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Keywords = Magnetorheological (MR) Fluid

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28 pages, 30126 KiB  
Article
Numerical Analysis of the Vehicle Damping Performance of a Magnetorheological Damper with an Additional Flow Energy Path
by Minje Kim, Seungin Yoo, Dongjin Yoon, Chanyoung Jin, Seongjae Won and Jinwook Lee
Appl. Sci. 2024, 14(22), 10575; https://doi.org/10.3390/app142210575 (registering DOI) - 16 Nov 2024
Viewed by 311
Abstract
Vehicles experience various frequency excitations from road surfaces. Recent research has focused on active dampers that adapt their damping forces according to these conditions. However, traditional magnetorheological (MR) dampers face a “block-up phenomenon” that limits their effectiveness. To address this, additional flow-type MR [...] Read more.
Vehicles experience various frequency excitations from road surfaces. Recent research has focused on active dampers that adapt their damping forces according to these conditions. However, traditional magnetorheological (MR) dampers face a “block-up phenomenon” that limits their effectiveness. To address this, additional flow-type MR dampers have been proposed, although revised designs are required to accommodate changes in damping force characteristics. This study investigates the damping performance of MR dampers with an additional flow path to enhance the vehicle ride quality. An optimization model was developed based on fluid dynamics equations and analyzed using electromagnetic simulations in ANSYS Maxwell software. Vibration analysis was conducted using AMESim by applying a sinusoidal road surface model with various frequencies. Results show that the optimized diameter of the additional flow path obtained from the analysis was 1.1 mm, and it was shown that the total damping force variation at low piston velocities decreased by approximately 56% compared to conventional MR dampers. Additionally, vibration analysis of the MR damper with the optimized additional flow path diameter revealed that at 30 km/h, 37.9% acceleration control was achievable, at 60 km/h, 18.7%, and at 90 km/h, 7.73%. This demonstrated the resolution of the block-up phenomenon through the additional flow path and confirmed that the vehicle with the applied damper could control a wider range of vehicle upper displacement, velocity, and acceleration compared to conventional vehicles. Full article
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<p>Cross section of the proposed MR damper.</p>
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<p>Floor section of the proposed MR damper.</p>
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<p>Schematic of flow mode with regions A and B.</p>
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<p>Flow in a non-magnetized orifice.</p>
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<p>Flow in a basic gap.</p>
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<p>Damping force in a normal MR damper.</p>
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<p>Damping force in the proposed MR damper.</p>
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<p>Quarter-car model.</p>
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<p>Magnetic circuit design procedure (L-Company).</p>
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<p>Flow chart to analyze the characteristics of an MR damper with an additional flow path.</p>
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<p>Additional flow-path-type MR damper designed using ANSYS.</p>
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<p>Quarter-car model using AMESim.</p>
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<p>Magnetic circuit model of the MR damper designed by ANSYS Maxwell.</p>
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<p>B-H curve of MRF-132DG.</p>
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<p>B-H curve of AISI 1008.</p>
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<p>Sine wave road model.</p>
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<p>Sine wave excitation by velocity.</p>
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<p>Lines of magnetic flux density graph.</p>
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<p>Magnetic flux density of the main orifice.</p>
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<p>Magnetic flux density of the additional orifice.</p>
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<p>Magnetic flux density of the solenoid core.</p>
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<p>Magnetic flux density of the MR damper.</p>
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<p>Yield stress according to the current.</p>
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<p>Damping force in the gap according to the current.</p>
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<p>Total damping force in the proposed model.</p>
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<p>Total damping force in <math display="inline"><semantics> <mrow> <msub> <mrow> <mi>D</mi> </mrow> <mrow> <mi>o</mi> <mi>r</mi> <mi>i</mi> <mi>f</mi> <mi>i</mi> <mi>c</mi> <mi>e</mi> </mrow> </msub> </mrow> </semantics></math> = 1.0 mm and <math display="inline"><semantics> <mrow> <msub> <mrow> <mi>D</mi> </mrow> <mrow> <mi>o</mi> <mi>r</mi> <mi>i</mi> <mi>f</mi> <mi>i</mi> <mi>c</mi> <mi>e</mi> </mrow> </msub> </mrow> </semantics></math> = 1.2 mm.</p>
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<p>Comparison of variable <math display="inline"><semantics> <mrow> <msub> <mrow> <mi>D</mi> </mrow> <mrow> <mi>o</mi> <mi>r</mi> <mi>i</mi> <mi>f</mi> <mi>i</mi> <mi>c</mi> <mi>e</mi> </mrow> </msub> </mrow> </semantics></math>.</p>
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<p>Displacement when the vehicle velocity was 30 km/h.</p>
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<p>Velocity when the vehicle velocity was 30 km/h.</p>
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<p>Acceleration when the vehicle velocity was 30 km/h.</p>
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<p>Displacement when the vehicle velocity was 60 km/h.</p>
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<p>Velocity when the vehicle velocity was 60 km/h.</p>
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<p>Acceleration when the vehicle velocity was 60 km/h.</p>
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<p>Displacement when the vehicle velocity was 90 km/h.</p>
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<p>Velocity when the vehicle velocity was 90 km/h.</p>
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<p>Acceleration when the vehicle velocity was 60 km/h.</p>
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<p>Result of AMESim and theoretical value when the vehicle velocity was 30 km/h.</p>
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17 pages, 5752 KiB  
Article
Theoretical and Experimental Research on an Optimal Control for a Magnetorheological Shock Mitigation System
by Mukai Wang, Duhui Lu, Yeyin Xu, Yunfei Guo, Bing Li and Norman M. Wereley
Appl. Sci. 2024, 14(16), 7317; https://doi.org/10.3390/app14167317 - 20 Aug 2024
Viewed by 606
Abstract
Vibration and shock control systems are of vital importance to modern vehicles when incorporating crashworthiness goals and enhancing occupant safety to protect avionics or electronics during survivable crash events. The study proposes a method denoted as the optimal generalized Bingham number (GBN) control [...] Read more.
Vibration and shock control systems are of vital importance to modern vehicles when incorporating crashworthiness goals and enhancing occupant safety to protect avionics or electronics during survivable crash events. The study proposes a method denoted as the optimal generalized Bingham number (GBN) control to improve the soft-landing control accuracy of a drop-induced shock mitigation system employing a magnetorheological shock absorber (MREA). Based on the theoretical and experimental analysis of the damping force characteristics of the MREA, the dynamics of a single-degree-of-freedom shock mitigation system are established, and the GBN is defined with consideration of quadratic damping. The optimal GBN control strategy for a magnetorheological shock mitigation system is proposed to achieve a soft landing. The deceleration, velocity, and displacement formulas of the payload are derived, and the dynamic response of the magnetorheological shock mitigation system, under different GBNs, is analyzed. In terms of soft-landing control accuracy, it is shown that the optimal GBN control strategy performs better for a linear stroke MREA when the control algorithm is based on quadratic damping rather than linear damping. Full article
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<p>The double-ended MR damper configuration with two electromagnetic coils. 1—Upper piston rod, 2—piston core, 3—electromagnetic coil, 4—piston cylinder, 5—hydraulic cylinder, 6—MR fluid, 7—underneath piston rod, 8—piston, 9—seal ring, and 10—hydraulic cylinder seal cap.</p>
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<p>Magnetic analysis results with 2 A applied current.</p>
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<p>Magnetic flux density with various applied current.</p>
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<p>Experimental setup for the yield force of MREA.</p>
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<p>The MREA yield force characteristic under triangular excitation.</p>
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<p>Yield force vs. applied current.</p>
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<p>MREA high-speed drop hammer experiment setup.</p>
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<p>MREA damping force vs. velocity.</p>
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<p>A configuration of the MREA for drop-induced shock mitigation.</p>
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<p>Comparison of linear and nonlinear field-off damping force characteristics of MREA.</p>
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<p>Dynamic response of shock mitigation system under different control algorithms.</p>
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<p>Semi-active drop hammer shock mitigation for rapid control experiment setup.</p>
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<p>Semi-active drop hammer shock mitigation for rapid control experiment setup.</p>
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<p>Comparison of experimental results between BN controller and GBN controller.</p>
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16 pages, 7370 KiB  
Article
Replication of Radial Pulses Using Magneto-Rheological Fluids
by Miranda Eaton, Jeong-Hoi Koo, Tae-Heon Yang and Young-Min Kim
Micromachines 2024, 15(8), 1010; https://doi.org/10.3390/mi15081010 - 6 Aug 2024
Viewed by 759
Abstract
The radial pulse is a critical health marker with expanding applications in wearable technology. To improve these applications, developing a pulse generator that consistently produces realistic pulses is crucial for validation and training. The goal of this study was to design and test [...] Read more.
The radial pulse is a critical health marker with expanding applications in wearable technology. To improve these applications, developing a pulse generator that consistently produces realistic pulses is crucial for validation and training. The goal of this study was to design and test a cost-effective pulse simulator that can accurately replicate a wide range of age-dependent radial pulses with simplicity and precision. To this end, this study incorporated a magneto-rheological (MR) fluid device into a cam-based pulse simulator. The MR device, as a key component, enables pulse shaping without the need for additional cams, substantially reducing the cost and complexity of control compared with existing pulse simulators. To evaluate the performance of the MR pulse simulator, the root-mean-square (RMS) error criterion (less than 5%) was used to compare the experimentally obtained pulse waveform with the in vivo pulse waveform for specific age groups. After demonstrating that the MR simulator could produce three representative in vivo pulses, a parametric study was conducted to show the feasibility of the slope-based pulse-shaping method for the MR pulse simulator to continuously generate a range of age-related pulses. Full article
(This article belongs to the Special Issue Magnetorheological Materials and Application Systems)
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<p>Illustration of experimental set-up, including cam pulse generator, electromagnet, frictionless plunger assembly, and displacement sensor.</p>
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<p>(<b>a</b>) Empty MR fluid chamber with exposed silicone tubing; (<b>b</b>) fully assembled chamber filled with MR fluid and covered with film and lid.</p>
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<p>(<b>a</b>) Input duty values programmed in the micro-controller; (<b>b</b>) pulse width modulation (PWM) signal generated by the micro-controller; (<b>c</b>) resulting magnetic field from input PWM signal; and (<b>d</b>) age-dependent pulse generation measured by the laser displacement sensor.</p>
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<p>(<b>a</b>) Example of range of age-related in vivo radial pulse waveforms; (<b>b</b>) normalized pulse waveforms for ages 10–80.</p>
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<p>(<b>a</b>) MR pulse-shaping cam; (<b>b</b>) pulse waveforms generated by baseline cam for (<b>c</b>) 20, 50, and 80-year-old normalized waveforms into which the base pulse waveform is shaped.</p>
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<p>(<b>a</b>) Target 20-year-old in vivo pulse to be shaped; (<b>b</b>) duty values and magnetic field used to shape the base pulse into a 20-year-old pulse; and (<b>c</b>) resulting displacement and experimental displacement compared with 20-year-old in vivo pulse.</p>
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<p>(<b>a</b>) Target 50-year-old in vivo pulse to be shaped; (<b>b</b>) duty values and magnetic field used to shape the base pulse into a 50-year-old pulse; and (<b>c</b>) resulting displacement and experimental displacement compared with 50-year-old in vivo pulse.</p>
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<p>(<b>a</b>) Target 80-year-old in vivo pulse to be shaped; (<b>b</b>) duty values and magnetic field used to shape the base pulse into an 80-year-old pulse; and (<b>c</b>) resulting displacement and experimental displacement compared with 80-year-old in vivo pulse.</p>
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<p>(<b>a</b>) Example of 5 slope zones analyzed in 80-year-old in vivo pulse; (<b>b</b>) 5 slopes that represent the 80-year-old in vivo pulse.</p>
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<p>(<b>a</b>) Schematic design of half-cam, which maintains a constant radius for half of the disk; (<b>b</b>) normalized displacement graph of half-cam, illustrating constant displacement due to a constant radius.; (<b>c</b>) Fabricated actual half-cam using wire-cutting, (<b>d</b>) actual normalized displacement by half-cam.</p>
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<p>Graph showing three different variables tested during parametric study: duty slope, time duration, and magnitude.</p>
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<p>Results showing effect of changing duty slope on displacement slope. (<b>a</b>) Changing duty slope from 0.03%/s to 0.75%/s. (<b>b</b>) Resulting normalized displacement slope from changing duty slopes; displacement slopes are taken from within the boxed area.</p>
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<p>Results showing effect of changing duty magnitude on displacement slope. (<b>a</b>) Changing initial duty value from 20 to 70%. (<b>b</b>) Normalized displacement from changing duty magnitude; displacement slopes are taken from within the boxed area.</p>
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<p>Results showing effect of changing time duration on displacement slope. (<b>a</b>) Changing total time duration from 0.100 to 0.275 s. (<b>b</b>) Normalized displacement from changing duty magnitude; displacement slopes are taken from within the boxed area.</p>
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20 pages, 6319 KiB  
Article
The Actuating Characteristics of Magnetorheological Fluids Subjected to Particle Sedimentation and Temperature Variation
by Elliza Tri Maharani, Dong-Hoon Lee, Young-Jun Kim, Jong-Seok Oh and Seung-Bok Choi
Actuators 2024, 13(8), 277; https://doi.org/10.3390/act13080277 - 24 Jul 2024
Viewed by 972
Abstract
Magnetorheological (MR) fluids are known for their controllable characteristics under the influence of magnetic fields and, hence, widely used as semi-active actuators for vibration control. Regardless of advantages such as fast response time and reversible property, MR fluids inevitably experience sedimentation caused by [...] Read more.
Magnetorheological (MR) fluids are known for their controllable characteristics under the influence of magnetic fields and, hence, widely used as semi-active actuators for vibration control. Regardless of advantages such as fast response time and reversible property, MR fluids inevitably experience sedimentation caused by significant density mismatches between magnetic particles and carrier liquids. Moreover, the effect of the temperature on actuating characteristics is also one of the problems to be resolved for practical implementation. This study experimentally investigates the sedimentation behavior under various temperatures ranging from 25 to 70 °C using a multiguide-arm magnetic device that generates a uniform magnetic flux density across MR fluids. The sedimentation stability is then observed after 168 h at current inputs of 0, 1, and 2 A, respectively. Subsequently, the field-dependent rheological properties of MR fluids are evaluated using a rheometer and discussed, showing actuating capability, which depends on the viscosity, shear stress, and yield stress before (initial state) and after the sedimentation (sedimentation state). The field-dependent yield stresses, which directly represent the actuating force of the semi-active actuator, are specifically evaluated. Under the on-state condition (2 A) at a temperature of 70 °C, the yield stress decreased from 2.747 kPa (initial state) to 2.352 kPa (sedimentation state). By using this yield stress, the field-dependent damping force was evaluated, showing a decrement from 1672 N (initial state) to 1623 N (sedimentation state) at a velocity of 0.8 m/s. It is shown that the temperature causes the reduction of the actuating properties after the long-term operation. The insightful findings achieved in this work will provide useful information for the evaluation of actuating characteristics of smart MR fluids and the design of MR application systems subjected to particle sedimentation and temperature variation. Full article
(This article belongs to the Special Issue Magnetorheological Actuators and Dampers)
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<p>B-H curve (<b>a</b>) MR fluid 132-DG (<b>b</b>) Steel 45C.</p>
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<p>B-H curve (<b>a</b>) MR fluid 132-DG (<b>b</b>) Steel 45C.</p>
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<p>Geometric configuration.</p>
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<p>Simulation results of the magnetic field: (<b>a</b>) 1 A, (<b>b</b>) 2 A.</p>
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<p>Flow chart of the proposed study.</p>
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<p>Experimental setup for temperature control and input current supply.</p>
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<p>Temperature conditions of sedimentation experiment.</p>
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<p>Rheometer configuration.</p>
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<p>Sedimentation rate under various temperatures of 25 °C, 50 °C, and 70 °C at current inputs of (<b>a</b>) 0 A, (<b>b</b>) 1 A, (<b>c</b>) 2 A.</p>
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<p>The viscosity of MR fluids for initial and sedimentation states under the controlled temperatures of 25 °C, 50 °C, and 70 °C at current inputs of (<b>a</b>) 0 A, (<b>b</b>) 1 A, (<b>c</b>) 2 A.</p>
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<p>Shear stress of MR fluids for initial and sedimentation states under the controlled temperatures of 25 °C, 50 °C, and 70 °C at current inputs of (<b>a</b>) 0 A, (<b>b</b>) 1 A, (<b>c</b>) 2 A.</p>
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<p>Shear stress of MR fluids for initial and sedimentation states under the controlled temperatures of 25 °C, 50 °C, and 70 °C at current inputs of (<b>a</b>) 0 A, (<b>b</b>) 1 A, (<b>c</b>) 2 A.</p>
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<p>Section view of MR damper.</p>
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<p>Yield stress under different controlled temperatures of 25, 50, and 70 °C at current input of 0 A, 1 A, 2 A for initiate state and sedimentation state.</p>
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<p>MR damper dynamic range at temperatures of (<b>a</b>) 25 °C, (<b>b</b>) 50 °C, (<b>c</b>) 70 °C.</p>
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<p>MR damper dynamic range at temperatures of (<b>a</b>) 25 °C, (<b>b</b>) 50 °C, (<b>c</b>) 70 °C.</p>
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21 pages, 7946 KiB  
Article
Design, Modeling, and Vibration Control of a Damper Based on Magnetorheological Fluid and Elastomer
by Zhuang Jin, Fufeng Yang, Xiaoting Rui, Min Jiang and Jiaqi Wang
Actuators 2024, 13(7), 241; https://doi.org/10.3390/act13070241 - 27 Jun 2024
Viewed by 1667
Abstract
The aim of this study is to propose a damper based on magnetorheological (MR) fluid and elastomer for application in vehicle engine mounting systems to dissipate the vibration energy transferred from the engine to the vehicle body. The magnetic circuit structure of the [...] Read more.
The aim of this study is to propose a damper based on magnetorheological (MR) fluid and elastomer for application in vehicle engine mounting systems to dissipate the vibration energy transferred from the engine to the vehicle body. The magnetic circuit structure of the damper has been precisely designed, and its reasonableness has been verified by static magnetic field simulation. After the principle prototype’s completion, the damper’s mechanical properties are tested by an electro–hydraulic servo fatigue machine. The results show that with the current increase, the damper’s in-phase stiffness increases by 20.6%. The equivalent damping improves by 81.6%, which indicates that the damper has a good MR effect. A new phenomenological model is proposed, and a genetic algorithm is used to identify the parameters of the model. Finally, a 1/4 vehicle engine vibration damping system model is established and a dynamics simulation is carried out. The simulation results show that the damper effectively reduces the vibration transmitted from the engine to the body, and the vibration-damping effect is even more obvious through sky-hook control. This proves that the damper proposed in this study has good vibration-damping performance. Full article
(This article belongs to the Special Issue Magnetorheological Actuators and Dampers)
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<p>The structure of the damper.</p>
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<p>Installation diagram of engine mount system.</p>
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<p>Distribution of magnetic circuits and damping channels.</p>
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<p>Key design parameters of the damper.</p>
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<p>Prototype of the damper.</p>
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<p>Distribution of magnetic circuit at 2 A applied current.</p>
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<p>Distribution of magnetic flux intensity in damping channel at 2 A applied current.</p>
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<p>Dynamic testing system.</p>
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<p>Test results under 1 Hz sinusoidal excitations with an amplitude of 2 mm. (<b>a</b>) Force–displacement curve; (<b>b</b>) force–velocity curve.</p>
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<p>Analysis results of test data under 1 Hz sinusoidal excitations with an amplitude of 2 mm. (<b>a</b>) In-phase stiffness under different currents; (<b>b</b>) equivalent damping under different currents.</p>
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<p>Test and analysis results under 1 Hz sinusoidal excitations with 0.4 A current. (<b>a</b>) Force–displacement curve; (<b>b</b>) force–velocity curve; (<b>c</b>) in-phase stiffness of the MRFE damper under different amplitudes; (<b>d</b>) equivalent damping of the MRFE damper under different amplitudes.</p>
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<p>The dynamic range of the damper with different excitation amplitude.</p>
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<p>Dynamic model of the damper.</p>
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<p>Parameters and current fitting curve.</p>
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<p>Comparison of test value and predicted value under excitation with different amplitudes. (<b>a</b>) Force–displacement curve; (<b>b</b>) force–velocity curve; (<b>c</b>) time–force curve.</p>
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<p>Comparison of test value and predicted value under different currents. (<b>a</b>) Force–displacement curve; (<b>b</b>) force–velocity curve; (<b>c</b>) time–force curve.</p>
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<p>1/4 engine vibration reduction system dynamic model.</p>
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<p>Simulation results at 35 Hz engine frequency. (<b>a</b>) Vehicle center vertical speed curve; (<b>b</b>) vehicle center vertical acceleration curve.</p>
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<p>Simulation results at different engine frequencies. (<b>a</b>) Curve of displacement RMS value with frequency; (<b>b</b>) curve of acceleration RMS value with frequency; (<b>c</b>) curve of vibration isolation rate with frequency.</p>
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<p>Simulation results under class C road when the engine frequency is 15 Hz. (<b>a</b>) Vehicle center vertical speed curve; (<b>b</b>) vehicle center vertical acceleration curve.</p>
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15 pages, 5493 KiB  
Article
Investigating the Impact of Circular Sector Pole Head Structure on the Performance of a Multipole Magnetorheological Brake
by Yaojung Shiao and Manichandra Bollepelly
Appl. Sci. 2024, 14(12), 5344; https://doi.org/10.3390/app14125344 - 20 Jun 2024
Viewed by 585
Abstract
The magnetorheological brake (MRB) epitomized a revolutionary modification in the braking systems because of its extremely efficient and well-controlled performance. To increase the safety and controllability of automotive braking system, researchers have developed a different MRB structures. Although much research on magnetorheological brakes [...] Read more.
The magnetorheological brake (MRB) epitomized a revolutionary modification in the braking systems because of its extremely efficient and well-controlled performance. To increase the safety and controllability of automotive braking system, researchers have developed a different MRB structures. Although much research on magnetorheological brakes has shown positive results in terms of brake torque, braking time, thermal efficiency, etc., the ability to increase braking force by expanding the disc surface, through which the magnetic field operates in a compact structure, is restricted. To address this issue, a new multipole MRB configuration with a unique pole head design that maintains compactness. Initially, the conceptual design was achieved by leveraging the combined impact of the twin disc-type structure and multipole concept. The model was used in a dynamic simulation to show how the braking torque of a magnetorheological braking system varies with coil current. The effects of circular sector pole head shape on braking performance were investigated using COMSOL Multiphysics software (version 5.5). A three-dimensional electromagnetic model of the proposed MRB was developed to examine the magnetic flux intensity and the impact of magnetic field dispersion on the proposed pole head structure of a magnetorheological brake. Based on simulation results, the circular sector pole head configuration is capable of increasing the active chaining regions for the MR fluid on the rotor surface, allowing for a more effective use of magnetic flux throughout the whole surface of a rotating brake disc, thereby increasing the magnetic field usage rate. The acquired simulation results show an increase in braking torque while keeping a compact and practical design structure. Full article
(This article belongs to the Section Mechanical Engineering)
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<p>Schematic cross-section of a MRB.</p>
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<p>Pole head configuration.</p>
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<p>Two-dimensional view of a magnetic flux flow in a closed loop from one pole to an adjacent pole.</p>
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<p>Sector pole head structure through which magnetic flux flows.</p>
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<p>Braking torque for variation of pole head gap.</p>
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<p>Magnetic field intensity for varied coil current.</p>
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<p>Field distribution of MRB at 2 Amp.</p>
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<p>Magnetic field lines on a pole head.</p>
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<p>Two-dimensional view of Flux flowlines in a MRB.</p>
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<p>Flux flow through adjacent poles.</p>
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<p>Optimization results.</p>
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<p>Simulation analysis of a MRB (<b>a</b>) Minimum flux flow (<b>b</b>) Intermediate flux flow (<b>c</b>) Maximum flux flow.</p>
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<p>Output braking torque at different input coil current.</p>
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<p>Braking torque comparison for circular sector pole head to circular pole head.</p>
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13 pages, 68607 KiB  
Article
Enhancement of Magnetorheological Fluids with Size and Morphology—Optimized Fe3O4 Nanoparticles: Impacts on Rheological Properties and Stability
by Liwei Xu and Guangdong Zhou
Materials 2024, 17(12), 2838; https://doi.org/10.3390/ma17122838 - 11 Jun 2024
Viewed by 822
Abstract
In this study, we synthesized Fe3O4 nanoparticles (Fe3O4 NPs) of varying sizes and morphologies using the solvothermal method and incorporated them as additives into carbonyl iron magnetorheological fluids (CI-MRFs). We tested the shear stress, yield stress, viscosity [...] Read more.
In this study, we synthesized Fe3O4 nanoparticles (Fe3O4 NPs) of varying sizes and morphologies using the solvothermal method and incorporated them as additives into carbonyl iron magnetorheological fluids (CI-MRFs). We tested the shear stress, yield stress, viscosity and storage modulus of the MRFs using a magnetorheometer to investigate how the size and morphology of Fe3O4 NPs influence the performance of MRFs. Our results indicate that the size of the additive nanoparticles significantly enhances the MR properties of MRFs more than their morphological attributes. This enhancement results from optimizing and stabilizing the CI magnetic chain structure of the nanoparticles in the presence of a magnetic field. Specifically, MRFs with Fe3O4 NPs averaging 250 nm in size exhibit higher yield stress and storage modulus and show increased resistance to shear strains. Although the nanoparticle morphology has a modest effect on the rheological properties of MRFs, hexahedral and octahedral particles can enhance rheological properties through increased internal friction compared to spherical particles. Additionally, Fe3O4 NPs of different sizes and morphologies improve the sedimentation stability of MRFs, with those around 250 nm being particularly effective at slowing down sedimentation. Both hexahedral and octahedral Fe3O4 NPs slow down sedimentation more effectively than spherical Fe3O4 NPs. This paper investigates the rheological properties of CI-MRFs by controlling the additive particle size and morphological features, providing a research foundation for the design and optimization of MRFs. Full article
(This article belongs to the Section Smart Materials)
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<p>XRD (<b>a</b>) and EDS (<b>b</b>) patterns of Fe<sub>3</sub>O<sub>4</sub>.</p>
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<p>SEM images of the (<b>a</b>) CI, (<b>b</b>) 120 nm spherical Fe<sub>3</sub>O<sub>4</sub>, (<b>c</b>) 120 nm octahedral Fe<sub>3</sub>O<sub>4</sub>, (<b>d</b>) 120 nm hexahedral Fe<sub>3</sub>O<sub>4</sub>, (<b>e</b>) TEM-10 nm Fe<sub>3</sub>O<sub>4</sub>, (<b>f</b>) 80 nm Fe<sub>3</sub>O<sub>4</sub>, (<b>g</b>) 250 nm Fe<sub>3</sub>O<sub>4</sub>, (<b>h</b>) 500 nm Fe<sub>3</sub>O<sub>4</sub>.</p>
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<p>Magnetic hysteresis loops of (<b>a</b>) the CI and Fe<sub>3</sub>O<sub>4</sub> NPs with different particle sizes, (<b>b</b>) 120 nm Fe<sub>3</sub>O<sub>4</sub> NPs with different morphology.</p>
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<p>(<b>a</b>) Flow curves of CI-MRF and CI-Fe<sub>3</sub>O<sub>4</sub>-MRFs with different particle sizes, (<b>b</b>) Flow curves of CI-Fe<sub>3</sub>O<sub>4</sub>-MRFs with different morphology.</p>
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<p>(<b>a</b>) Viscosity curves of CI-MRFs and CI-Fe<sub>3</sub>O<sub>4</sub>-MRFs with different particle sizes, (<b>b</b>) Viscosity curves of CI-Fe<sub>3</sub>O<sub>4</sub>-MRFs with different morphology.</p>
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<p>(<b>a</b>) Yield stresses of CI-MRFs and CI-Fe<sub>3</sub>O<sub>4</sub>-MRFs with different particle sizes, (<b>b</b>) Yield stresses CI-Fe<sub>3</sub>O<sub>4</sub>-MRFs with different morphologies.</p>
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<p>The storage modulus (G′), damping factor versus shear strain of CI-MRFs and CI-Fe<sub>3</sub>O<sub>4</sub>-MRFs with different particle sizes in 67.2 kA/m (<b>a</b>,<b>b</b>) and 268.5 kA/m (<b>c</b>,<b>d</b>) magnetic fields.</p>
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<p>The storage modulus (G′), damping factor versus shear strain of CI-Fe<sub>3</sub>O<sub>4</sub>-MRFs with different morphologies in 67.2 kA/m (<b>a</b>,<b>b</b>) and 268.5 kA/m (<b>c</b>,<b>d</b>) magnetic fields.</p>
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<p>(<b>a</b>) Sedimentation ratios of CI-MRF and CI-Fe<sub>3</sub>O<sub>4</sub>-MRF with different particle sizes, (<b>b</b>) Sedimentation ratios of CI-Fe<sub>3</sub>O<sub>4</sub>-MRF with different morphologies.</p>
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<p>Shear modeling of CI-Fe<sub>3</sub>O<sub>4</sub> bi-dispersed phase MRFs. (<b>a</b>) MRFs without magnetic field (<b>b</b>) MRF with magnetic field (<b>c</b>) MRFs after shear thinning.</p>
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<p>Void filling modeling of CI by Fe<sub>3</sub>O<sub>4</sub> NPs with different morphologies. (<b>a</b>) spherical, bct lattice, (<b>b</b>) octahedral, (<b>c</b>) hexahedral.</p>
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15 pages, 5573 KiB  
Article
A Study on Power Transmission Control for Applying MR Fluid Multi-Plate Clutch to Automobile Power Distribution Device
by Jin-Young Park, Jae-Hoon Jeon and Young-Choon Kim
Appl. Sci. 2024, 14(9), 3871; https://doi.org/10.3390/app14093871 - 30 Apr 2024
Viewed by 967
Abstract
The aim of this study is to design and manufacture a multi-plate clutch system that uses magnetorheological (MR) fluid control to allow for a variable power transmission ratio in power distribution systems. MR fluid is a smart material that enables presenting a solution [...] Read more.
The aim of this study is to design and manufacture a multi-plate clutch system that uses magnetorheological (MR) fluid control to allow for a variable power transmission ratio in power distribution systems. MR fluid is a smart material that enables presenting a solution to the shocks and power loss that occur due to mechanical problems in power distribution systems. As such, the longitudinal and lateral dynamic properties of 4WD (four-wheel drive) vehicles were examined and analyzed to develop an algorithm to control the front/rear power distribution according to the road surface state and driving conditions. To verify the algorithm, the CarSim vehicle dynamics simulation program was adopted to perform experiments to understand the vehicle’s dynamic performance improvements and turning stability via a HILS (Hardware in the Loop) system. In this study, an MR fluid, multi-plate clutch was used that combines a dry clutch and a wet clutch using the characteristics of the MR fluid. Such a clutch was designed to enable continuous and smooth torque transmission by utilizing the strengths of each of the dry and wet clutches. The CarSim vehicle dynamics program was used to conduct the experiments, which were conducted by linking to the manufactured MR fluid clutch experimental device. The experiments investigated the dynamic performance based on the power distribution ratio by performing longitudinal flat, inclined driving and lateral DLC (double lane change) driving. In summary, this study found that it is possible to perform power transmission by applying a current to an MR fluid and forming a magnetic field to change the flow properties of the fluid to control the torque transmission ratio that occurs in an MR fluid clutch. Full article
(This article belongs to the Section Fluid Science and Technology)
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<p>Diagram of the MR fluid multi-plate clutch. (<b>a</b>) An exploded CAD model of an MR fluid multi-plate clutch. (<b>b</b>) Prototype MR fluid multi-plate clutch.</p>
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<p>Simulation results for the acceleration performance during lateral driving.</p>
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<p>Comparison based on the vehicle drive style. (<b>a</b>) Comparison of the lateral acceleration according to the vehicle driving style. (<b>b</b>) Comparison of the yaw rate according to the vehicle driving style.</p>
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<p>The HiLS system configuration.</p>
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<p>Control system flowchart. (<b>a</b>) Main routine. (<b>b</b>) Sub routine.</p>
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<p>Graph of the torque by current value and drive RPM.</p>
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<p>Power distribution ratio: (<b>a</b>) 20 rpm. (<b>b</b>) 100 rpm.</p>
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<p>Front/rear driveshaft torque: (<b>a</b>) 20 rpm. (<b>b</b>) 100 rpm.</p>
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<p>The wheel’s longitudinal slip ratio: (<b>a</b>) 20 rpm. (<b>b</b>) 100 rpm.</p>
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<p>Power distribution ratio: (<b>a</b>) 20 rpm. (<b>b</b>) 100 rpm.</p>
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<p>Power distribution ratio: (<b>a</b>) 20 rpm. (<b>b</b>) 100 rpm.</p>
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<p>The vehicle lateral acceleration and yaw rate when DLC driving.</p>
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12 pages, 5211 KiB  
Article
Mechanical Properties Comparison of Isotropic vs. Anisotropic Hybrid Magnetorheological Elastomer-Fluid
by Hammam M. Ananzeh, Rahizar Ramli, Sabariah Julai and Asan G. A. Muthalif
Polymers 2024, 16(9), 1215; https://doi.org/10.3390/polym16091215 - 26 Apr 2024
Viewed by 976
Abstract
Magnetorheological (MR) materials are smart materials that can change their rheological characteristics when exposed to a magnetic field. Such rheological properties include viscosity and dynamic modulus. MR materials have emerged as one of the most efficient smart materials that can modify mechanical and [...] Read more.
Magnetorheological (MR) materials are smart materials that can change their rheological characteristics when exposed to a magnetic field. Such rheological properties include viscosity and dynamic modulus. MR materials have emerged as one of the most efficient smart materials that can modify mechanical and viscoelastic characteristics. Depending on the medium used, MR materials can be classified into two types: magnetorheological fluids (MRFs) and magnetorheological elastomers (MREs). MREs are classified as isotropic or anisotropic based on CIP distribution inside the elastomer matrix. A unique hybrid material incorporating MRE and MRF is constructed in this work to investigate, compare, and the dynamic properties of isotropic, anisotropic, hybrid isotropic, and hybrid anisotropic MREs under various magnetic fields (0, 104, and 160.2 mT). The created samples are subjected to extensive testing, including static and dynamic evaluations. In the static tests, experiments use a compression linear displacement mode with a fixed maximum gap change of 3 mm. The temperature is maintained at a constant level of 24 °C throughout the 40 s test duration for each test, and the magnetic field is incrementally increased by varying the number of magnets, ranging from 0 to 160.2 mT for dynamic qualities using compression oscillations on a dynamic mechanical analyzer (DMA), including frequency and strain-dependent data. These experiments, carried out using sinusoidal shear movements, include an excitation frequency range of 0.1 Hz to 15 Hz while preserving, with a fixed shear strain of 2%. Full article
(This article belongs to the Section Polymer Physics and Theory)
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<p>Schematic diagram of the hybrid anisotropic and isotropic fabrication process.</p>
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<p>The hybrid sample fabrication, with (<b>a</b>) the anisotropic or isotropic MRE, (<b>b</b>) the MRE sample after adding the MRF, and (<b>c</b>) the final H-MRE-F sample.</p>
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<p>MRE sample position on the dynamic mechanical analyzer.</p>
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<p>(<b>a</b>,<b>b</b>) Magnetic vector contour for the magnetic field system by finite element analysis, and (<b>c</b>) the distribution of normalized magnetic flux density (measured) and location of the test sample (top view).</p>
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<p>Microstructure images of fabricated MRE samples: (<b>a</b>) isotropic sample, (<b>b</b>) anisotropic sample (The red arrows indicate the direction of the particle chains).</p>
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<p>Force–displacement with zero magnets (<b>a</b>), nine magnets (<b>b</b>), and fifteen magnets (<b>c</b>).</p>
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<p>The effective stiffness of H-MRE-F and MRE samples under the influence of a magnetic field.</p>
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<p>Stiffness magnetorheological (SMR) effect.</p>
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<p>Storage modulus and loss factor of each isotropic, anisotropic MRE, and isotropic and anisotropic H-MREF sample at different magnetic fields.</p>
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<p>Storage modulus and loss factor for (<b>a</b>,<b>b</b>) isotropic MRE, (<b>c</b>,<b>d</b>) anisotropic MRE, (<b>e</b>,<b>f</b>) hybrid isotropic HMRE-F, and (<b>g</b>,<b>h</b>) hybrid anisotropic HMRE-F.</p>
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17 pages, 5650 KiB  
Article
A New Type of Hydraulic Clutch with Magnetorheological Fluid: Theory and Experiment
by Karol Musiałek, Ireneusz Musiałek, Karol Osowski, Artur Olszak, Aneta Mikulska, Zbigniew Kęsy, Andrzej Kęsy and Seung-Bok Choi
Micromachines 2024, 15(5), 572; https://doi.org/10.3390/mi15050572 - 26 Apr 2024
Cited by 1 | Viewed by 1060
Abstract
This paper presents a new type of hydraulic clutch operating by means of magnetorheological (MR) fluids and the results achieved from both theoretical analysis and experimental measurement. A hydraulic clutch system with MR working fluid and a rotating magnetic field located was designed. [...] Read more.
This paper presents a new type of hydraulic clutch operating by means of magnetorheological (MR) fluids and the results achieved from both theoretical analysis and experimental measurement. A hydraulic clutch system with MR working fluid and a rotating magnetic field located was designed. The clutch was based on the principle of using a rotating magnetic field created by an alternating current electromagnet to set the MR fluid in motion. To test the hydraulic clutch with a rotating magnetic field, MR fluids were produced by our laboratory, consisting of solid iron particles of various diameters mixed with a silicone oil. With MR working fluid and a rotating magnetic core was designed. The rheological properties of the MR fluids were assessed on the basis of tests carried out with a Brookfield DV2T rheometer equipped with a magnetic device for generating a magnetic field. The characteristics of the hydraulic clutch were tested on a specially built test stand. It was found that the torque transmitted by the clutch increased with the rotational speed of the magnetic field and with a lower rotational speed of the beaker in which the working fluid was placed. It was also found that the greatest torque occurred with the working fluid with the highest iron content. Based on the analysis of the structure and characteristics of the clutch in which the magnetic field is used, it has been shown that the design of the developed clutch is similar to that of an induction clutch, and its characteristics correspond to the characteristics of the eddy current clutch. Therefore, the proposed new clutch with MR fluid and rotating magnetic field can be applied to stationary power transmission systems in a manner similar to an eddy current clutch. Full article
(This article belongs to the Section E:Engineering and Technology)
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<p>HMCR construction scheme: 1—coil, 2—bearings, 3—output shaft, 4—beaker, 5—MR fluid, 6—stator of a three-phase induction motor, 7—slip rings, 8—input shaft, 9—bearing housing.</p>
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<p>View of the station used for testing the rheological properties of the MR fluid: 1—PC, 2—rheometer, 3—electric power supply, 4—magnetic device.</p>
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<p>Magnetic device used to test the MR fluid: 1—beaker with MR fluid, 2—electromagnet coil, 3—magnetic circuit.</p>
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<p>The dependence of the torque, <span class="html-italic">M<sub>r</sub></span>, on magnetic induction <span class="html-italic">B</span> for fluids A1 and B1 and for <span class="html-italic">ω<sub>r</sub></span> = 2 rad/s.</p>
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<p>Dependences of the torque <span class="html-italic">M<sub>r</sub></span> on <span class="html-italic">ω<sub>r</sub></span> for fluid A5 and different values of <span class="html-italic">B</span>.</p>
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<p>HCMR test stand: (<b>a</b>) construction scheme: 1—stator of a three-phase induction motor, 2—beaker, 3—beaker bearing, 4—torque meter, 5—output shaft, 6—brake, 7—rotational speed meter, 8—clutch, 9—MR fluid, 10—frame; (<b>b</b>) view.</p>
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<p>View of the B3 fluid surface at HCMR start-up for <span class="html-italic">ω</span> = 240 rad/s: (<b>a</b>) wrinkles, (<b>b</b>) ring of swirling fluid.</p>
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<p>View of a hexagon formed by the rotation of the MR fluid for B3 fluid and <span class="html-italic">ω</span> = 240 rad/s.</p>
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<p>View of the potential vortex in fluid B2.</p>
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<p>View of the B2 fluid spread evenly on the beaker walls.</p>
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<p>Dependences of angular velocity <span class="html-italic">ω</span><sub>2</sub> on angular velocity <span class="html-italic">ω</span> for the fluid B5 and fluid volume <span class="html-italic">V</span> = 75 cm<sup>3</sup>.</p>
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<p>Dependence of the torque <span class="html-italic">M</span> on the angular velocity <span class="html-italic">ω</span><sub>2</sub> for fluids A1 and B1, <span class="html-italic">ω</span> = 300 rad/s, <span class="html-italic">V</span> = 75 cm<sup>3</sup>.</p>
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<p>Dependence of the torque <span class="html-italic">M</span> on the angular velocity <span class="html-italic">ω</span><sub>2</sub> for fluids B1–B5 for <span class="html-italic">ω</span> = 300 rad/s, <span class="html-italic">V</span> = 75 cm<sup>3</sup>.</p>
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<p>Dependence of the torque <span class="html-italic">M</span> on the angular velocity <span class="html-italic">ω</span><sub>2</sub> for fluids A1 and B1 for <span class="html-italic">ω</span> = 300 rad/s, <span class="html-italic">V</span> = 75 cm<sup>3</sup>.</p>
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<p>Dependence of the torque <span class="html-italic">M<sub>max</sub></span> on angular velocity <span class="html-italic">ω</span> for fluids A4 and B4, <span class="html-italic">V</span> = 75 cm<sup>3</sup>.</p>
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<p>Dependence of the torque <span class="html-italic">M<sub>max</sub></span> on the volume <span class="html-italic">V</span> of the fluid A1 for <span class="html-italic">ω</span> = 200 rad/s.</p>
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<p>Viscous-plastic model of Bingham’s fluid: <span class="html-italic">F</span>—force acting on particles, <span class="html-italic">T</span>—friction force, <span class="html-italic">L</span>—viscous force.</p>
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<p>Forces acting on the MR fluid and the beaker during HCMR operation: (<b>a</b>) <span class="html-italic">ω</span><sub>2</sub> = <span class="html-italic">ω</span>; 1—beaker wall, 2—magnet, 3—MR fluid pulled by the magnet, 4—a ring of MR fluid; (<b>b</b>) <span class="html-italic">ω</span><sub>2</sub> &lt; <span class="html-italic">ω</span>.</p>
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<p>Characteristics of clutches using the influence of a magnetic field: 1—electromagnetic friction-type clutches [<a href="#B8-micromachines-15-00572" class="html-bibr">8</a>], 2—induction clutches [<a href="#B45-micromachines-15-00572" class="html-bibr">45</a>], 3—viscous clutches with MR fluid [<a href="#B47-micromachines-15-00572" class="html-bibr">47</a>], 4—magnetic particle clutches [<a href="#B8-micromachines-15-00572" class="html-bibr">8</a>], 5—eddy current clutches [<a href="#B8-micromachines-15-00572" class="html-bibr">8</a>].</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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14 pages, 4488 KiB  
Article
Synthesis of rGO/CoFe2O4 Composite and Its Magnetorheological Characteristics
by Yang Lv, Chengjie Gong, Yuzhen Dong and Hyoung Jin Choi
Materials 2024, 17(8), 1859; https://doi.org/10.3390/ma17081859 - 18 Apr 2024
Cited by 1 | Viewed by 1165
Abstract
In this study, composite particles of rGO/CoFe2O4 were synthesized using a solvothermal method to fabricate a low-density magnetorheological (MR) material with enhanced sedimentation stability. The morphology and crystallographic features of rGO/CoFe2O4 were characterized via SEM, TEM, and [...] Read more.
In this study, composite particles of rGO/CoFe2O4 were synthesized using a solvothermal method to fabricate a low-density magnetorheological (MR) material with enhanced sedimentation stability. The morphology and crystallographic features of rGO/CoFe2O4 were characterized via SEM, TEM, and XRD, and its magnetic properties were tested using VSM. The MR fluid was formulated by blending rGO/CoFe2O4 particles into silicone oil. Under different magnet strengths (H), a rotational rheometer was used to test its MR properties. Typical MR properties were observed, including shear stress, viscosity, storage/loss modulus, and dynamic yield stress (τdy) following the Herschel–Bulkley model reaching 200 Pa when H is 342 kA/m. Furthermore, the yield stress of the MR fluid follows a power law relation as H increases and the index changes from 2.0 (in the low H region) to 1.5 (in the high H region). Finally, its MR efficiency was calculated to be about 104% at H of 342 kA/m. Full article
(This article belongs to the Section Smart Materials)
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<p>SEM images of (<b>a</b>) GO sheet, (<b>b</b>,<b>c</b>) rGO/CoFe<sub>2</sub>O<sub>4</sub>, and TEM images of (<b>d</b>) GO sheet, (<b>e</b>,<b>f</b>) rGO/CoFe<sub>2</sub>O<sub>4</sub> composite. Inset in (<b>d</b>) shows side view of GO sheet.</p>
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<p>XRD patterns of (<b>a</b>) GO and (<b>b</b>) rGO/CoFe<sub>2</sub>O<sub>4</sub>. Inset depicts XRD pattern of graphite.</p>
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<p>Magnetization curve of rGO/CoFe<sub>2</sub>O<sub>4</sub> composite.</p>
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<p>Flow curve for rGO/CoFe<sub>2</sub>O<sub>4</sub>-based MR fluid under various <span class="html-italic">H</span> (<b>a</b>) shear stress and (<b>b</b>) shear viscosity curves as a function of shear rate.</p>
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<p>Flow curve for rGO/CoFe<sub>2</sub>O<sub>4</sub>-based MR fluid under various <span class="html-italic">H</span> (<b>a</b>) shear stress and (<b>b</b>) shear viscosity curves as a function of shear rate.</p>
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<p>(<b>a</b>) Strain and (<b>b</b>) frequency dependence of storage (closed) and loss (open) modulus for rGO/CoFe<sub>2</sub>O<sub>4</sub>-based MR fluid.</p>
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<p>Relaxation modulus calculated from the storage and loss modulus as a function of time.</p>
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<p>(<b>a</b>) Shear stress as a function of shear rate and (<b>b</b>) elastic stress as a function of strain under various <span class="html-italic">H</span>.</p>
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<p>Dynamic yield stress (cubic) and elastic yield stress (trigonal) as function of <span class="html-italic">H</span>.</p>
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<p>Dynamic and elastic yield stress as a function of <span class="html-italic">H</span> and universal fitting line.</p>
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<p>MR efficiency as a function of shear rate under various <span class="html-italic">H</span>.</p>
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21 pages, 10990 KiB  
Article
Electromagnetic Interaction Model between an Electric Motor and a Magnetorheological Brake
by Sidorela Caushaj, Giovanni Imberti, Henrique de Carvalho Pinheiro and Massimiliana Carello
Designs 2024, 8(2), 25; https://doi.org/10.3390/designs8020025 - 14 Mar 2024
Cited by 1 | Viewed by 1855
Abstract
This article focuses on modelling and validating a groundbreaking magnetorheological braking system. Addressing shortcomings in traditional automotive friction brake systems, including response delays, wear, and added mass from auxiliary components, the study employs a novel brake design combining mechanical and electrical elements for [...] Read more.
This article focuses on modelling and validating a groundbreaking magnetorheological braking system. Addressing shortcomings in traditional automotive friction brake systems, including response delays, wear, and added mass from auxiliary components, the study employs a novel brake design combining mechanical and electrical elements for enhanced efficiency. Utilizing magnetorheological (MR) technology within a motor–brake system, the investigation explores the influence of external magnetic flux from the nearby motor on MR fluid movement, particularly under high-flux conditions. The evaluation of a high-magnetic-field mitigator is guided by simulated findings with the objective of resolving potential issues. An alternative method of resolving an interaction between an electric motor and a magnetorheological brake is presented. In addition, to test four configurations, multiple absorber materials are reviewed. Full article
(This article belongs to the Special Issue Design and Manufacture of Electric Vehicles)
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<p>(<b>a</b>) Magnetic field configuration magnet array; (<b>b</b>) Simulation Analysis of a Halbach Array Model [<a href="#B16-designs-08-00025" class="html-bibr">16</a>].</p>
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<p>Magnetic field simulation of the Helmholtz coil comprising two 200 mm, 500500-turnectric coils in air [<a href="#B18-designs-08-00025" class="html-bibr">18</a>]: (<b>a</b>) Top view; (<b>b</b>) Side view.</p>
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<p>Coil configuration and simulation in two different directions [<a href="#B25-designs-08-00025" class="html-bibr">25</a>]: (<b>a</b>) Same direction; (<b>b</b>) Opposite direction.</p>
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<p>Brake geometry: (<b>a</b>) Brake section; (<b>b</b>) Brake parts: 1. MR Fluid Selection (blue), 2. Coils (purple), 3. Bobbins (red), 4. Lip Seals (black), 5. Rotor (light green), 6. Stator (dark green), 7. Cover (grey).</p>
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<p>B-H curve for MRF [<a href="#B31-designs-08-00025" class="html-bibr">31</a>].</p>
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<p>Configuration simulation at <math display="inline"><semantics> <mrow> <mi mathvariant="normal">k</mi> <mo>=</mo> <msup> <mrow> <mn>10</mn> </mrow> <mrow> <mn>5</mn> </mrow> </msup> </mrow> </semantics></math>: (<b>a</b>) Coil configuration side view; (<b>b</b>) Influence of coil configuration on the brake; (<b>c</b>) Close-up lip view.</p>
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<p>Configuration 2 simulation at <math display="inline"><semantics> <mrow> <mi mathvariant="normal">k</mi> <mo>=</mo> <msup> <mrow> <mn>10</mn> </mrow> <mrow> <mn>5</mn> </mrow> </msup> </mrow> </semantics></math>: (<b>a</b>) Coil configuration side view; (<b>b</b>) Influence of coil configuration on the brake; (<b>c</b>) Close-up lip view.</p>
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<p>Configuration 3 simulation at k = 1: (<b>a</b>) Coil configuration side view; (<b>b</b>) Influence of coil configuration on the brake; (<b>c</b>) Close-up lip view.</p>
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<p>Configuration 3 simulation at <math display="inline"><semantics> <mrow> <mi mathvariant="normal">k</mi> <mo>=</mo> <msup> <mrow> <mn>10</mn> </mrow> <mrow> <mn>5</mn> </mrow> </msup> </mrow> </semantics></math>: (<b>a</b>) Coil configuration side view; (<b>b</b>) Influence of coil configuration on the brake; (<b>c</b>) Close-up lip view.</p>
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<p>Configuration 4 simulation at <math display="inline"><semantics> <mrow> <mi mathvariant="normal">k</mi> <mo>=</mo> <msup> <mrow> <mn>10</mn> </mrow> <mrow> <mn>5</mn> </mrow> </msup> </mrow> </semantics></math>: (<b>a</b>) Coil configuration side view; (<b>b</b>) Influence of coil configuration on the brake; (<b>c</b>) Close-up lip view.</p>
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<p>The four configurations of the Helmholtz coil: (<b>a</b>) Configuration 1; (<b>b</b>) Configuration 2; (<b>c</b>) Configuration 3; (<b>d</b>) Configuration 4.</p>
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<p>The four configurations of the Helmholtz coil: (<b>a</b>) Configuration 1; (<b>b</b>) Configuration 2; (<b>c</b>) Configuration 3; (<b>d</b>) Configuration 4.</p>
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<p>Magnetic Flux Density of the motor averages vs. Magnetic Field of the Motor: (<b>a</b>) B-H curves of all configurations; (<b>b</b>) Zoomed-in B-H curves of all configurations.</p>
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<p>Magnetic Flux Density of the motor averages vs. Magnetic Field of the MRF: (<b>a</b>) B-H curves of all configurations; (<b>b</b>) B-H curves of Configuration 3.</p>
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<p>Magnetic field influence on a metal object and on a magnetic sheet [<a href="#B36-designs-08-00025" class="html-bibr">36</a>]: (<b>a</b>) metal object without the absorber; (<b>b</b>) metal object after the insertion of the absorber.</p>
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<p>Magnetic field strength of MRF-132-DG vs. Magnetic flux density on Configuration 3: (<b>a</b>) Comparison of B-H curves between three absorbers; (<b>b</b>) Comparison of B-H curves with and without the absorber.</p>
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17 pages, 4161 KiB  
Article
Magnetorheological Polishing Based on Honing Vertical Mechanism for Inner Surface of Titanium Alloy Pipes
by Wanli Song, Zhen Yang, Dezhi Meng, Na Wang and Seung-Bok Choi
Lubricants 2024, 12(3), 86; https://doi.org/10.3390/lubricants12030086 - 8 Mar 2024
Cited by 2 | Viewed by 1381
Abstract
Recently, high internal surfaces for titanium alloy pipes have been required due to the increment of various applications such as aerospace components. In this work, vertical magnetorheological polishing (VMRP) is carried out to achieve high polishing performance on the internal surface of the [...] Read more.
Recently, high internal surfaces for titanium alloy pipes have been required due to the increment of various applications such as aerospace components. In this work, vertical magnetorheological polishing (VMRP) is carried out to achieve high polishing performance on the internal surface of the titanium alloy pipe. A series of comparative experiments were conducted to investigate the polishing mechanism of magnetorheological polishing (MRP) fluid and enhance the polishing performance. It is shown from the experimental results that the VMRP method under the opposite polarity arrangement improves the surface roughness from 47.85% to 83.34% by reducing unwanted vibration and noise during operation. This provides nanoscale surface polishing quality, while such a precision cannot be achieved from the previous horizontal MR polishing apparatus method. It is found that under a 2700 cycle polishing time, a polishing process combining a rough and fine polishing approach with a combination of different particle diameters results in an axial surface roughness of 0.05 μm and circumferential surface roughness of 0.038 μm, respectively. It is also identified that the axial surface roughness of 0.04 μm–0.041 μm is achieved through the combination of high- and low-speed polishing process after 1602 cycles. Full article
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<p>Schematic diagram of honing MR polishing principle.</p>
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<p>Chain structure of MR fluid and MR polishing fluid.</p>
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<p>Photograph and schematic diagram of the VMRP apparatus.</p>
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<p>Diagram of the magnetic field assignment.</p>
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<p>Distributions of the magnetic flux under different assignments.</p>
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<p>Simulation of the magnetic field strength in different working gaps for different schemes.</p>
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<p>The internal surface and surface topography of pipes under different polishing times.</p>
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<p>The surface roughness of pipes under different polishing times: (<b>a</b>) axial surface roughness, (<b>b</b>) circumferential surface roughness.</p>
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<p>The mass of material removal of pipes under different polishing times.</p>
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<p>The internal surface and surface topographies of pipes under different size combinations of particles.</p>
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<p>The surface roughness of pipes under different size combinations of particles: (<b>a</b>) axial surface roughness, (<b>b</b>) circumferential surface roughness.</p>
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<p>The mass of material removal of pipes under different size combinations of particles.</p>
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<p>The internal surface and surface topography of pipes under rotation speed combinations.</p>
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<p>The surface roughness of pipes under rotation speed combinations: (<b>a</b>) axial surface roughness, (<b>b</b>) circumferential surface roughness.</p>
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<p>The mass of material removal of pipes under rotation speed combinations.</p>
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16 pages, 8751 KiB  
Article
The Influence of Current Magnitudes and Profiles on the Sedimentation of Magnetorheological Fluids: An Experimental Work
by Elliza Tri Maharani, Myeong-Won Seo, Jung Woo Sohn, Jong-Seok Oh and Seung-Bok Choi
Magnetochemistry 2024, 10(3), 18; https://doi.org/10.3390/magnetochemistry10030018 - 7 Mar 2024
Cited by 1 | Viewed by 1774
Abstract
Magnetorheological fluids (MRFs) are widely used for various kinds of controllable devices since their properties can be controlled by an external magnetic field. Despite many benefits of MRFs, such as fast response time, the sedimentation arisen due to the density mismatch of the [...] Read more.
Magnetorheological fluids (MRFs) are widely used for various kinds of controllable devices since their properties can be controlled by an external magnetic field. Despite many benefits of MRFs, such as fast response time, the sedimentation arisen due to the density mismatch of the compositions between iron particles and carrier oil is still one of bottlenecks to be resolved. Many studies on the sedimentation problem of MR fluids have been carried out considering appropriate additives, nanoparticles, and several carrier oils with different densities. However, a study on the effect of current magnitudes and profiles on the sedimentation is considerably rare. Therefore, this study experimentally investigates sedimentation behaviors due to different current magnitudes and different magnitude profiles such as square and sine waves in different diameters. The evaluation was performed by visual observation to obtain the sedimentation rate. It was found that the average sedimentation rate of the square type of current is slower compared to the sinusoidal type. It has also been identified that the higher intensity of the applied current results in a stronger electromagnetic field, which could slow down the sedimentation. The results achieved in this work can be effectively used to reduce particle sedimentation in the controller design of various application systems utilizing MRFs in which the controller generates a different magnitude and different profile of the external magnetic field. Full article
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<p>The schematic of surface precision machining.</p>
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<p>Cross-section model of experimental setup.</p>
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<p>B-H curve of MR fluids 132-DG.</p>
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<p>The result of the magnetic field analysis in a different current input, (<b>a</b>) 0.5 A, (<b>b</b>) 1 A, (<b>c</b>) 1.5 A, (<b>d</b>) 2 A.</p>
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<p>Flow diagram of experimental study.</p>
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<p>Output signal of power supply (<b>a</b>) sine wave excitation, (<b>b</b>) square wave excitation.</p>
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<p>Output signal of power supply (<b>a</b>) sine wave excitation, (<b>b</b>) square wave excitation.</p>
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<p>Experimental setup, (<b>a</b>) initial stage of experimental setup, (<b>b</b>) front view of hall sensor, (<b>c</b>) front view of the final experimental setup.</p>
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<p>Experimental setup, (<b>a</b>) initial stage of experimental setup, (<b>b</b>) front view of hall sensor, (<b>c</b>) front view of the final experimental setup.</p>
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<p>The calibrated value of the CGS unit of magnetic field intensity by the hall sensor at a current input of 2 A under (<b>a</b>) sine wave excitation, (<b>b</b>) square wave excitation.</p>
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<p>The comparison of sedimentation rate according to wave types and current input intensity using the small tube.</p>
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<p>MR fluids samples for small measuring tube: (<b>a</b>) initial condition (0 h); (<b>b</b>) 0 A (336 h); (<b>c</b>) sine wave, 0.5 A (336 h); (<b>d</b>) sine wave, 1 A (336 h); (<b>e</b>) sine wave, 1.5 A (336 h); (<b>f</b>) sine wave, 2 A (336 h); (<b>g</b>) square wave, 1 A (336 h); (<b>h</b>) square wave, 2 A (336 h).</p>
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<p>The distribution of iron particles under exciting electromagnetic fields.</p>
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<p>The comparison of sedimentation rate according to different current input intensities under sine wave using the small tube.</p>
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<p>The comparison of sedimentation rate according to different current input intensities under sine wave using the small tube and big tube.</p>
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<p>MR fluid samples for big measuring tube, (<b>a</b>) initial condition (0 h), (<b>b</b>) 0 A (336 h), (<b>c</b>) sine wave, 1 A (336 h), (<b>d</b>) sine wave, 2 A (336 h).</p>
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