Статті в журналах: "Rigid model"

1

Miškinis, P., and G. Karlikauskas. "Rigid surface bag model." Nuclear Physics A 683, no. 1-4 (February 2001): 339–58. http://dx.doi.org/10.1016/s0375-9474(00)00442-5.

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2

Chelushkin, Ilya, and Albert Burhanuddinov. "Model of junctioning rigid and non-rigid road pavement." IOP Conference Series: Materials Science and Engineering 890 (August 13, 2020): 012034. http://dx.doi.org/10.1088/1757-899x/890/1/012034.

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3

Siddharthan, Raj, Samia Ara, and Gary M. Norris. "Simple Rigid Plastic Model for Seismic Tilting of Rigid Walls." Journal of Structural Engineering 118, no. 2 (February 1992): 469–87. http://dx.doi.org/10.1061/(asce)0733-9445(1992)118:2(469).

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4

Lück, Reinhard. "A Rigid Generalisation of the Association Model / A Rigid Generalisation of the Association Model." International Journal of Materials Research 80, no. 10 (October 1, 1989): 719–22. http://dx.doi.org/10.1515/ijmr-1989-801006.

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5

Sharma, Sunil Kumar, Rakesh Chandmal Sharma, Yeongil Choi, and Jaesun Lee. "Experimental and Mathematical Study of Flexible–Rigid Rail Vehicle Riding Comfort and Safety." Applied Sciences 13, no. 9 (April 22, 2023): 5252. http://dx.doi.org/10.3390/app13095252.

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This paper analyses the dynamic behavior of a rail vehicle using experimental and simulation analysis on a multi-rigid–flex body model. The mathematical models are developed considering the car body, bogie frame, and wheel axle for rail vehicles of rigid–flexible and multi-rigid formulations, taking the car body as rigid for the rigid body analysis and the flexible car body for flex–rigid analysis. A finite element model of the car body was developed in ANSYS, and substructure and modal analyses were performed. The mathematical model is validated through an experiment conducted by the Research Design and Standards Organization. Then, the validated model is further analyzed to evaluate the running comfort, using the Sperling ride index and the running safety, by investigating the derailment coefficient and wheel load reduction rate. The impact of flexibility on the vehicle’s running stability is investigated using the rigid body dynamics model and experimental data. Compared to experimental data, the simulation results reveal that elastic vibration cannot be neglected in vehicle dynamics, since the rigid–flexible coupling model is slightly more significant than the rigid-body model for ride comfort and safety.

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6

Bratu, Polidor, and Ovidiu Vasile. "Viscoelastic Model for the Rigid Body Vibrations of a Viaduct Depending on the Support Devices’ Rheological Model." Romanian Journal of Transport Infrastructure 2, no. 2 (December 1, 2013): 1–10. http://dx.doi.org/10.1515/rjti-2015-0014.

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Rezumat Lucrarea abordează comportarea unui model de solid-rigid cu anumite simetrii structurale. Aceste simetrii permit simplificarea calculelor (ecuaţii de mişcare) şi, deci, a modelelor matematice. Dacă solidul rigid este conectat la structură prin patru legături elastice, modelul rămâne încă simplu şi uşor de rezolvat, vibraţiile putând fi decuplate în patru subsisteme de mişcare. În final, se prezintă un studiu de caz pentru analiza modală a unui viaduct, modelat precum un corp solid-rigid, rezemat elastic, de pe autostrada Transilvania (km 29+602.75 m).

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7

Kang, Jaeyoung. "Squeal propensity due to rigid modes of brake pad." Proceedings of the Institution of Mechanical Engineers, Part C: Journal of Mechanical Engineering Science 228, no. 12 (December 2, 2013): 2100–2109. http://dx.doi.org/10.1177/0954406213515200.

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This paper examines the squeal propensity associated with the rigid motion of a brake pad. For the description of the rigid motion, the brake pad is analytically modeled as a composite annular sector plate with both the back plate and friction material rigid. The friction material is subject to friction contact with a rotating disc. The vibration modes of the rigid pad consist of the six rigid modes including three rotation and three translation modes coupled with contact stiffness. The analytical formulation for the dynamic motion of the composite rigid pad is presented. From the numerical calculation, the rigid pad modes are shown to be coupled with one another and thus generate the modal instability in both finite element full model and simplified pad model. It is suggested that the squeal propensity of the rigid pad modes can be estimated by using the simplified pad model and controlled by the certain design modification such as the contact area.

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8

Fan, Hong Chao, Feng Lian Niu, and Rong Liang. "Rigid Body Orientation Analysis Model Based on Stereo Vision." Applied Mechanics and Materials 707 (December 2014): 372–76. http://dx.doi.org/10.4028/www.scientific.net/amm.707.372.

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In order to satisfy the orientation measuring requirements of rigid-body such as work piece, cutting tool in industry, the paper presents a binocular vision detection technique based on spatial position information of markers to extract rigid-body pose information and analyzes the pose accuracy of rigid-body using the principal component analysis (PCA) when spatial position error of markers exist. The simulation experiment demonstrates the maximum angle error of orientation is about 0.59 degree when the position error of markers satisfy the Gaussian distribution with the mean is zero and the standard deviation is 0~3mm. The experimental results verify this method can robustly solve the orientation of rigid body using the position information of markers with position errors, and it provides a theoretical and experimental basis for orientation measurement of rigid body.

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9

Hu, Wengang, and Na Liu. "Comparisons of finite element models used to predict bending strength of mortise-and-tenon joints." BioResources 15, no. 3 (June 10, 2020): 5801–11. http://dx.doi.org/10.15376/biores.15.3.5801-5811.

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This study aimed to obtain a better method for establishing a finite element model of mortise-and-tenon (M-T) joints. Three types of M-T joint finite element models, which included a whole rigid model, a tie rigid model, and a semi-rigid model, were established and compared with experimental results by predicting the bending moment capacity (BMC) of M-T joints based on the finite element method (FEM). The results showed that the semi-rigid model performed much better than the tie rigid model, followed by the whole rigid model. For the semi-rigid model, the ratios of FEM ranged from 0.85 to 1.09. For the whole rigid model and tie rigid model, the BMC of the M-T joint was overestimated. In addition, the results showed that tenon size remarkably affected the BMC and stiffness of the M-T joint, and tenon width had a greater effect on the BMC of the M-T joint than the tenon length.

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10

Devi, Jyoti, Veena Sharma, and Mohini Kapalta. "Electroconvection in Rotating Jeffrey Nanofluid Saturating Porous Medium: Free–Free, Rigid-Free, Rigid–Rigid Boundaries." Journal of Nanofluids 12, no. 6 (June 1, 2023): 1554–65. http://dx.doi.org/10.1166/jon.2023.2039.

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The impact of rotation and the boundaries on the initiation of convective instability in a rheological nanofluid layer heated beneath saturated by a porous media with the inclusion of an AC electric field (vertical) is studied employing linear stability analysis. The stationary convective stability of rheological nanofluid is customarily established utilizing Buongiorno model for nanoparticles and Jeffrey model for rheological behavior of regular fluid. The Buongiorno model deployed for nanofluids incorporates the influence of thermophoresis and Brownian motion. Using the normal mode technique, the set of coupled differential equations is solved analytically for both stress-free boudaries and numerically by using the Galerkin-type Weighted Residual Method (GWRM) for top-free, bottom-rigid and rigid–rigid bounding surfaces. The numerical computed values of stationary thermal Rayleigh number are presented graphically for three distinct combinations of boundary conditions. The Taylor number accounting for rotation parameter, Jeffrey parameter, and nanofluid Lewis number delay the start of stationary convection, whereas electric field and concentration Rayleigh number destabilize a system for three groups of boundaries. The bottom-/top-heavy nanofluids are found to be more/less stable. Rigid–rigid boundaries augment the stability in a more pronounced manner than that of the stress-free and rigid-free boundaries. The conditions for non-occurrence of over stability are also derived. This study is of great significance in many metallurgical processes including megma flow, deep convective chimneys, polymer solutions, microfluidic devices and blood flow in micro circulatory systems. An excellent coincidence is found admist present paper and the earlier published work.

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11

Suh, Jungsoo, and Steven H. Frankel. "Comparing turbulence models for flow through a rigid glottal model." Journal of the Acoustical Society of America 123, no. 3 (March 2008): 1237–40. http://dx.doi.org/10.1121/1.2836783.

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12

Ahuja, Jyoti, and Urvashi Gupta. "Rayleigh-Bénard Convection for Nanofluids for More Realistic Boundary Conditions (Rigid-Free and Rigid-Rigid) Using Darcy Model." International Journal of Mathematical, Engineering and Management Sciences 4, no. 1 (February 1, 2019): 139–56. http://dx.doi.org/10.33889/ijmems.2019.4.1-013.

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In this article, Rayleigh-Bénard convection for nanofluids for more realistic boundary conditions (rigid-free and rigid-rigid) under the influence of the magnetic field is investigated. Presence of nanoparticles in base fluid has introduced one additional conservation equation of nanoparticles that incorporates the effect of thermophoretic forces and Brownian motion and the inclusion of magnetic field has introduced Lorentz’s force term in the momentum equation along with Maxwell’s equations. The solution of the Eigen value problem is found in terms of Rayleigh number by implementing the technique of normal modes and weighted residual Galerkin approximation. It is found that the stationary as well as oscillatory motions come into existence and heat transfer takes place through oscillatory motions. The critical Rayleigh number for alumina water nanofluid has an appreciable increase in its value with the rise in Chandrasekhar number and it increases moderately as we move from rigid-free to both rigid boundaries. The effect of different nanofluid parameters on the onset of thermal convection for two types of boundaries is investigated.

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13

Baraldi, Daniele, Claudia Brito De Carvalho Bello, Antonella Cecchi, and Filippo Ubertini. "Refined Rigid Block Model for In-Plane Loaded Masonry." Advances in Civil Engineering 2020 (September 29, 2020): 1–13. http://dx.doi.org/10.1155/2020/8844759.

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In this work, a refined rigid block model is proposed for studying the in-plane behavior of regular masonry. The rigid block model is based on an existing discrete/rigid model with rigid blocks and elastoplastic interfaces that already proven its effectiveness in representing masonry behavior in linear and nonlinear fields. In this case, the proposed model is improved by assuming rigid quadrilateral elements connected by one-dimensional nonlinear interfaces, which are adopted both to represent mortar (or dry) joints between the blocks and also to represent inner potential cracks into the blocks. Furthermore, the softening behavior of interfaces in tension and shear is taken into account. Several numerical tests are performed by considering masonry panels with regular texture subjected to compression and shear. Particular attention is given to the collapse mechanisms and the pushover curves obtained numerically and compared with existing numerical and laboratory results. Furthermore, the numerical tests aim to evaluate the applicability limits of the proposed model with respect to existing results.

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14

Guan, Hsin, Chun Guang Duan, and Ping Ping Lu. "The Friction Model of Dynamic-Wheel Model Based on LuGre Model." Applied Mechanics and Materials 556-562 (May 2014): 4288–92. http://dx.doi.org/10.4028/www.scientific.net/amm.556-562.4288.

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With the development of the simulator and the increase of vehicle model simulation frequency, the ring tire models become the research focus. The ring model considers the physical characteristics of the tire, thus it can more accurately describe the tire force transmission. State Key Laboratory of Automotive Simulation and Control of Jilin University has developed a dynamic wheel model. This model takes the tire crown part as a rigid-ring and describes the elasticity of the tire by using six spring-dampers to connect the rigid-ring with the wheel rim. This paper focuses on the logical judgment of dynamic, static friction between tire and road. Based on the logical analysis, the tire forces at transient process are researched in order to avoid oscillation. Based on the C language to build simulation program, and embed it into complex vehicle model to simulate different conditions, the simulation results show that the vehicle can start smoothly.

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15

Tůma, Jiří, and Jolana Škutová. "Matlab & Simulink Model of Rigid Rotors." Transactions of the VŠB - Technical University of Ostrava, Mechanical Series 57, no. 2 (December 30, 2011): 169–76. http://dx.doi.org/10.22223/tr.2011-2/1885.

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16

Khaimovich, A. I., M. A. Bolotov, and E. Yu Pechenina. "Model of virtual balancing of rigid rotors." VESTNIK of Samara University. Aerospace and Mechanical Engineering 21, no. 1 (April 27, 2022): 99–109. http://dx.doi.org/10.18287/2541-7533-2022-21-1-99-109.

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Rotor imbalances have a significant impact on the level of their vibration and reliability. Reduction of rotor imbalances is achieved through static and dynamic balancing that we propose to accomplish by virtual balancing of rigid rotors in two stages. At the first stage mutual orientation of the rotor parts is calculated to compensate their imbalances and couple unbalance. At the second stage the values of the masses and angular coordinates of two correction weights that allow eliminating the residual imbalance of the rotor are determined. The correction weights are placed in two balancing planes of the rotor. A model of virtual balancing is proposed to implement the balancing stages. The model makes it possible to determine the relative angular positions of the rotor parts, the values of the mass of two correction weights and their angular coordinates in the balancing planes. The effectiveness of using the proposed model was verified by performing calculations using the finite element model (FEM) of the rotor in the ANSYS software package. In the course of the study, data were obtained on the values of vibration velocities on the rotor supports. The results obtained show a significant reduction in the vibration velocities of the supports, amounting to 80% of their initial value.

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17

Rollings, R. S., and M. W. Witczak. "Structural Deterioration Model for Rigid Airfield Pavements." Journal of Transportation Engineering 116, no. 4 (July 1990): 479–91. http://dx.doi.org/10.1061/(asce)0733-947x(1990)116:4(479).

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18

Usmani, A. A., M. A. Alvi, and I. Ahmad. "A correction to the rigid-projectile model." Journal of Physics G: Nuclear and Particle Physics 15, no. 11 (November 1, 1989): 1667–80. http://dx.doi.org/10.1088/0954-3899/15/11/011.

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19

Reich, Johannes, and Wolfgang J. Daunicht. "A rigid body model of the forearm." Journal of Biomechanics 33, no. 9 (September 2000): 1159–68. http://dx.doi.org/10.1016/s0021-9290(00)00039-7.

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20

Wolf, Guy, Stephane Mallat, and Shihab Shamma. "Rigid Motion Model for Audio Source Separation." IEEE Transactions on Signal Processing 64, no. 7 (April 2016): 1822–31. http://dx.doi.org/10.1109/tsp.2015.2508787.

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21

Lau, Y. H., M. Braun, and B. F. Hutton. "Deformable grid model for non-rigid registration." Nuclear Medicine Communications 20, no. 4 (April 1999): 373. http://dx.doi.org/10.1097/00006231-199904000-00050.

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22

Saccon, A., J. Hauser, and A. Beghi. "Trajectory Exploration of a Rigid Motorcycle Model." IEEE Transactions on Control Systems Technology 20, no. 2 (March 2012): 424–37. http://dx.doi.org/10.1109/tcst.2011.2116788.

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23

Wu, Fu-Hsiang, and Wai-Fah Chen. "A design model for semi-rigid connections." Engineering Structures 12, no. 2 (April 1990): 88–97. http://dx.doi.org/10.1016/0141-0296(90)90013-i.

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24

Hu�tink, J., A. H. Van den Boogaard, A. D. Rietman, J. Lof, and T. Meinders. "A mixed elastoplastic/rigid-plastic material model." International Journal for Numerical Methods in Engineering 46, no. 9 (November 30, 1999): 1421–34. http://dx.doi.org/10.1002/(sici)1097-0207(19991130)46:9<1421::aid-nme706>3.0.co;2-p.

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25

Tokad, Yilmaz. "A network model for rigid-body motion." Dynamics and Control 2, no. 1 (February 1992): 59–82. http://dx.doi.org/10.1007/bf02169806.

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26

Raković, Saša V. "The implicit rigid tube model predictive control." Automatica 157 (November 2023): 111234. http://dx.doi.org/10.1016/j.automatica.2023.111234.

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27

Yu, Yue-Qing, Peng Zhou, and Qi-Ping Xu. "Kinematic and dynamic analysis of compliant mechanisms considering both lateral and axial deformations of flexural beams." Proceedings of the Institution of Mechanical Engineers, Part C: Journal of Mechanical Engineering Science 233, no. 3 (February 26, 2018): 1007–20. http://dx.doi.org/10.1177/0954406218760956.

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The kinematic and dynamic analysis of compliant mechanisms is investigated comprehensively in this work. Based on the pseudo-rigid-body model, a new PR model is proposed to simulate both the lateral and axial deformations of flexural beams in compliant mechanisms. An optimization for the characteristic factors and a linear regression for the stiffness coefficients of PR pseudo-rigid-body model are presented. Compared with the 1R and 2R pseudo-rigid-body model, the advantage of the PR model is well illustrated. The dynamic modeling of flexible beams in compliant mechanisms is then developed based on the PR pseudo-rigid-body model. The dynamic equation of a PR pseudo-rigid-body dynamic model is derived and the dynamic responses are then presented. The kinematic and dynamic analysis of a compliant slider-crank mechanism is presented by the 1R, 2R and PR model, respectively. The effectiveness of pseudo-rigid-body models and the superiorities of the PR pseudo-rigid-body model and PR pseudo-rigid-body dynamic model are shown clearly in the numerical example.

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28

Yu, Yue-Qing, Qian Li, and Qi-Ping Xu. "Pseudo-rigid-body dynamic modeling and analysis of compliant mechanisms." Proceedings of the Institution of Mechanical Engineers, Part C: Journal of Mechanical Engineering Science 232, no. 9 (May 11, 2017): 1665–78. http://dx.doi.org/10.1177/0954406217707547.

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An intensive study on the dynamic modeling and analysis of compliant mechanisms is presented in this paper based on the pseudo-rigid-body model. The pseudo-rigid-body dynamic model with single degree-of-freedom is proposed at first and the dynamic equation of the 1R pseudo-rigid-body dynamic model for a flexural beam is presented briefly. The pseudo-rigid-body dynamic models with multi-degrees-of-freedom are then derived in detail. The dynamic equations of the 2R pseudo-rigid-body dynamic model and 3R pseudo-rigid-body dynamic model for the flexural beams are obtained using Lagrange equation. Numerical investigations on the natural frequencies and dynamic responses of the three pseudo-rigid-body dynamic models are made. The effectiveness and superiority of the pseudo-rigid-body dynamic model has been shown by comparing with the finite element analysis method. An example of a compliant parallel-guiding mechanism is presented to investigate the dynamic behavior of the mechanism using the 2R pseudo-rigid-body dynamic model.

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29

KURNIA, JUNDIKA CANDRA, ERIK BIRGERSSON, and ARUN S. MUJUMDAR. "A PHENOMENOLOGICAL MODEL FOR HYDROGELS WITH RIGID SKIN FORMATION." International Journal of Applied Mechanics 04, no. 01 (March 2012): 1250007. http://dx.doi.org/10.1142/s1758825112001361.

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A phenomenological model for stimuli sensitive hydrogels immersed in water subject to changes in temperature is presented and analyzed. In short, the model takes into account conservation of mass and momentum for polymer network and interstitial fluid with an expression for permeability to capture the rigid skin formation during shrinking. The nature of this expression is secured from the observation of and validation with experimental deformation kinetics. Overall, good agreement is achieved between model predictions and their experimental counterparts; the rigid skin formation and rigid core presence are also captured reasonably well. The model can be extended to account for arbitrary-shaped hydrogels as well as for other types of stimuli-sensitive hydrogels that exhibit rigid-skin formation during shrinking.

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30

Gao, Pu, Yong Chang Du, and Huai Cheng Xia. "Treatment of Substructure Rigid-Body Modes in Close-Loop Coupling Disc Brake Squeal Model." Applied Mechanics and Materials 668-669 (October 2014): 298–301. http://dx.doi.org/10.4028/www.scientific.net/amm.668-669.298.

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It’s found that the rigid-body modes of brake pads and brake caliper have significant influence on squeal occurrence while analyzing disc brake squeal problems using close-loop coupling disc brake squeal model. The modal shapes of these rigid-body modes calculated from finite element method (FEM) are linear combination of multiple translational and rotational motions, which is unfavorable for further analysis. In this paper, method to achieve ‘pure’ rigid-body modes such as translations along and rotations on its principal axes of inertia is presented. Modal shapes derived from this method consist with those from FEM model under suitable constraints. The result is used in substructure modal composition analysis on a disc brake squeal problem, where the effects of specific rigid-body modes can be shown clearly. The method is helpful for researchers to choose right measures to suppress squeals.

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31

Ajani, Ibrahim, and Cong Lu. "Assembly variation analysis of the non-rigid assembly with a deformation gradient model." Assembly Automation 42, no. 1 (November 18, 2021): 40–53. http://dx.doi.org/10.1108/aa-07-2021-0092.

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Purpose This paper aims to develop a mathematical method to analyze the assembly variation of the non-rigid assembly, considering the manufacturing variations and the deformation variations of the non-rigid parts during the assembly process. Design/methodology/approach First, this paper proposes a deformation gradient model, which represents the deformation variations during the assembly process by considering the forces and the self-weight of the non-rigid parts. Second, the developed deformation gradient models from the assembly process are integrated into the homogenous transformation matrix to model the deformation variations and manufacturing variations of the deformed non-rigid part. Finally, a mathematical model to analyze the assembly variation propagation is developed to predict the dimensional and geometrical variations due to the manufacturing variations and the deformation variations during the assembly process. Findings Through the case study with a crosshead non-rigid assembly, the results indicate that during the assembly process, the individual deformation values of the non-rigid parts are small. However, the cumulative deformation variations of all the non-rigid parts and the manufacturing variations present a target value (w) of −0.2837 mm as compared to a target value of −0.3995 mm when the assembly is assumed to be rigid. The difference in the target values indicates that the influence of the non-rigid part deformation variations during the assembly process on the mechanical assembly accuracy cannot be ignored. Originality/value In this paper, a deformation gradient model is proposed to obtain the deformation variations of non-rigid parts during the assembly process. The small deformation variation, which is often modeled using a finite-element method in the existing works, is modeled using the proposed deformation gradient model and integrated into the nominal dimensions. Using the deformation gradient models, the non-rigid part deformation variations can be computed and the accumulated deformation variation can be easily obtained. The assembly variation propagation model is developed to predict the accuracy of the non-rigid assembly by integrating the deformation gradient models into the homogeneous transformation matrix.

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32

Steigmann, David J. "On pseudo-rigid bodies." Proceedings of the Royal Society A: Mathematical, Physical and Engineering Sciences 462, no. 2066 (December 13, 2005): 559–65. http://dx.doi.org/10.1098/rspa.2005.1573.

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The concept of the pseudo-rigid body , a model of hypothetical bodies constrained to deform homogeneously, is discussed critically. An analysis is given of a recent attempt, published in this journal, to establish this model on the basis of continuum mechanics.

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33

Rodríguez González, César Antonio, Julio José Caparrós-Mancera, José Antonio Hernández-Torres, and Ángel Mariano Rodríguez-Pérez. "Nonlinear Analysis of Rotational Springs to Model Semi-Rigid Frames." Entropy 24, no. 7 (July 9, 2022): 953. http://dx.doi.org/10.3390/e24070953.

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This paper explains the mathematical foundations of a method for modelling semi-rigid unions. The unions are modelled using rotational rather than linear springs. A nonlinear second-order analysis is required, which includes both the effects of the flexibility of the connections as well as the geometrical nonlinearity of the elements. The first task in the implementation of a 2D Beam element with semi-rigid unions in a nonlinear finite element method (FEM) is to define the vector of internal forces and the tangent stiffness matrix. After defining the formula for this vector and matrix in the context of a semi-rigid steel frame, an iterative adjustment of the springs is proposed. This setting allows a moment–rotation relationship for some given load parameters, dimensions, and unions. Modelling semi-rigid connections is performed using Frye and Morris’ polynomial model. The polynomial model has been used for type-4 semi-rigid joints (end plates without column stiffeners), which are typically semi-rigid with moderate structural complexity and intermediate stiffness characteristics. For each step in a non-linear analysis required to adjust the matrix of tangent stiffness, an additional adjustment of the springs with their own iterative process subsumed in the overall process is required. Loops are used in the proposed computational technique. Other types of connections, dimensions, and other parameters can be used with this method. Several examples are shown in a correlated analysis to demonstrate the efficacy of the design process for semi-rigid joints, and this is the work’s application content. It is demonstrated that using the mathematical method presented in this paper, semi-rigid connections may be implemented in the designs while the stiffness of the connection is verified.

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34

BAĞCI, GŎKHAN B., RAMAZAN SEVER, and CEVDET TEZCAN. "NON-EXTENSIVE STUDY OF RIGID AND NON-RIGID ROTATORS." Modern Physics Letters B 18, no. 11 (May 10, 2004): 467–77. http://dx.doi.org/10.1142/s0217984904007098.

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The isotropic rigid and non-rigid rotators in the framework of Tsallis statistics are studied in the high and low temperature limits. The generalized partition functions, internal energies and heat capacities are calculated. Classical results of the Boltzmann–Gibbs statistics have been recovered as non-extensivity parameter approaches to 1. It has also been observed that non-extensivity parameter q behaves like a scale parameter in the low temperature regime of the rigid rotator model.

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35

Villaggio, Piero. "How to Model a Bonded Joint." Journal of Applied Mechanics 56, no. 3 (September 1, 1989): 590–94. http://dx.doi.org/10.1115/1.3176132.

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The problem is considered of a semi-infinite plane region bonded to a rigid region, with the boundary of contact being in the shape of a cosine curve. It is shown that, when a rigid displacement is applied to the boundary of the elastic region, there is a particular value of the amplitude of the contact curve that minimizes the sum of the strain energy and adhesion energy.

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36

Yin, Hai Jun, Guang Yao Yuan, and Rui Jie Zhang. "Equivalent Space Rigid Frame Model of Pile-Group Foundation." Advanced Materials Research 243-249 (May 2011): 1788–93. http://dx.doi.org/10.4028/www.scientific.net/amr.243-249.1788.

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The paper suggests a space rigid frame model which is equivalent to the space flexibility of pile-group foundation. Firstly, calculating the flexibility of pile-group foundation with “m” method, then the formulas to calculate geometrical parameters such as height of the rigid frame, length and width of the column section, as well as distance between the columns are deduced. So the equivalent rigid frame is acquired exclusively by these parameters. Finally ,discussing the accurate simulation of vertical flexibility and tensional flexibility. Which are achieved by additional springs.

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37

Aryanto, Salam. "IMPLEMENTASI RIGID BODY PADA RIGGING TERHADAP ANIMASI DINAMIS MODEL KENDARAAN TIGA DIMENSI." Angkasa: Jurnal Ilmiah Bidang Teknologi 10, no. 1 (May 23, 2018): 77. http://dx.doi.org/10.28989/angkasa.v10i1.216.

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Semakin berkembangnya teknologi, proses pemodelan dalam tiga dimensi saat ini menjadi jauh lebih mudah dari sebelumnya. Namun sebelum menganimasikan sebuah objek tiga dimensi memerlukan rigging secara manual untuk menentukan struktur kerangka internalnya. Peneliti akan melakukan eksperimen dengan beberapa skenario percobaan terhadap proses rigging untuk menghasilkan animasi kendaraan yang dinamis dengan memanfaatkan rigid body. Dalam hal ini implementasi rigid body pada rigging dilakukan karena rigid body sangat mirip dengan objek di dunia nyata. Memiliki gaya gravitasi dan gaya lainnya, seperti bisa bertumbukan dengan objek lain dan bisa saling mendorong antar objek. Secara khusus sistem rigging dengan mengimplementasikan rigid body pada model kendaraan tiga dimensi yang digunakan sebagai masukan akan menghasilkan rigging yang dapat digunakan untuk menciptakan massa dan gaya sehingga gerakan animasi kendaraan tiga dimensi lebih dinamis. Hasil penelitian ini menunjukkan bahwa Implementasi rigid body pada rigging model kendaraan tiga dimensi menghasilkan animasi yang dinamis karena rigid body dapat disimulasikan secara dinamis berkaitan dengan kontak dan tumbukan, serta objek yang dikendalikan secara dinamis merespon gerakan dan tumbukan dengan benda lain.

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38

Souchay, J. "Rigid-Earth Nutation Models." International Astronomical Union Colloquium 180 (March 2000): 190–95. http://dx.doi.org/10.1017/s0252921100000282.

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AbstractDespite the fact that the main causes of the differences between the observed Earth nutation and that derived from analytical calculations come from geophysical effects associated with nonrigidity (core flattening, core-mantle interactions, oceans, etc…), efforts have been made recently to compute the nutation of the Earth when it is considered to be a rigid body, giving birth to several “rigid Earth nutation models.” The reason for these efforts is that any coefficient of nutation for a realistic Earth (including effects due to nonrigidity) is calculated starting from a coefficient for a rigid-Earth model, using a frequency-dependent transfer function. Therefore it is important to achieve high quality in the determination of rigid-Earth nutation coefficients, in order to isolate the nonrigid effects still not well-modeled.After reviewing various rigid-Earth nutation models which have been established recently and their relative improvement with respect to older ones, we discuss their specifics and their degree of agreement.

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39

Lei, Liu. "A Multibody System Model for Meshing Gears." Applied Mechanics and Materials 44-47 (December 2010): 1273–78. http://dx.doi.org/10.4028/www.scientific.net/amm.44-47.1273.

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As a type of numerical approach to dynamics of gears, multibody dynamics method can handle realistic cases of contact modeling with acceptable accuracy and considerably less computational effort. The ability to simulate contact between teeth has become an essential topic in multibody dynamics. Fully rigid method is not suited for a high quality of the analysis to take into account some elasticity in the model of meshing gear wheels. In our new approach the circumferentially rotatable rigid teeth and elastic elements composed of rotational spring-damper combinations are hereby put forward. The teeth and the body of each gear wheel are still regarded as rigid bodies, but they are connected with each other by elastic elements. Besides, Lankarani & Nikravesh Contact Model is utilized, which counts energy dissipation by means of viscous damping. Both large motions with revolutions and important elasticity are considered in this teeth-wheel multibody system model. Two examples are provided in which the simulation results of completely rigid method, the approach in [10], our new approach and finite element methods are compared. Comparisons indicate that our newly developed approach is more suitable for modeling multibody geared systems.

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40

Wang, H. N., X. W. Hou, and X. P. Su. "Application of Rigid-Flexible Coupling in Stiffness Calculation of Double Wishbone Suspension." Applied Mechanics and Materials 214 (November 2012): 161–64. http://dx.doi.org/10.4028/www.scientific.net/amm.214.161.

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Based on multi-body Dynamics theory, the 1/4 multi-rigid model of double wishbone suspension of automobile in ADAMS/View is created, and use ANSYS software to analyze torsion beam flexibility. Furthermore, the rigid-flexibility model has been created and the rigid change of suspension line along with the tire dynamics change is simulated. The result shows that the rigid-flexible coupling model is more accuracy than the multi-rigid one and fits the practical situation even better. This paper proposes an efficient method for analyzing the rigid of double-wishbone suspension vertical line.

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41

DU, Songlin, and Takeshi IKENAGA. "Hierarchical Progressive Trust Model for Mismatch Removal under Both Rigid and Non-Rigid Transformations." IEICE Transactions on Fundamentals of Electronics, Communications and Computer Sciences E101.A, no. 11 (November 1, 2018): 1786–94. http://dx.doi.org/10.1587/transfun.e101.a.1786.

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42

KAZAMA, Motoki, and Takamasa INATOMI. "Earthquake response analyses for embedded rigid structures using a rigid body-ground spring model." Doboku Gakkai Ronbunshu, no. 410 (1989): 425–34. http://dx.doi.org/10.2208/jscej.1989.410_425.

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43

Shen, Chi Chih. "Discussion on Finite Element Model for Three Dimensional Rolling Process Analysis." Applied Mechanics and Materials 496-500 (January 2014): 452–55. http://dx.doi.org/10.4028/www.scientific.net/amm.496-500.452.

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A three dimensional numerical simulation model of metal rolling formation is developed from the theoretical model. In this theoretical model, the two variables of element deformation and temperature variation are placed in a variable matrix. The thermal elastic plastic rigid matrix and heat transfer rigid matrix are placed in the same expansion rigid matrix. Furthermore, the numerical simulation analytical model developed in this paper was used to simulate aluminum strip rolling.

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44

Prasad, Yenumula VSN, and T. R. Chari. "Rigid pile with a baseplate under large moments: laboratory model evaluations." Canadian Geotechnical Journal 33, no. 6 (December 1, 1996): 1021–26. http://dx.doi.org/10.1139/t96-129.

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Results of tests on a rigid embedded pile with baseplate are presented. Laboratory tests were conducted with an instrumented 102 mm rigid circular pile embedded in sand and subjected to combined moment and horizontal load. Two different backfills and two different baseplates were used. The rotation of pile and the soil pressure distributions along the length of the pile and at the bottom of the baseplate were measured. It was found that the moment carrying capacity of a rigid pile can be increased between 25 and 50% by using a baseplate. The investigations reported in this paper are useful in the design of directly embedded transmission-pole foundations. Key words:baseplate, model tests, rigid pile, sand, transmission poles, ultimate moment.

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45

Na, SD, DW Park, and WS Yoo. "Rigid ring with Bouc–Wen tire model for vehicle dynamic analysis." Proceedings of the Institution of Mechanical Engineers, Part C: Journal of Mechanical Engineering Science 231, no. 19 (May 10, 2016): 3530–40. http://dx.doi.org/10.1177/0954406216647416.

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Tires are one of the main automobile components that affect driving performance and ride quality. The rigid ring tire model had been widely used to characterise a vehicle rolling over uneven road surfaces. The stiffness of an rigid ring tire is calculated in the quasi-static state; however, this model is limited in its ability to represent the dynamic response of a tire. In this study, a Bouc–Wen type force element was included in the rigid ring tire model to enhance the dynamic response of a tire, and the effectiveness of the proposed rigid ring with Bouc–Wen model was demonstrated. To validate the proposed rigid ring with Bouc–Wen tire model, two experiments were performed. The first one was performed using a flat-trac test system, and the second one was a full-car test performed over a single cleat by using accelerometers and velocity sensors. For the vehicle dynamic simulation, the equations of motion of the vehicle were established using a functional suspension model defined in terms of the kinematic and compliance characteristics of the wheel and chassis. The simulation results obtained using the proposed rigid ring with Bouc–Wen tire model were compared with the experimental results, which showed both efficiency and accuracy of the propsed model.

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46

Chen, Lin, and Hua Deng. "Model Reduction of Rigid-Flexible Manipulators with Experimental Validation." Advanced Materials Research 655-657 (January 2013): 1101–7. http://dx.doi.org/10.4028/www.scientific.net/amr.655-657.1101.

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An investigation into the dynamic modeling of rigid-flexible manipulator systems based on spectral approximation methods was presented. The nonlinear dynamic equation of the rigid-flexible manipulator was established on the theory of Lagrange equation and the model was approximated with the spectral approximation method. Furthermore, an experimental platform system was set up to validate the effectiveness of the model. Simulation results of the response of the rigid-flexible manipulators were presented. Moreover, experimental validations were carried out to assess the effectiveness of the modeling approach by comparing with the simulation results. The results verified that the method is effective and feasible.

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47

Ge, Xu Kun, Da Wei Liu, and Bin Tian. "Dynamic Analysis of Lifting Mechanism Based on Rigid-Flexible Coupling." Advanced Materials Research 849 (November 2013): 411–16. http://dx.doi.org/10.4028/www.scientific.net/amr.849.411.

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To obtain realistic dynamic characteristics of the lifting mechanism, the liftarm and drawbar were regarded as flexible bodies. The modal neutral file (MNF) of liftarm and drawbar were obtained from modal analysis conducted by finite element analysis (FEA) software MSC.Patran/Nastran . Then the MNF were translated into ADAMS, a rigid-flexible coupling model of the lift mechanism was built by replacing the rigid bodies with MNF. The forces of each hinge points in the rigid-flexible system, which were obtained from dynamic analysis, were compared with the rigid ones. The results showed that forces obtained from the rigid-flexible system were smaller than the rigid ones, which provided a reference for the design and improvement of the lifting mechanism.

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48

Souchay, J. "New series of rigid and non rigid Earth nutation. Comparison with observations." Symposium - International Astronomical Union 172 (1996): 239–42. http://dx.doi.org/10.1017/s0074180900127457.

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After analysing the recent developments of the theory of the nutation for a simplified rigid Earth model (Kinoshita and Souchay, 1990) with new corrections and new contributions (Williams, 1994; Souchay and Kinoshita, 1996), we will study the effect of these developments on the calculation of the coefficients of nutation for a non rigid Earth model, based on the transfer function given by Wahr (1979). The relative improvements characterized by the residuals with the observations are explained in the following.

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49

Yoder, C. F., and E. R. Ivins. "Improved Analytic Nutation Model." Symposium - International Astronomical Union 129 (1988): 379–80. http://dx.doi.org/10.1017/s0074180900135077.

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Models describing earth's nutations can be separated into two major components, plus several small perturbations, of which ocean tides and solid friction are the most significant. The primary element of a successful model is an accurate rigid earth nutation theory. The effect of mantle elasticity and differential nutation of the fluid core is then obtained as a correction factor which multiplies the rigid body result. Wahr's (1981) theory is certainly the most sophisticated elastodynamic response model. However, we have found that the simple model of Sasao et al., (1980) differs from Wahr's theory term by term by less than 0.3mas if a modern earth structure model (1066B) is used to evaluate the nutation structure constants.

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50

Zhao, Shen, Xue Yi You, Sheng Jun Liu, Yu Huang, Feng Shi, and Hong Bo Lu. "On the Rigid-Lid Hypothesis Application to the Flow Simulation of Step-Feed A/O Process." Advanced Materials Research 886 (January 2014): 319–22. http://dx.doi.org/10.4028/www.scientific.net/amr.886.319.

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The feasibility of the rigid-lip hypothesis was studied in the flow field simulation of the reaction tank in the step-feed A/O process. Two models were built. One model applied the rigid-lip hypothesis was called as rigid-lid model and the other was called free surface model. The results showed that the velocity distribution of the rigid-lid model is basically consistent with that of the free-surface model. On the vertical monitor sections, the error of the mean velocity between the two models is less than 8%. The results showed that the much less expensive rigid-lid model is applicable to simulate the flow field of reaction tank.

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