</p>
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<p>Reactor pressure.</p>
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<p>Break flow.</p>
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<p>Core inlet flow.</p>
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<p>Collapsed water level in the core.</p>
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<p>Loop seal steam flow rate—original.</p>
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<p>Loop seal steam flow rate—modified.</p>
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<p>Peak cladding temperature.</p>
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14 pages, 4021 KiB  
Article
AI-Aided Gait Analysis with a Wearable Device Featuring a Hydrogel Sensor
by Saima Hasan, Brent G. D’auria, M. A. Parvez Mahmud, Scott D. Adams, John M. Long, Lingxue Kong and Abbas Z. Kouzani
Sensors 2024, 24(22), 7370; https://doi.org/10.3390/s24227370 - 19 Nov 2024
Viewed by 280
Abstract
Wearable devices have revolutionized real-time health monitoring, yet challenges persist in enhancing their flexibility, weight, and accuracy. This paper presents the development of a wearable device employing a conductive polyacrylamide–lithium chloride–MXene (PLM) hydrogel sensor, an electronic circuit, and artificial intelligence (AI) for gait [...] Read more.
Wearable devices have revolutionized real-time health monitoring, yet challenges persist in enhancing their flexibility, weight, and accuracy. This paper presents the development of a wearable device employing a conductive polyacrylamide–lithium chloride–MXene (PLM) hydrogel sensor, an electronic circuit, and artificial intelligence (AI) for gait monitoring. The PLM sensor includes tribo-negative polydimethylsiloxane (PDMS) and tribo-positive polyurethane (PU) layers, exhibiting extraordinary stretchability (317% strain) and durability (1000 cycles) while consistently delivering stable electrical signals. The wearable device weighs just 23 g and is strategically affixed to a knee brace, harnessing mechanical energy generated during knee motion which is converted into electrical signals. These signals are digitized and then analyzed using a one-dimensional (1D) convolutional neural network (CNN), achieving an impressive accuracy of 100% for the classification of four distinct gait patterns: standing, walking, jogging, and running. The wearable device demonstrates the potential for lightweight and energy-efficient sensing combined with AI analysis for advanced biomechanical monitoring in sports and healthcare applications. Full article
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<p>Schematic circuit diagram of the wearable device.</p>
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<p>Photographs of the enclosure with the electronic circuit. (<b>a</b>) Enclosed. (<b>b</b>) and (<b>c</b>) Internal components. (<b>d</b>) Weight (19 g).</p>
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<p>Knee brace. (<b>a</b>) Illustration of a human body wearing the knee brace. (<b>b</b>) Photograph of the knee brace with the wearable device. (<b>c</b>) Weight of the wearable device.</p>
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<p>Preparation of the PLM sensor. (<b>a</b>) Preparation of the PLM hydrogel (left); internal morphology of the hydrogel (right). (<b>b</b>) PDMS preparation (left); assembly of the PLM sensor (right).</p>
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<p>Working mechanism of the PLM sensor-based gait monitoring system. (<b>a</b>) Working principle of the PLM sensor during a stretch–release cycle. (<b>b</b>) System-level block diagram of the gait monitoring system, showing analog signals from the four activities (blue), processing and wireless transmission (green), the digital signal output, and the machine learning algorithm run by the computer (yellow).</p>
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<p>Mechanical and electrical performance of the PLM sensor. (<b>a</b>) Tensile stress–strain characteristics. (<b>b</b>) Generated voltage signals with different tensile strains (20%, 40%, 60%, 80%, and 100%). (<b>c</b>) Generated voltage signals at different stretching rates (from 100 to 500 mm min<sup>−1</sup>) at a fixed strain of 80%. (<b>d</b>) Mechanical durability test for up to 1000 continuous stretch–release cycles at 80% strain.</p>
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<p>Gait identification using the 1D CNN model. (<b>a</b>) Voltage acquisition from four gait patterns: standing, walking, jogging, and running. (<b>b</b>) Model structure. (<b>c</b>) Model accuracy. (<b>d</b>) Model loss. (<b>e</b>) Confusion map of the accuracy prediction for the four activities.</p>
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11 pages, 2870 KiB  
Article
Safety and Effectiveness of a Novel Liposomal Intra-Articular Lubricant in Symptomatic Knee Osteoarthritis: A First-in-Human Study
by Shai Shemesh, Oleg Dolkart, Ronit Goldberg, Sabrina Jahn, Amal Khoury, Yaniv Warschawski, Haggai Schermann, Moshe Salai, Gaby Agar and Michael Drexler
J. Clin. Med. 2024, 13(22), 6956; https://doi.org/10.3390/jcm13226956 - 18 Nov 2024
Viewed by 421
Abstract
Background/Objectives: Osteoarthritis (OA) is a common disease that affects almost half the population at some point in their lives, causing pain and decreased functional capacity. New conservative treatment modalities are being proposed to provide symptomatic relief and delay surgical intervention. This study aimed [...] Read more.
Background/Objectives: Osteoarthritis (OA) is a common disease that affects almost half the population at some point in their lives, causing pain and decreased functional capacity. New conservative treatment modalities are being proposed to provide symptomatic relief and delay surgical intervention. This study aimed at evaluating the safety of the novel liposomal boundary lubricant, injected intra-articularly in patients with moderate knee OA. Additionally, the effect on the functionality and life quality was assessed. Methods: Eighteen of the twenty screened subjects met inclusion criteria and were enrolled in the study. After receiving a single IA injection of AqueousJoint, patients were prospectively evaluated at baseline and at 2, 4, 8, 12, and 26 weeks. Numeric Pain Rating Scale (NRS), Knee injury and Osteoarthritis Outcome Score (KOOS), Short Form Health Survey (SF12) and range of motion were also recorded. Results: The final analysis was conducted on 18 subjects. No adverse events related to the investigational product were observed in the study. No serious adverse events were observed at all. A significant decrease in pain was demonstrated at all time points vs. baseline (Friedman X2 = 35.08, p < 0.001). Significant improvement was demonstrated in KOOS pain, symptoms, sports, and ADL subscales (p < 0.001). Conclusions: Despite a relatively small sample, it was demonstrated that single IA AqueousJoint injection is a safe procedure, resulting in significant pain reduction, higher ADL score, and higher KOOS sport scores. The effects lasted up to 6 months. Full article
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<p>CONSORT.</p>
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<p>(<b>A</b>) NRS scores by visits; (<b>B</b>) change in NRS from baseline. Values are presented as mean ± SD.</p>
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<p>(<b>A</b>) KOOS symptoms by visits; (<b>B</b>) change in KOOS symptoms from baseline.</p>
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<p>(<b>A</b>) KOOS pain by visits; (<b>B</b>) change in KOOS pain from baseline. Values are presented as mean ± SD.</p>
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<p>(<b>A</b>) KOOS ADL by visits; (<b>B</b>) change in KOOS ADL from baseline. Values are presented as mean ± SD.</p>
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<p>(<b>A</b>) KOOS sport by visits; (<b>B</b>) change in KOOS sport from baseline. Values are presented as mean ± SD.</p>
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<p>(<b>A</b>) KOOS QOL by visits; (<b>B</b>) change in KOOS QOL from baseline. Values are presented as mean ± SD.</p>
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