Relevant bibliographies by topics / Meshing; Gear mesh stiffness

Contents

  1. Journal articles
  2. Dissertations / Theses
  3. Book chapters
  4. Conference papers

Academic literature on the topic 'Meshing; Gear mesh stiffness'

Author: Grafiati
Published: 4 June 2021
Last updated: 15 February 2022

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Journal articles on the topic "Meshing; Gear mesh stiffness"

1

Cui, Lingli, Tongtong Liu, Jinfeng Huang, and Huaqing Wang. "Improvement on Meshing Stiffness Algorithms of Gear with Peeling." Symmetry 11, no. 5 (May 1, 2019): 609. http://dx.doi.org/10.3390/sym11050609.

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This paper investigates the effect of a gear tooth peeling on meshing stiffness of involute gears. The tooth of the gear wheel is symmetric about the axis, and its symmetry will change after the gear spalling, and its meshing stiffness will also change during the meshing process. On this basis, an analytical model was developed, and based on the energy method a meshing stiffness algorithm for the complete meshing process of single gear teeth with peeling gears was proposed. According to the influence of the change of meshing point relative to the peeling position on the meshing stiffness, this algorithm calculates its stiffness separately. The influence of the peeling sizes on mesh stiffness is studied by simulation analysis. As a very important parameter, the study of gear mesh stiffness is of great significance to the monitoring of working conditions and the prevention of sudden failure of the gear box system.
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2

Zhang, Donglin, Rupeng Zhu, Bibo Fu, and Wuzhong Tan. "Mesh Phase Analysis of Encased Differential Gear Train for Coaxial Twin-Rotor Helicopter." Mathematical Problems in Engineering 2019 (July 25, 2019): 1–9. http://dx.doi.org/10.1155/2019/8421201.

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Dynamic excitation caused by time-varying meshing stiffness is one of the most important excitation forms in gear meshing process. The mesh phase relations between each gear pair are an important factor affecting the meshing stiffness. In this paper, the mesh phase relations between gear pairs in an encased differential gear train widely used in coaxial twin-rotor helicopters are discussed. Taking the meshing starting point where the gear tooth enters contact as the reference point, the mesh phase difference between adjacent gear pairs is analyzed and calculated, the system reference gear pair is selected, and the mesh phase difference of each gear pair relative to the system reference gear pair is obtained. The derivation process takes into account the modification of the teeth, the processing, and assembly of the duplicate gears, which makes the calculation method and conclusion more versatile. This work lays a foundation for considering the time-varying meshing stiffness in the study of system dynamics, load distribution, and fault diagnosis of compound planetary gears.
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Muhammad, Arif Abdullah, and Guang Lei Liu. "Time Varying Meshing Stiffness of Cracked Sun and Ring Gears of Planetary Gear Train." Applied Mechanics and Materials 772 (July 2015): 164–68. http://dx.doi.org/10.4028/www.scientific.net/amm.772.164.

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The time varying meshing stiffness of normal and cracked spur gears of planetary gear train is studied by applying the unit normal forces at mesh point on the face width along the line of action of the single gear tooth in FE based software Ansys Workbench 14.5. The tooth deflections due to the applied forces at one mesh point are noted and a deflection matrix is established which is solved using Matlab to get net deflection and finally the meshing stiffness of gear tooth at particular mesh point. The process is repeated for other mesh points of gear tooth by rotating it to get meshing stiffness for whole gear tooth.
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Yin, Jiao. "Analysis of Gear Static Transmission Error and Mesh Stiffness." Applied Mechanics and Materials 365-366 (August 2013): 327–30. http://dx.doi.org/10.4028/www.scientific.net/amm.365-366.327.

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In this paper, the object of study is one pair increasing gear with building a two-dimensional plane model in ANSYS. According to the gears meshing theory, considering the gear deformation, solve the static transmission error and the gear mesh stiffness in different conditions. The influence of the centre errors on static transmission error and mesh Stiffness are basis for modal analysis based on the mesh stiffness of gear and unbalanced harmonic response.
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Huo, Chun Jing, Hui Liu, Zhong Chang Cai, and Ming Zheng Wang. "Non-Linear Vibration Modeling and Simulation of a Gear Pair Based on ADAMS and Simulink." Advanced Materials Research 681 (April 2013): 219–23. http://dx.doi.org/10.4028/www.scientific.net/amr.681.219.

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To set up the virtual prototype of a gear train system in the dynamic analysis software ADAMS, the torsional vibration model of a gear pair was transformed into an equivalent transmission model in which a multi-body model was established in ADAMS and its meshing force solution model was established in Simulink. The time-varying mesh stiffness, gear clearance, meshing errors and other non-linear factors can be included in the gear meshing feedback model, more importantly, the influence of gear speed fluctuation on the time-varying mesh stiffness was taken into consideration. The simulation results contrastively prove the feasibility of co-simulation for obtaining the dynamic characteristics of gear meshing process.
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Wang, Feng, Zong De Fang, and Sheng Jin Li. "Nonlinear Dynamic Analysis of Helical Gear Considering Meshing Impact." Applied Mechanics and Materials 201-202 (October 2012): 135–38. http://dx.doi.org/10.4028/www.scientific.net/amm.201-202.135.

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Comprehensive meshing stiffness and single tooth meshing stiffness are calculated by tooth contact analysis and load tooth contact analysis program. The corner meshing impact model is proposed. Nonlinear dynamic model of helical gear transmission system is established in this paper considering time-varying meshing stiffness excitation, transmission error excitation, corner meshing impact excitation, and the backlash excitation. Take the ship’s helical gear transmission system as an example, the mesh impact force is derived and the primary factors that produce noises are discussed. The effects which the mesh impact brings to vibration characteristics of the gear dynamic system are concluded. Meshing impact has an inevitable effect on the vibration of the dynamic system. Impact excitation costs 8.5% in maximum of vibration acceleration response, 31% in maximum of instantaneous acceleration, and 4.9% in maximum of spectral component amplitude.
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7

Wang, J., and I. Howard. "The torsional stiffness of involute spur gears." Proceedings of the Institution of Mechanical Engineers, Part C: Journal of Mechanical Engineering Science 218, no. 1 (January 1, 2004): 131–42. http://dx.doi.org/10.1243/095440604322787009.

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This paper presents the results of a detailed analysis of torsional stiffness of a pair of involute spur gears in mesh using finite element methods. Adaptive meshing has been employed within a commercial finite element program to reveal the detailed behaviour in the change over region from single- to double-tooth contact zones and vice versa. Analysis of past gear tooth stiffness models is presented including single- and multitooth models of the individual and combined torsional mesh stiffness. The gear body stiffness has been shown to be a major component of the total mesh stiffness, and a revised method for predicting the combined torsional mesh stiffness is presented. It is further shown tha the mesh stiffness and load sharing ratios will be a function of applied load.
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Hu, Yu Mei, De Shuang Xue, and Yang Jun Pi. "Effect of Friction Coefficient on the Stiffness Excitation of Gear." Applied Mechanics and Materials 86 (August 2011): 713–16. http://dx.doi.org/10.4028/www.scientific.net/amm.86.713.

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This study addresses the effect of different friction coefficients on the stiffness excitation of gear using finite element technique. Firstly, the simulation model of single pair of gear teeth mesh is established, and the effect of friction coefficient on the composite stiffness values of the teeth meshing is studied. After that, simulation model of multiple pairs of gear teeth meshing is created and the normal load distributions under different friction coefficients in a single meshing cycle are calculated using quasi-static calculation method. Finally, the relationship between friction coefficient and stiffness excitation of gear system is obtained. The investigation results indicate that at the alternation place of single tooth meshing and double teeth meshing, the stiffness excitation of the system is greater under larger friction coefficient when double teeth meshing change into single tooth meshing, while the opposite situation occur when single tooth meshing change into double teeth meshing. The amplitude value of stiffness variation for single pair of teeth meshing under different friction coefficients is 2.12%, while the amplitude value of teeth loads variation for multiple pairs of teeth meshing under different friction coefficients is 22.87%.
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Xu, Xiangyang, Hongwei Ge, Jijun Deng, Jibo Wang, and Renxiang Chen. "An investigation on dynamic characteristics of herringbone planetary gear system with torsional flexibility between the left and right teeth of the sun gear." Mechanics & Industry 21, no. 6 (2020): 602. http://dx.doi.org/10.1051/meca/2020074.

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Herringbone planetary gear system (HPGS) has high power density and complex structure. The torsional flexibility of the left and right teeth of the sun gear is closely related to the dynamic characteristics of the HPGS. In this research, considering the coordination conditions of both sides torsional stiffness and axial slide of the sun gear, a new dynamic model of the HPGS considering the meshing phase difference between left and right teeth of the sun gear is developed based on the lumped-parameter method, and the influence mechanism of torsional stiffness and axial sliding is studied. Moreover, the dynamic parameters and dynamic characteristics of the HPGS are analyzed in the case of varying torsoinal stiffness and axial slide. The results show that the torsional stiffness of left and right teeth and the axial slide of sun gear have significant impacts on the dynamic parameters and dynamic mesh force response. With the increase of the torsional flexibility (the decrease the torsional stiffness), the sun gear and planet gear meshing stiffness and the maximum tooth surface load are both increased on the left side (input side) and decreased on the right side, but the main peak values and peak frequencies of dynamic response on both sides of the s-p meshing pairs decrease significantly. In addition, when the sun gear slides toward the output side axially, meshing stiffness and dynamic mesh force response main peak values decreased on the left side (input side) and increased on the right side, but the main resonance peaks frequencies keep the same.
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Lin, Jian, and Robert G. Parker. "Mesh Stiffness Variation Instabilities in Two-Stage Gear Systems." Journal of Vibration and Acoustics 124, no. 1 (September 1, 2001): 68–76. http://dx.doi.org/10.1115/1.1424889.

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Mesh stiffness variation, the change in stiffness of meshing teeth as the number of teeth in contact changes, causes parametric instabilities and severe vibration in gear systems. The operating conditions leading to parametric instability are investigated for two-stage gear chains, including idler gear and countershaft configurations. Interactions between the stiffness variations at the two meshes are examined. Primary, secondary, and combination instabilities are studied. The effects of mesh stiffness parameters, including stiffness variation amplitudes, mesh frequencies, contact ratios, and mesh phasing, on these instabilities are analytically identified. For mesh stiffness variation with rectangular waveforms, simple design formulas are derived to control the instability regions by adjusting the contact ratios and mesh phasing. The analytical results are compared to numerical solutions.
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Dissertations / Theses on the topic "Meshing; Gear mesh stiffness"

1

Yao, ShiPing. "Modelling and simulation of vibration signals for monitoring of gearboxes." Thesis, University of Oxford, 1999. http://ethos.bl.uk/OrderDetails.do?uin=uk.bl.ethos.301653.

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Mehdi, Pour Reza. "Transmission DynamicsModelling : Gear Whine Simulation Using AVL Excite." Thesis, KTH, Fordonsdynamik, 2018. http://urn.kb.se/resolve?urn=urn:nbn:se:kth:diva-243090.

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Nowadays, increasing pressure from legislation and customer demands in the automotive industry are forcing manufacturers to produce greener vehicles with lower emissions and fuel consumption.As a result, electrified and hybrid vehicles are a growing popular alternative to traditional internal combustion engines (ICE). The noise from an electric vehicle comes mainly from contact between tyres and road, wind resistance and driveline. The noise emitted from the driveline is for the mostpart related to the gearbox. When developing a driveline, it is a factor of importance to estimate the noise radiating from the gearbox to achieve an acceptable design.Gears are used extensively in the driveline of electric vehicles. As the gears are in mesh, a main intrusive concern is known as gear whine noise. Gear whine noise is an undesired vibroacoustic phenomenon and is likely to originate through the gear contacts and be transferred through themechanical components to the housing where the vibrations are converted into airborne and structure-borne noise. The gear whine noise originates primarily from the excitation coming from transmission error (TE). Transmission error is defined as the difference between the ideal smoothtransfer of motion of a gear and what is in practice due to lack of smoothness.The main objective of this study is to simulate the vibrations generated by the gear whine noise in an electric powertrain line developed by AVL Vicura. The electric transmission used in this study provides only a fixed overall gear ratio, i.e. 9.59, under all operation conditions. It is assumed thatthe system is excited only by the transmission error and the mesh stiffness of the gear contacts. In order to perform NVH analysis under different operating conditions, a multibody dynamics model according to the AVL Excite program has been developed. The dynamic simulations are thencompared with previous experimental measurements provided by AVL Vicura.Two validation criteria have been used to analyse the dynamic behaviour of the AVL Excite model: signal processing using the FFT method and comparison with the experimental measurements.The results from the AVL Excite model show that the FFT criterion is quite successful and all excitation frequencies are properly observed in FFT plots. Nevertheless, when it comes to the second criterion, as long as not all dynamic parameters of the system such as damping or stiffnesscoefficients are provided with certainty in the model, it is too difficult to investigate the accuracy of the AVL Excite model. Another investigation is a numerical design study to analyses how the damping coefficients influence the response. After reducing the damping parameters, the results show that the housing and bearings have the highest influence on the response. If more acceptable results are desired,future studies must be concentrated on these to obtain more acceptable damping values.
För närvarande tvingar ökat tryck från lagstiftning och kundkrav inom bilindustrin tillverkarna attproducera grönare fordon med lägre utsläpp och bränsleförbrukning. Som ett resultat ärelektrifierade och hybridfordon ett växande populärt alternativ till traditionellaförbränningsmotorer (ICE). Bullret från ett elfordon kommer främst från kontakten mellan däckoch väg, vindmotstånd och drivlinan. Bullret från drivlinan är i huvudsak relaterat till växellådan.Vid utveckling av en drivlina är det av betydelse att uppskatta bullret från växellådan för att uppnåen acceptabel design.Utväxlingar används i stor utsträckning i elfordons drivlina. Eftersom kugghjulen är i kontaktuppstår ett huvudproblem som är känt som ett vinande ljud från kugghjulskontakten.Kugghjulsljud är ett oönskat vibro-akustiskt fenomen och uppstår sannolikt på grund avkugghjulkontakterna och överförs via de mekaniska komponenterna till växellådshuset därvibrationerna omvandlas till luftburet och strukturburet ljud. Kugghjulsljudet härstammarhuvudsakligen från exciteringen som kommer från transmissionsfel (TE) i kugghjulskontakten.Överföringsfelet definieras som skillnaden mellan den ideala smidiga rörelseöverföringen hoskugghjulen och rörelsen som sker i verkligheten på grund av ojämnheter.Huvudsyftet med denna studie är att simulera vibrationerna som genereras avkugghjulskontakterna i en elektrisk drivlina utvecklad av AVL Vicura. Den elektriska drivlinan somanvänds i denna studie har endast ett fast utväxlingsförhållande, dvs 9,59, för alladriftsförhållanden. Det antas att systemet är exciterat endast av överföringsfelet och kugghjulensstyvhet i kuggkontakterna. För att kunna utföra NVH-analys under olika driftsförhållanden har enstelkroppsdynamikmodell utvecklats med hjälp av programmet AVL Excite. De dynamiskasimuleringarna jämförs sedan med tidigare experimentella mätningar som tillhandahålls av AVLVicura.Två valideringskriterier har använts för att analysera det dynamiska beteendet hos AVL Excitemodellen:signalbehandling med FFT-metoden och jämförelse med experimentella mätningar.Resultaten från AVL Excite-modellen visar att FFT-kriteriet är ganska framgångsrikt och allaexcitationsfrekvenser observeras korrekt i FFT-diagrammen. Men när det gäller det andra kriteriet,så länge som inte alla dynamiska parametrar i systemet, såsom dämpnings- ellerstyvhetskoefficienter, är tillförlitliga i modellen, är det för svårt att undersöka exaktheten hos AVLExcite-modellen.En annan undersökning som utförts är en numerisk designstudie för att analysera hurdämpningskoefficienterna påverkar responsen. Efter minskning av dämpningsparametrarna visarresultaten att växellådshus och lager har störst inflytande på resultatet. Om mer acceptabla resultatär önskvärda måste framtida studier koncentreras på dessa parametrar för att uppnå mer acceptabladämpningsvärden.
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3

Mehdi, Pour Reza. "Transmission Dynamics Modelling : Gear Whine Simulation Using AVL Excite." Thesis, KTH, Fordonsdesign, 2018. http://urn.kb.se/resolve?urn=urn:nbn:se:kth:diva-234817.

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Nowadays, increasing pressure from legislation and customer demands in the automotive industryare forcing manufacturers to produce greener vehicles with lower emissions and fuel consumption.As a result, electrified and hybrid vehicles are a growing popular alternative to traditional internalcombustion engines (ICE). The noise from an electric vehicle comes mainly from contact betweentyres and road, wind resistance and driveline. The noise emitted from the driveline is for the mostpart related to the gearbox. When developing a driveline, it is a factor of importance to estimatethe noise radiating from the gearbox to achieve an acceptable design.Gears are used extensively in the driveline of electric vehicles. As the gears are in mesh, a mainintrusive concern is known as gear whine noise. Gear whine noise is an undesired vibroacousticphenomenon and is likely to originate through the gear contacts and be transferred through themechanical components to the housing where the vibrations are converted into airborne andstructure-borne noise. The gear whine noise originates primarily from the excitation coming fromtransmission error (TE). Transmission error is defined as the difference between the ideal smoothtransfer of motion of a gear and what is in practice due to lack of smoothness.The main objective of this study is to simulate the vibrations generated by the gear whine noise inan electric powertrain line developed by AVL Vicura. The electric transmission used in this studyprovides only a fixed overall gear ratio, i.e. 9.59, under all operation conditions. It is assumed thatthe system is excited only by the transmission error and the mesh stiffness of the gear contacts. Inorder to perform NVH analysis under different operating conditions, a multibody dynamics modelaccording to the AVL Excite program has been developed. The dynamic simulations are thencompared with previous experimental measurements provided by AVL Vicura.Two validation criteria have been used to analyse the dynamic behaviour of the AVL Excite model:signal processing using the FFT method and comparison with the experimental measurements.The results from the AVL Excite model show that the FFT criterion is quite successful and allexcitation frequencies are properly observed in FFT plots. Nevertheless, when it comes to thesecond criterion, as long as not all dynamic parameters of the system such as damping or stiffnesscoefficients are provided with certainty in the model, it is too difficult to investigate the accuracy ofthe AVL Excite model.Another investigation is a numerical design study to analyses how the damping coefficientsinfluence the response. After reducing the damping parameters, the results show that the housingand bearings have the highest influence on the response. If more acceptable results are desired,future studies must be concentrated on these to obtain more acceptable damping values.
För närvarande tvingar ökat tryck från lagstiftning och kundkrav inom bilindustrin tillverkarna attproducera grönare fordon med lägre utsläpp och bränsleförbrukning. Som ett resultat ärelektrifierade och hybridfordon ett växande populärt alternativ till traditionellaförbränningsmotorer (ICE). Bullret från ett elfordon kommer främst från kontakten mellan däckoch väg, vindmotstånd och drivlinan. Bullret från drivlinan är i huvudsak relaterat till växellådan.Vid utveckling av en drivlina är det av betydelse att uppskatta bullret från växellådan för att uppnåen acceptabel design.Utväxlingar används i stor utsträckning i elfordons drivlina. Eftersom kugghjulen är i kontaktuppstår ett huvudproblem som är känt som ett vinande ljud från kugghjulskontakten.Kugghjulsljud är ett oönskat vibro-akustiskt fenomen och uppstår sannolikt på grund avkugghjulkontakterna och överförs via de mekaniska komponenterna till växellådshuset därvibrationerna omvandlas till luftburet och strukturburet ljud. Kugghjulsljudet härstammarhuvudsakligen från exciteringen som kommer från transmissionsfel (TE) i kugghjulskontakten.Överföringsfelet definieras som skillnaden mellan den ideala smidiga rörelseöverföringen hoskugghjulen och rörelsen som sker i verkligheten på grund av ojämnheter.Huvudsyftet med denna studie är att simulera vibrationerna som genereras avkugghjulskontakterna i en elektrisk drivlina utvecklad av AVL Vicura. Den elektriska drivlinan somanvänds i denna studie har endast ett fast utväxlingsförhållande, dvs 9,59, för alladriftsförhållanden. Det antas att systemet är exciterat endast av överföringsfelet och kugghjulensstyvhet i kuggkontakterna. För att kunna utföra NVH-analys under olika driftsförhållanden har enstelkroppsdynamikmodell utvecklats med hjälp av programmet AVL Excite. De dynamiskasimuleringarna jämförs sedan med tidigare experimentella mätningar som tillhandahålls av AVLVicura.Två valideringskriterier har använts för att analysera det dynamiska beteendet hos AVL Excitemodellen:signalbehandling med FFT-metoden och jämförelse med experimentella mätningar.Resultaten från AVL Excite-modellen visar att FFT-kriteriet är ganska framgångsrikt och allaexcitationsfrekvenser observeras korrekt i FFT-diagrammen. Men när det gäller det andra kriteriet,så länge som inte alla dynamiska parametrar i systemet, såsom dämpnings- ellerstyvhetskoefficienter, är tillförlitliga i modellen, är det för svårt att undersöka exaktheten hos AVLExcite-modellen.En annan undersökning som utförts är en numerisk designstudie för att analysera hurdämpningskoefficienterna påverkar responsen. Efter minskning av dämpningsparametrarna visarresultaten att växellådshus och lager har störst inflytande på resultatet. Om mer acceptabla resultatär önskvärda måste framtida studier koncentreras på dessa parametrar för att uppnå mer acceptabladämpningsvärden.
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4

Jayasankaran, Kathik. "STRUCTURE-BORNE NOISE MODEL OF A SPUR GEAR PAIR WITH SURFACE UNDULATION AND SLIDING FRICTION AS EXCITATIONS." The Ohio State University, 2010. http://rave.ohiolink.edu/etdc/view?acc_num=osu1269451200.

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5

Gazda, Silvester. "Výpočtové modelování tuhosti záběru ozubených kol." Master's thesis, Vysoké učení technické v Brně. Fakulta strojního inženýrství, 2017. http://www.nusl.cz/ntk/nusl-318524.

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This master's thesis deals with the design of FEM model of gear pair with an intention to find out how stiffness changes during meshing. It firstly describes the necessary knowledge needed to analyse the problem, like the geometry of an involute tooth and evaluation of meshing stiffness. Followed by a description of work procedures from the creation of models through settings of mesh, contacts and analysis to evaluating of results.
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Planka, Michal. "Využití neuronových sítí pro výpočet průběhu záběrové tuhosti soukolí s čelními ozubenými koly." Master's thesis, Vysoké učení technické v Brně. Fakulta strojního inženýrství, 2017. http://www.nusl.cz/ntk/nusl-318391.

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The aim of this master's thesis is to build artificial neural network that is able to calculate varying single tooth-pair mesh stiffness of spur gear for given input parameters. The training set for this network was determined by computational modelling by finite element method. Therefore, creating of computational model and mesh stiffness calculating were a partial aim of this thesis. Input parameters for stiffness calculation were number of driving and driven gear teeth and gear loading. Creating of computational model and performing series of simulations was followed by creating artificial neural network. Multilayer neural network with backpropagation training was chosen as a type of the network. Created neural network is sufficiently efficient and can determine varying mesh stiffness in input set range for learned input parameters and for values of parameters that are not included in training set as well. This neural network can be used for varying single tooth-pair mesh stiffness estimation in input set range.
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7

Oudich, Hamza. "Analytical Investigation of Planetary Gears Instabilities and the Impact of Micro-Macro Geometry Modifications." Thesis, KTH, Farkostteknik och Solidmekanik, 2020. http://urn.kb.se/resolve?urn=urn:nbn:se:kth:diva-276775.

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Due to their large torque-speed ratio and transmission efficiency, planetary gears are widely used in the automotive industry. However, high amplitude vibrations remain their critical weakness, which limits their usage especially when new strict noise legislations come into action. A new approach to handle the instability problems of planetary gears encountered in real industrial context is presented in this work. First, the dynamic response of a planetary gear failing to pass the noise regulations is theoretically investigated through an analytical model. The equations of motion were solved using the Spectral Iterative Method. The observed experimental results correlated well with those from the developed model. In order to limit the resonance phenomena, impacts of different macro and micro-geometry modifications were analytically investigated: quadratic teeth profile, different planets positioning, different number of teeth and number of planets. Optimum modifications were retrieved and are expected to be tested experimentally on a test bench and on the truck. Finally, the analytical model’s limits and sensitivity to different parameters were investigated in order to certify its reliability, and suggestions for improvements were presented.
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8

Lin, Jhao-wei, and 林兆偉. "Analysis of the Mesh Stiffness and Vibration of a Spur Gear Pair." Thesis, 2012. http://ndltd.ncl.edu.tw/handle/13964418738100480146.

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碩士
國立中央大學
機械工程研究所
100
The purpose of this research is to investigate the dynamic characteristics of a spur gear pair and to study the effects of tooth crack on the dynamic response. The gear dynamic model is developed by a lumped parameter method for the vibration response. The mesh stiffness between two gears is calculated by using a finite element software – ANSYS. Then, the equations of motion are solved by using Runge-Kutta method. The features of dynamic signals for the crack in a tooth are found.
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9

Wu, Sheng Lin, and 吳昇霖. "The Effects of Bearing Stiffness on Nonlinear Dynamic Behaviors of Multi-Mesh Gear Train." Thesis, 2011. http://ndltd.ncl.edu.tw/handle/33067020701510520015.

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碩士
國立中正大學
機械工程學系暨研究所
99
This study discusses bearing stiffness effect on the multi-tooth system.First,the gear profile with modification coefficient by using rack cutter is proposed and the mesh stiffness at the position along the line of action is calculated.Final,the time-varying mesh stiffness into the system of equations of motion and use the Runge-Kutta method in the system, discuss different bearing stiffness on nonlinear dynamic behavior of gear system. The results show, from low speed to high speed of the system , if the bearing stiffness is 10^10 and 10^12N/mm , that bearing stiffness reduction will make chaos ahead of the system. In the case of high speed, positive modification coefficient chaos to occur is faster than negative modification coefficient when bearing stiffness lower, Moreover，bearing stiffness Increase the scope of the system of Chaos whan bearing stiffness lower. In terms of radial displacement, due to the strong stiffness of bearing, radial displacement effect on dynamic transmission error will low. On the other hand,Bearing damping did not affect of chaos of system.
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Yang, I.-Lin, and 楊宜霖. "Nonlinear Dynamic Analysis of Geared System with Time-Dependent Gear Mesh Stiffness Using Rack Cutter." Thesis, 2008. http://ndltd.ncl.edu.tw/handle/13419728619668052053.

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碩士
國立中正大學
機械工程所
96
The analysis of the mesh stiffness in the nonlinear dynamic gear train was simulated by applying mathematical technique such as Fourier series, rectangular wave function. However, the error always exists between practical experience and mathematical technique. This study is focused on the involute tooth profile of generation of the rack cutter and evaluated the mesh stiffness by using tooth profile. Furthermore, the effect of the mesh stiffness affected the non-linear dynamic behavior of the gear train. The generated parameters of the rack cutter included line and fillet parts, pressure angle, and tooth depth (which included root tooth, addendum, and clearance). These can affect the tooth profile and evaluation of the mesh stiffness. In this study, the parameters design how to affect the tooth profile, mesh stiffness, and non-linear dynamic behavior. According to the results, the dynamic behavior of gear train was affected by the contact ratio and mesh stiffness. The system response was small for the gear train of high contact ratio as stable action at high speed. The response can be increased for high mesh stiffness. This theoretical model of system can be quickly solved response to pre-analysis a situation of the motion and selected the gear train in the mechanical transmission.
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Book chapters on the topic "Meshing; Gear mesh stiffness"

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de Carvalho, Áquila Chagas, Fabio Mazzariol Santiciolli, Samuel Filgueira da Silva, Jony J. Eckert, Ludmila C. A. Silva, and Franco G. Dedini. "Gear Mesh Stiffness and Damping Co-simulation." In Multibody Mechatronic Systems, 177–84. Cham: Springer International Publishing, 2020. http://dx.doi.org/10.1007/978-3-030-60372-4_20.

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Meagher, Jim, Xi Wu, Dewen Kong, and Chun Hung Lee. "A Comparison of Gear Mesh Stiffness Modeling Strategies." In Structural Dynamics, Volume 3, 255–63. New York, NY: Springer New York, 2011. http://dx.doi.org/10.1007/978-1-4419-9834-7_23.

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Chakroun, Ala Eddin, Chaima Hammami, Ahmed Hammami, Ana De-Juan, Fakher Chaari, Alfonso Fernandez, Fernando Viadero, and Mohamed Haddar. "Quasi-static Study of Gear Mesh Stiffness of a Polymer-Metallic Spur Gear System." In Lecture Notes in Mechanical Engineering, 301–7. Cham: Springer International Publishing, 2021. http://dx.doi.org/10.1007/978-3-030-84958-0_32.

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Chen, Yong, Libin Zang, Kai Li, Huidong Zhou, Wangyang Bi, and Jinkai Li. "Effects of Supporting Stiffness on Meshing Characteristics of Helical Gear Under Multiple Load Cases." In Lecture Notes in Electrical Engineering, 1013–26. Singapore: Springer Singapore, 2020. http://dx.doi.org/10.1007/978-981-15-7945-5_75.

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Onkareshwar, M., Vamsi Inturi, S. P. Rajendra, P. K. Penumakala, and G. R. Sabareesh. "Effect of Local Gear Tooth Failures on Gear Mesh Stiffness and Vibration Response of a Single-Stage Spur Gear Pair." In Lecture Notes in Mechanical Engineering, 1095–103. Singapore: Springer Singapore, 2020. http://dx.doi.org/10.1007/978-981-15-8049-9_69.

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Chen, Zhiying, and Pengfei Ji. "Time Varying Mesh Stiffness Calculation of Spur Gear Pair Under Mixed Elastohydrodynamic Lubrication Condition." In Lecture Notes in Electrical Engineering, 2898–911. Singapore: Springer Singapore, 2019. http://dx.doi.org/10.1007/978-981-13-3305-7_237.

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Peng, Quancheng, Tengjiao Lin, Zeyin He, Jing Wei, and Hesheng Lv. "Calculation of Mesh Stiffness of Gear Pair with Profile Deviation Based on Realistic Tooth Flank Equation." In Communications in Computer and Information Science, 506–17. Singapore: Springer Singapore, 2018. http://dx.doi.org/10.1007/978-981-13-2396-6_47.

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Liang, Xihui, Ming J. Zuo, and Yangming Guo. "Evaluating the Time-Varying Mesh Stiffness of a Planetary Gear Set Using the Potential Energy Method." In Lecture Notes in Mechanical Engineering, 365–74. Cham: Springer International Publishing, 2014. http://dx.doi.org/10.1007/978-3-319-06966-1_33.

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Langhart, J., I. Zotos, and G. Franzoso. "Casing stiffness variations and influence on the gear meshing properties." In International Conference on Gears 2017, 1161–68. VDI Verlag, 2017. http://dx.doi.org/10.51202/9783181022948-1161.

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Cooley, Christopher G., Chunguang Liu, Xiang Dai, and Robert G. Parker. "Techniques for the calculation of gear pair mesh stiffness." In Power Engineering, 161–66. CRC Press, 2016. http://dx.doi.org/10.1201/9781315386829-25.

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Conference papers on the topic "Meshing; Gear mesh stiffness"

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Karpat, Fatih, Tufan Gürkan Yılmaz, Oğuz Doğan, and Onur Can Kalay. "Stress and Mesh Stiffness Evaluation of Bimaterial Spur Gears." In ASME 2019 International Mechanical Engineering Congress and Exposition. American Society of Mechanical Engineers, 2019. http://dx.doi.org/10.1115/imece2019-11554.

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Abstract Lightweight spur gears have been a trending topic in aerospace and automotive applications recently. Traditionally, weight reduction could be ensured by using gear body with holes or thin rim design which result in to fluctuate mesh stiffness or it may increase stress and deformation levels. Indeed, high stresses occur in only contact and root region of gear tooth during the meshing process, so other regions are subjected to low stress. Based upon this point; various materials with low density and adequate strength could be used in low stress region while gear steel remains for high stress region. In this study, two different lightweight materials (Aluminum alloy and Carbon fiber reinforced polymer) were used for low stress region. The effect of these materials was investigated in view of stiffness and root stress for the same gear design parameters. Unidirectional CFRP laminas were used in a symmetric lay up to ensure quasi-isotropic laminate properties. Finite element analyses were conducted to obtain root stress and then total deformation of the tooth for stiffness calculation. Interface properties of ring and core regions were assumed as pure bonded. Meshing load was applied on the highest point single tooth contact (HPSTC) line. Weight reduction ratios were also compared. According to results, the steel/composite design is superior to steel/aluminum hybrid design in view of stress, stiffness and weight.
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Lin, Jian, and Robert G. Parker. "Mesh Stiffness Variation Instabilities in Two-Stage Gear Systems." In ASME 2001 International Design Engineering Technical Conferences and Computers and Information in Engineering Conference. American Society of Mechanical Engineers, 2001. http://dx.doi.org/10.1115/detc2001/vib-21439.

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Abstract Mesh stiffness variation, the change in stiffness of meshing teeth as the number of teeth in contact changes, causes parametric instabilities and severe vibration in gear systems. The operating conditions leading to parametric instability are investigated for two-stage gear chains, including idler gear and countershaft configurations. Interactions between the stiffness variations at the two meshes are examined. Primary, secondary, and combination instabilities are studied. The effects of mesh stiffness parameters, including stiffness variation amplitudes, mesh frequencies, contact ratios, and mesh phasing, on these instabilities are analytically identified. For mesh stiffness variation with rectangular waveforms, simple design formulae are derived to control the instability regions by adjusting the contact ratios and mesh phasing. The analytical results are compared to numerical solutions.
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Wei, Jing, Shaoshuai Hou, Aiqiang Zhang, and Chunpeng Zhang. "An Improved Model for Calculating the Mesh Stiffness of Helical Gears." In ASME 2019 International Design Engineering Technical Conferences and Computers and Information in Engineering Conference. American Society of Mechanical Engineers, 2019. http://dx.doi.org/10.1115/detc2019-97191.

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Abstract Time-varying mesh stiffness (TVMS) is one of the important internal excitations of gear transmission systems. Accurate solution of meshing stiffness is the key to research the vibration response of gear transmission system. In the traditional analytical method (TAM), the TVMS of single-teeth engaged region consist of bending, shearing, axial compression deformation stiffness, fillet-foundation stiffness, and Hertzian contact stiffness, the TVMS of double-tooth engaged region is the sum of the single-tooth engaged region, which will lead to repeated calculation of the fillet-foundation stiffness. In order to overcome this shortcoming, considering the coupling effect between two pairs of meshing tooth, an improved method of fillet-foundation is adopted to calculate to TVMS of each slice gear. According to the ‘slicing method’, the helical gear is divided into slice gear. Considering the coupling effect of each slice gear, the TVMS of helical gear can be obtained. The improved analytical method (IAM) is verified by comparing with finite element method (FEM) and TAM. Based on the IAM, the effects of the helical angle, face width, the number of gear, and modification coefficient on the mesh characteristics are analyzed. The results show that the IAM is consistent with the FEM and also consistent with TAM in single-tooth engagement. However, there is obviously error with the TAM in double-tooth or multi-tooth engagement.
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Zhang, Jianwu, Han Guo, Liang Zou, and Haisheng Yu. "Optimization of Compound Planetary Gear Train by Improved Mesh Stiffness Approach." In ASME 2017 International Mechanical Engineering Congress and Exposition. American Society of Mechanical Engineers, 2017. http://dx.doi.org/10.1115/imece2017-70403.

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An improved mesh stiffness approach is presented for optimization of vibration and noise performance of the planetary gear trains in a full power split hybrid transmission, in which mesh stiffness time-variability and biaxial gear stiffness couplings in gear pairs are taken into account. For improving accuracy of the mesh stiffness in double teeth-meshing region for spur gear pairs, a simplified solution to the loading gear deformations counting for time-varying mesh stiffness of the helical gear pairs is proposed, based on the integral potential energy method and FEM simulation. By the new biaxial coupling model, effects of gear body and tooth coupled stiffnesses on gear pair vibro-acoustic responses are also investigated and approved to be considerable. Numerical examples with optimal analyses of the specified planetary gear trains for the full hybrid transmission are provided. Numerical solutions of eigen frequencies and vibration modes for the gear pairs with a variety of time-varying mesh stiffnesses are constructed by the biaxial coupling model and Fourier Series. The dynamic parameters optimization of the compound planetary gear train is then conducted. The optimized planetary gear system is applied in the full hybrid transmission and bench tests for its vibro-acoustic performance are also undertaken. Computational predictions and experimental results are shown to be in fairly good agreement.
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Sirichai, Seney, Ian Howard, Laurie Morgan, and Kian Teh. "The Static Transmission Error of Cracked Spur Gear Teeth Using FEA." In ASME 1998 Design Engineering Technical Conferences. American Society of Mechanical Engineers, 1998. http://dx.doi.org/10.1115/detc98/cie-5510.

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Abstract This paper considers a Finite Element Model which is used to predict the torsional mesh stiffness and static transmission error of a pair of spur gears in mesh. The model involves the use of 2D plain strain elements, coupled with contact elements at the points of contact between the meshing teeth. A simple strategy of how to determine an appropriate value of the penalty parameter of the contact elements (gap element) is also presented. When gears are unloaded, a pinion and gear with perfect involute profiles, should theoretically run with zero transmission error. However, when gears with involute profiles are loaded, the individual torsional mesh stiffness of each gear changes throughout the mesh cycle, causing variations in angular rotation of the gear body and subsequent transmission error. The theoretical changes in the torsional mesh stiffness throughout the mesh cycle are developed using finite element analysis and related to the static transmission error. A 5mm through thickness tooth crack is also modelled, and the comparison of the torsional mesh stiffness and static transmission error with and without the tooth crack is discussed.
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Kuang, Jao-Hwa, and Ah-Der Lin. "An Analytical Model for Spur Gear Dynamics." In ASME 1997 Design Engineering Technical Conferences. American Society of Mechanical Engineers, 1997. http://dx.doi.org/10.1115/detc97/dac-3855.

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Abstract A mathematical model for a spur gear pair with two-step mesh stiffness is proposed. Two constant values of mesh stiffness are used to approximate the complicated compliance alternation of contact tooth pairs between one and two during meshing. Analytical solutions of the dynamic loads are derived. The method has been employed to calculate the dynamic contact load, transmitted torque and the bearing forces. The results compared favorably with a more detailed model found in the literature.
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Shao, Yimin, Xi Wang, Zaigang Chen, and Teik C. Lim. "Effect of Gear Tooth Crack on Spur Gear Dynamic Response by Simulation." In ASME 2011 International Design Engineering Technical Conferences and Computers and Information in Engineering Conference. ASMEDC, 2011. http://dx.doi.org/10.1115/detc2011-47524.

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Geared transmission systems are widely applied to transmit power, torque and high rotational speed, and as well as change the direction of rotational motion. Their performances and efficiencies depend greatly on the integrity of the gear structure. Hence, health monitoring and fault detection in geared systems have gained much attention. Often, as a result of inappropriate operating conditions, application of heavy load beyond the designed capacity or end of fatigue life, gear faults frequently occur in practice. When fault happens, gear meshing characteristics, including mesh stiffness that is one of the important dynamic parameters, can be affected. This sudden change in mesh stiffness can induce shock vibration as the faulty gear tooth passes through the engagement zone. In this study, a finite element model representing the crack at the tooth root of a spur gear is developed. The theory is applied to investigate the effect of different crack sizes and the corresponding change in mesh stiffness. In addition, a lumped parameter model is formulated to examine the effect of tooth fault on gear dynamic response.
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Parker, R. G., S. M. Vijayakar, and T. Imajou. "Modeling the Nonlinear Vibration of a Spur Gear Pair." In ASME 2000 International Design Engineering Technical Conferences and Computers and Information in Engineering Conference. American Society of Mechanical Engineers, 2000. http://dx.doi.org/10.1115/detc2000/ptg-14434.

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Abstract The dynamic response of a spur gear pair is investigated using a finite element/contact mechanics model that offers significant advantages for dynamic gear analyses. The gear pair is analyzed across a wide range of operating speeds and torques. Comparisons are made to other researchers’ published experiments that reveal complex nonlinear phenomena. The nonlinearity source is contact loss of the meshing teeth, which, in contrast to the prevailing understanding, occurs even for large torques despite use of high-precision gears. A primary feature of the modeling is that dynamic mesh forces are calculated using detailed contact analysis at each time step as the gears roll through mesh; there is no need to externally specify the excitation in the form of time-varying mesh stiffness, static transmission error input, or the like. A semi-analytical model near the tooth surface is matched to a finite element solution away from the tooth surface, and the computational efficiency that results permits dynamic analysis. Two single degree of freedom models are discussed briefly. While one gives encouragingly good results, the second, which appears to have better mesh stiffness modeling, gives poor comparisons with experiments. The results indicate the sensitivity of such models to changing mesh stiffness representations.
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Ramamohana Rao, A., and B. Srinivasulu. "Studies on the Dynamic Performance of a Spur Gear With Hollow Teeth." In ASME 1992 Design Technical Conferences. American Society of Mechanical Engineers, 1992. http://dx.doi.org/10.1115/detc1992-0005.

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Abstract Performance of spur gears largely depends on the magnitude and nature of variation of dynamic loads occuring between mating teeth. Variable tooth mesh stiffness is one of the primary sources causing parametric excitations resulting in dynamic loads. The usual method of varying the mesh stiffness to reduce dynamic loads is to use high contact ratio and profile modified gears. In this paper, a new type of tooth design to improve the dynamic performance of spur gears is presented. In this, a through hole is drilled in each tooth in a direction parallel to the gear axis. The diameter of the hole and its position on the tooth centre line are variable. Such a gear is called a hollow gear. Dynamic analysis is carried out for the mesh of hollow pinions mating with solid gears. The results are compared with solid pinions (no holes in teeth) meshing with solid gears. Finite element method is used for the analysis. For estimation of the dynamic load variation in hollow-solid and solid-solid gear meshes, a model incorporating the varying mesh stiffness and damping of gear teeth is used. Governing differential equations are solved using unconditionally stable Newmark-beta algorithm. The dynamic loads obtained are used as an input time varying loads for the determination of dynamic fillet and hole stress response of solid and hollow gear teeth whichever is applicable. Modal superposition technique is used for transient response analysis. The study shows that for the same damping ratio, dynamic loads in hollow-solid meshes are nearly the same as in a solid-solid mesh. In reality, the dynamic loads in a hollow-solid mesh are less than a solid-solid mesh due to its inherent higher material damping.
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Kuang, J. H., and A. D. Lin. "On the Interaction Between the Dynamic Contact Load and the Surface Wear of a Plastic Gear Pair." In ASME 2000 International Design Engineering Technical Conferences and Computers and Information in Engineering Conference. American Society of Mechanical Engineers, 2000. http://dx.doi.org/10.1115/detc2000/dac-14529.

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Abstract Due to the merits, for example, silent operation, self-lubrication, and light weight, etc., the demand for plastic gears increases tremendously. The purpose of this paper is to investigate the interaction between the dynamic contact loads and the sliding wear depths of a meshing plastic gear pair. Parameters, such as time-varying mesh stiffness, damping ratio, tooth errors, etc., are included in the gear dynamic model presented. As to the mesh stiffness, finite element results will be used to curve fit the flexible stiffnesses at different contact points. The values of the damping ratio and the friction coefficient are referenced to the experimental results in the papers cited. In addition to the studies of the parameters involved in the dynamic model, the wear equation proposed by Archard is used to calculate the wear depths of the running gear pair. With the gear dynamic model and the wear model developed, a computation algorithm is designed to simulate the interaction of the sliding wears and the dynamic contact loads.
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