Many researchers have compared predicted stiffness and damping coefficients for tilting-pad journal bearings (TPJBs) to measurements. Most have found that direct damping is consistently overpredicted. The thrust of this research is to explain the difference between measured and predicted stiffness and damping coefficients for TPJBs, and to provide some confidence to designers that TPJB dynamic coefficients can be accurately predicted. Most analytical models for TPJBs are based on the assumption that explicit dependence on pad motion can be eliminated by assuming harmonic rotor motion such that the amplitude and phase of pad motions resulting from radial and transverse rotor motions are predicted by rotor-pad transfer functions. In short, these transfer functions specify the amplitude and phase of pad motion (angular, radial, translational, etc.) in response to an input rotor motion. A new pad perturbation model is developed including the effects of angular, radial, and circumferential pad motion and changes in pad clearance due to pad bending compliance. Though all of these pad variables have previously been included in different analyses, there are no publications containing perturbations of all four variables. In addition, previous researchers have only perturbed the journal, while both the bearing and journal motions are perturbed in the present analysis, and the applicability of comparing rotor-perturbed bearing impedance predictions to impedances measured on a bearing-perturbed test rig is discussed. This perturbation model was implemented in a Reynolds-based TPJB code to predict the frequency-dependent bearing impedances and rotor-pad transfer functions. Direct measurements of pad motion during test excitation were recorded to produce measured transfer functions between rotor and pad motion, and a comparison between these measurements and predictions is given. Motion probes were added to the loaded pad (having the static load vector directed through its pivot) of a 5-pad TPJB to obtain accurate measurement of pad radial and tangential motion, as well as tilt, yaw, and pitch. Strain gages were attached to the side of the loaded pad to measure static and dynamic bending strains, which were then used to determine static and dynamic changes in pad curvature (pad clearance). Good agreement was found between the amplitude of the measured and predicted transfer functions concerning radial and transverse pad motions throughout the range of speeds and loads tested, while pad tilt was moderately underpredicted. For the bearing investigated, radial pad motions resulting from pivot compliance were as large as 60% of the radial component of shaft motion when operating at 4400 rpm under heavily loaded conditions. Hence, if a dynamic load applied to the shaft resulted in a shaft displacement of 25 microns (1 mil), the pad would displace radially 15 microns (0.6 mils), and the fluid film height would only decrease by 10 microns (0.4 mils). The consequence of this pad motion is that fluid film stiffness and damping forces produced by relative rotor-pad motions are significantly reduced, resulting in a bearing having significantly less direct stiffness and damping than predicted. A similar effect occurs when shaft motions produce significant changes in pad clearance due to pad compliance. For the pad tested here, the measurements show that predicting TPJB stiffness and damping coefficients without accounting for pad and pivot compliance will produce large errors, and is not advised. Transverse pad motion was predicted and observed. Based on phase measurements, this motion is lightly damped, and appears to be caused by pivot deflection instead of slipping. Despite observing a lightly damped phase change, an increase in magnitude at this natural frequency was not observed. Predicted direct stiffness and damping for unit loads from 0-3200 kPa (0-450 psi) fit through 1.5× running speed are within 18% of measurements at 4400 rpm, while predictions at 10200 rpm are within 10% of measurements. This is a significant improvement on the accuracy of predictions cited in literature. Comparisons between predictions from the developed bearing model neglecting pad, pivot, and pad and pivot flexibility show that predicted direct stiffness and damping coefficients for a model having a rigid pad and pivot are overestimated, respectively, by 202% and 811% at low speeds and large loads, by 176% and 513% at high speeds and high loads, and by 51% and 182% at high speeds and light loads. While the reader is likely questioning the degree to which these predictions are overestimated in regard to previous comparisons, these predictions are based on measured operating bearing clearances, which are 20-30% smaller than the cold bearing clearances that previous comparisons were based on. The effect of employing a full bearing model (retaining all of the pad degrees of freedom) versus a reduced bearing model (where only journal degrees of freedom are retained) in a stability calculation for a realistic rotor-bearing system is assessed. For the bearing tested, the bearing coefficients reduced at the frequency of the unstable eigenvalue (subsynchronously reduced) predicted a destabilizing cross-coupled stiffness coefficient at the onset of instability within 1% of the full model, while synchronously reduced coefficients for the lightly loaded bearing required 25% more destabilizing cross-coupled stiffness than the full model to cause system instability. This overestimation of stability is due to an increase in predicted direct damping at the synchronous frequency over the subsynchronously reduced value. This increase in direct damping with excitation frequency was also seen in highly loaded test data at frequencies below approximately 2×running speed, after which direct damping decreased with increasing excitation frequency. This effect was more pronounced in predictions, occurring at all load and speed combinations. The same stability calculation was performed using measured stiffness and damping coefficients at synchronous and subsynchronous frequencies at 10200 rpm. It was found that both the synchronously measured stiffness and damping and predictions using the full bearing model were more conservative than the model using subsynchronously measured stiffness and damping. This outcome contrasts with the comparison between models using synchronously and subsynchronously reduced impedance predictions, which showed the subsynchronously reduced model to be the most conservative. This contrast results from a predicted increase in damping with increasing excitation frequency at all speeds and loads, while this increase in damping with increasing excitation frequency was only measured at the most heavily loaded conditions.

Submitted by Everton Coelho de Medeiros null (everton.medeiros@feg.unesp.br) on 2017-08-29T19:01:48Z No. of bitstreams: 1 Dissertação_final.pdf: 4345654 bytes, checksum: 76773f0a6cc1d17c5e1162955ff8879a (MD5) / Approved for entry into archive by Luiz Galeffi (luizgaleffi@gmail.com) on 2017-08-29T19:06:26Z (GMT) No. of bitstreams: 1 medeiros_ec_me_guara.pdf: 4345654 bytes, checksum: 76773f0a6cc1d17c5e1162955ff8879a (MD5) / Made available in DSpace on 2017-08-29T19:06:26Z (GMT). No. of bitstreams: 1 medeiros_ec_me_guara.pdf: 4345654 bytes, checksum: 76773f0a6cc1d17c5e1162955ff8879a (MD5) Previous issue date: 2017-06-30 / Os estudos relacionados a máquinas rotativas são muito importantes no apoio e manutenção da operação de máquinas de grande porte, tais como turbo compressores ou turbinas. Modelos analíticos e numéricos têm sido aplicados por anos, entretanto, eles nem sempre apresentam as condições reais dessas máquinas. Por isso, o uso de procedimentos experimentais para a avaliação e validação de resultados de máquinas rotativas é importante para a etapa de projeto mecânico. O uso de modelos em escala, por exemplo, turbinas hidráulicas ou turbinas a vapor, tem sido comum nesta área. Um rotor é dividido em várias partes, sendo uma delas os elementos de suporte, mais especificamente os mancais. Os mancais podem ser divididos em vários tipos, os mais utilizados são os do tipo rolamento e tipo hidrodinâmico. Devido este último ser o mais encontrado em máquinas pesadas, seu estudo é muito importante. Este trabalho objetiva apresentar o projeto de um protótipo de um mancal hidrodinâmico e sua avaliação experimental. O mancal desenvolvido consiste de uma bucha de bronze montada sobre uma casa de mancal de alumínio e sistemas de vedação para o óleo lubrificante. As geometrias das buchas e as propriedades dos fluidos foram analisadas pela medição do comportamento dinâmico de um rotor apoiados por esses mancais. Esta avaliação foi baseada na medição de uma bancada do tipo Jeffcott apoiada em um par de mancais hidrodinâmicos em condições diversas, incluindo combinações entre mancais do tipo rolamento e hidrodinâmico, variação da geometria interna da bucha de bronze e uso de mancal de material compósito com lubrificação de contorno. Podendo concluir que mancais com buchas de geometria fixa e cilíndrica mostram um comportamento anisotrópico, causado pela diferença de rigidez entre os planos horizontal e vertical. Ao variar para mancais de geometria assimétrica (Elíptico e Offset-halves), buchas de material compósito e modificação do tipo de lubrificação este fenômeno de anisotropia é reduzido, levando a condição de apoio para mais próxima de isotrópica. A combinação entre diferentes mancais (rolamento e hidrodinâmico) levou à observação da análise de mancais montados próximo a região do acoplamento de torque e também a importância do sentido da rotação do rotor para a formação do filme de óleo e evitar o seu sobreaquecimento. / Studies related to rotary machines are very important to support and keep the operation of large machines such as turbochargers or turbines. Analytical and numerical models have been applied for years, however, they do not always present the real condition of these machines. Therefore, the use of experimental procedures for the evaluation and validation of rotating machine results is important for mechanical design step. The use of scale models, for example, hydraulic turbines or steam turbines, has been very common in this area. A rotor is divided into several parts, one of which is the support elements, more specifically the bearings. The bearings can be divided into several types, the most common are the ball/roller bearing and the hydrodynamic bearing. Due to the latter be the most applied in heavy machinery, his study is very important. This work aims to show the design of a prototype of a hydrodynamic bearing and its experimental evaluation. The developed bearing consists of a bronze bushing mounted on an aluminum bearing housing and sealing systems for lubricating oil. The bushing geometries and the properties of the fluids are analyzed by measuring the dynamic behavior of a rotor supported by these bearings. This evaluation was based on the measurement of a Jeffcott rotor test bench supported by hydrodynamic bearings under a variety of conditions, including combinations of rolling and hydrodynamic type bearings,variation of the internal geometry of the bronze bushing and use of composite material bearing for the bush with contour lubrication. It may be concluded that bearings with fixed and cylindrical geometry bearings show an anisotropic behavior caused by the difference in rigidity between the horizontal and vertical planes. When the bush is changed for asymmetric geometries (Elliptical and Offset-halves), composite material bushings and modification of the lubrication type, the anisotropy phenomenon is reduced, leading to a supportive condition closer to isotropic. The combination of different bearings (ball/roller bearing and hydrodynamic bearing) led to the observation the analysis of mounted bearings near a torque coupling region and also the importance of the direction of rotation for oil film formation and to avoid his overheating.

Orientador: Katia Lucchesi Cavalca Dedini, Hélio Fiori de Castro / Dissertação (mestrado) - Universidade Estadual de Campinas, Faculdade de Engenharia Mecânica / Made available in DSpace on 2018-08-16T15:47:14Z (GMT). No. of bitstreams: 1 Camargo_LucasWardFrancode_M.pdf: 3927704 bytes, checksum: fae6a20117d598883d434bc95dfb93fd (MD5) Previous issue date: 2010 / Resumo: O estudo de máquinas rotativas ocupa uma posição destacada no contexto de máquinas e estruturas devido à quantidade significativa de fenômenos que podem ocorrer durante a operação desses equipamentos. Este trabalho é focado no estudo de sistemas rotativos sustentados por mancais hidrodinâmicos (com ou sem um acoplamento conectando o eixo movido ao eixo motriz) e, principalmente, na análise das falhas que podem mais comumente ocorrer nesses sistemas (desbalanceamento, empenamento e desalinhamento). A análise é estendida para o caso de múltiplas falhas, visto que essa é uma condição comum em sistemas rotativos. O alinhamento e o balanceamento perfeitos da máquina não podem ser obtidos em aplicações reais e, portanto, forças de excitação são geradas nesses sistemas, as quais afetam significantemente a operação das máquinas. Dessa forma, a influência do desbalanceamento, empenamento e desalinhamento nas amplitudes de vibração constituem uma importante consideração, especialmente o efeito dos componentes harmônicos que podem surgir em uma máquina desalinhada. Para representar matematicamente o sistema, um modelo de elementos finitos é utilizado e a análise é realizada no domínio da frequência. O acoplamento também é modelado como um elemento finito e as forças de desalinhamento, desbalanceamento e empenamento são incluídas no modelo de falhas. Com a adição de um nível de ruído aos sinais simulados, um possível sinal experimental é obtido e, com o objetivo de identificar os parâmetros de falha considerados desconhecidos, um algoritmo genético multiobjetivo é proposto. A análise individual de cada função objetivo (erro entre sinal simulado e sinal ajustado) permite que seja possível identificar um conjunto de soluções ótimas para o problema e, assim, identificar os parâmetros de falhas / Abstract: The study of rotating machinery occupies an outstanding position in the study of machinery and structures due to the significant amount of phenomena that occur in the operation of these equipments. This work is focused on the study of rotating systems supported by hydrodynamic bearings (with or without a flexible coupling connecting the driving motor and the driven shaft), mainly considering faults that can commonly occur in these systems (misalignment, bow and unbalance) as the presence of multiple faults in a real machine is a common situation. The perfect balance and alignment of the machine cannot be achieved in practical applications. Consequently excitation forces are generated at these systems, which significantly affect the operation of the machines. In this way, the influence of the unbalance, bow and misalignment on the vibration amplitude is an important consideration, specially the effect of the harmonic components that can rise when a machine is misaligned. To mathematically represent the system, a finite element model is used and the analysis is held in the frequency domain. The coupling is also modeled as a finite element and the misalignment, bow and unbalance forces are included in the fault model. Noise is added to the simulated results to build a possible experimental result and, in order to identify the fault unknown parameters, the multi-objective genetic algorithm is proposed. The individual analysis of each objective function (difference between simulated and adjusted results) allows the identification of an optimal set of solutions resulting in the identification the fault parameters / Mestrado / Mecanica dos Sólidos e Projeto Mecanico / Mestre em Engenharia Mecânica

Orientador: Kátia Lucchesi Cavalca Dedini / Dissertação (mestrado) - Universidade Estadual de Campinas, Faculdade de Engenharia Mecânica / Made available in DSpace on 2018-08-16T19:43:14Z (GMT). No. of bitstreams: 1 Tuckmantel_FelipeWenzeldaSilva_M.pdf: 5340309 bytes, checksum: a62c87427ed691bb455fd23f46cde6f0 (MD5) Previous issue date: 2010 / Resumo: O estudo de máquinas rotativas ocupa uma posição destacada no contexto de máquinas e estruturas, tendo em vista a grande aplicação das máquinas rotativas e a importância de conhecer o seu funcionamento com fins de otimização e de projeto para diminuição de custos, melhora de qualidade e aumento da vida útil dos componentes. Estas máquinas, e seus componentes, possuem características peculiares em seu funcionamento, as quais se refletem em seu comportamento dinâmico e, conseqüentemente, nos problemas mecânicos a estes associados. A análise do comportamento das máquinas rotativas envolve considerável complexidade, já que são constituídas, geralmente, por um sistema de equipamentos que abrangem, além do rotor, eixos e mancais, fundação e outros equipamentos auxiliares, como, por exemplo, selos de fluxo. Portanto, para se estudar o comportamento dinâmico desses sistemas, é necessário determinar a interação de todos os componentes para o entendimento dos fenômenos envolvidos. O sistema rotativo foi matematicamente modelado através da modelagem do eixo por elementos finitos, através de um conjunto de discos rígidos e segmentos de eixo com massa e elasticidade distribuídas, e dos mancais hidrodinâmicos, cuja representação ocorre a partir de seus coeficientes equivalentes de rigidez e amortecimento. A fundação também teve sua influência contemplada pelas representações por Parâmetros Concentrados, Impedância Mecânica e Coordenadas Mistas. Portanto, neste trabalho, desenvolveu-se a configuração do pacote computacional, a padronização da entrada e saída dos arquivos, a implementação dos elementos de viga e de disco rígido, a excitação por desbalanceamento, a determinação dos carregamentos nos mancais e a resposta dinâmica do sistema no domínio da freqüência, tendo como objetivo robustez, flexibilidade, confiabilidade, além de usabilidade e interface amigável do pacote / Abstract: The Rotordynamics occupies a prominent position in the design of machines and structures, due to the wide application of rotating machinery and the importance of the knowledgment of its operation for purposes of optimization and design for cost reduction, quality improvement and increased component life cycle. These machines and their components have peculiar characteristics in its operation, which will reflect in its dynamic behavior and, consequently, on the mechanical problems associated with these. The behavior of rotating machinery involves considerable complexity, as they are composed, usually by a system of equipment which includes, besides the rotor, shafts and bearings, foundation and other auxiliary equipment, for example, shaft seals. Therefore, to study the dynamic of these systems, it is necessary to determine the interaction of all components for understanding the phenomena involved. The rotation system was mathematically modeled by the shaft modeling through the Finite Element Method, through a set of disks and shaft segments with elasticity and mass distribution, and hydrodynamic bearings, whose representation occurs through the coefficients of equivalent stiffness and damping. The foundation also had its influence covered by the formulation of Concentrated Parameters, Mechanical Impedance and Mixed Coordinates. Therefore, in this work, it is developed the computational package configuration, standardization of input and output files, the implementation of beam elements and disks, the unbalance excitation, the determination of loads on the bearings and the frequency dynamic response of the system, aiming at robustness, flexibility, reliability, usability and user-friendly of the software / Mestrado / Mecanica dos Sólidos e Projeto Mecanico / Mestre em Engenharia Mecânica

Orientadores: Katia Lucchesi Cavalca, Eduardo Paiva Okabe / Dissertação (mestrado) - Universidade Estadual de Campinas, Faculdade de Engenharia Mecanica / Made available in DSpace on 2018-08-14T09:22:50Z (GMT). No. of bitstreams: 1 Santana_PedroMenezes_M.pdf: 1559305 bytes, checksum: 5e83f98a9c2a81717c597a0f31a71208 (MD5) Previous issue date: 2009 / Resumo: Um sistema rotativo, quando gira, pode apresentar precessão no mesmo sentido (precessão direta) ou no sentido contrário (precessão retrógrada) ao da rotação. Estes dois modos combinados podem definir o comportamento da vibração do rotor. A formulação direcional é utilizada para representar os modos de precessão, possibilitando a obtenção da resposta dos modos diretos e retrógrados, separados no domínio da freqüência. O modo retrógrado, que pode ser resultado da anisotropia do sistema, deve ser evitado, já que provoca variações constantes nas tensões de tração e compressão nas fibras do eixo, o que pode propagar trincas e causar falha por fadiga. Este trabalho tem o objetivo de analisar a influência do grau de anisotropia dos mancais e da estrutura de suporte na resposta do modo retrógrado de precessão. Diversas configurações de sistema rotor-mancais foram modelados e estudados, utilizando coordenadas direcionais, para diferentes graus de anisotropia dos mancais flexíveis. Foram utilizados modelos de eixo rígido e flexível, incluindo um modelo de elementos finitos. Diferentes modelos experimentais de fundação foram incorporados ao sistema rotor-mancais. Os principais modos da fundação foram representados por coordenadas principais, e o sistema resultante é, portanto, representado por coordenadas mistas (físicas para o rotor e principais para a fundação). / Abstract: A rotating system, as it spins, can perform a whirling at the same direction (forward whirl) or at the opposite direction (backward whirl). These two whirling modes can define the rotor's vibration behavior. The directional formulation is used in modal analysis to represent the whirling modes, so it can be possible to obtain the forward and backward response separately on the frequency domain. The backward mode, that may occur as a result of the system's anisotropy, must be avoided, since it generates constant variations of the traction and compression tensions at the shaft, which can provoke fatigue failure. The objective of this work is to analyze the influence of the anisotropy degree of the bearings and supporting structure on the backward mode of whirl. Different rotor-bearings configuration where modeled and studied, using directional coordinates, for different bearings' coefficients. Rigid and flexible shaft models where used, including a finite elements model. For a better understanding of the system's response, different experimental supporting structure (foundation) models where incorporated to the rotor-bearings system, and the directional response of the rotor-bearings-foundation system was calculated. The main foundation modes were represented by modal coordinates, and the resulting system is, thus, represented by mixed coordinates (physical coordinates for the rotor and modal coordinates for the foundation). / Mestrado / Mecanica dos Sólidos e Projeto Mecanico / Mestre em Engenharia Mecânica

La prise en compte des couplages dynamiques entre les différents organes constituant une turbomachine s’inscrit dans le processus d’optimisation des designs moteur. L’amélioration des performances des turboréacteurs passe souvent par l’utilisation d’architectures multi-rotors. Dans le contexte des moteurs avec une architecture bi-rotor, des résultats d’essais expérimentaux montrent qu’il est nécessaire de considérer, dès la conception, l’influence de la dynamique de l’arbre Haute Pression (HP) sur les aubages de l’arbre Basse Pression (BP). Dans ce cadre d’étude, un premier modèle simplifié de bi-rotor aubagé est développé dans le repère tournant lié au rotor BP. Ce modèle est composé de deux rotors modélisés par des équivalents poutres - masses - ressorts et d’une roue aubagée constituée d’aubes souples modélisées par des poutres encastrées sur un disque rigide. Desnon-linéarités de type jeu radial avec contact au niveau des paliers sont également considérées et la réponse des aubes soumises à des excitations multi-fréquentielles de type balourd BP et HP est analysée. La présence de non-linéarités dans le système conduit à mettre en oeuvre des algorithmes adaptés, basés sur des techniques de résolution dans le domaine fréquentiel avec l’évaluation des efforts non-linéaires dans le domaine temporel. Afin d’avoir une meilleure description de la dynamique de la roue aubagée, une méthode spécifique de couplage est proposée, permettant de coupler un modèle réduit de roue aubagée 3D à un modèle simplifié de bi-rotor. Une démarche adaptée à la modélisation de la roue aubagée en symétrie cyclique est implémentée afin de considérer des non-linéarités de type contact en tête d’aube. La méthode de couplage proposée est ensuite illustrée sur un exemple simple puis validée dans un cadre linéaire et non-linéaire. Enfin, cette méthode de couplage est appliquée au cas d’une structure industrielle, constituée d’un modèle d’ensemble simplifié représentatif d’un moteur et d’un modèle éléments finis d’une roue de turbine BP. Les résultats obtenus mettent en évidence le couplage entre la dynamique d’ensemble et la dynamique de la roue aubagée et permettent de prédire la réponse non-linéaire des aubes de turbine BP en présence d’une excitation multi-fréquentielle, dans des configurations de co-rotation et de contra-rotation. / The design and optimization process of high efficiency turbomachinery has become a major challenge and a topical issue at both industrial and research levels. Performance improvement has motivated the use of multi-shaft architecture in engines. In the context of dual-shaft aircraft engines, the interaction between dynamics occurring within shafts and bladed disks seems to play an important role at the design stage. The present research work deals with the coupling of these components involving several unbalances in the dynamic response of blades. Within this framework, a simplified analytical model of a bladed dual-shaft developed in the rotating frame is presented. The dual-shaft is modelled by spring - mass- beam systems and connected to a bladed disk composed of a set of flexible blades modelled by Euler-Bernoulli beams clamped in a rigid disk. Nonlinearities coming from bearings are also considered and modelled as a radial clearance and contact stiffness. Considering nonlinearities requires the implementation of dedicated algorithms and specific resolution techniques in the frequency domain as well as the computation of nonlinear forces in the time domain. The nonlinear response of blades subjected to unbalances excitations is investigated and analysed. To have a finer description of the bladed disk dynamics, a specific coupling method is proposed allowing to connect a bladed disk finite element model with the simplified dual-shaft model. A cyclic symmetry approach well-suited to the nonlinear dynamics of bladed disks is developed in order to consider blade tip contact nonlinearities. Performances of the proposed method are illustrated through an academic example and validated in both linear and nonlinear settings. Eventually, the coupling technique is applied to a complex industrial case involving a classical simplified dual-shaft model and a finite element model of the low pressure turbine bladed disk. Numerical results clearly demonstrate the coupling between dynamics and enable to predict the nonlinear response of low pressure turbine blades to several unbalances, for both co-rotating and counter-rotating engines.

L’objectif de ces travaux est de prédire la stabilité dynamique d’un moteur d’avion de type turbofan, lors de contacts légers entre l’extrémité des aubes et le carter en regard. Une voix d’amélioration des performances des turboréacteurs d’avion consiste, en effet, à réduire les jeux entre les extrémités des aubes en rotation et le carter. Réduction qui s’accompagne d’une augmentation des possibilités de contact entre ces parties tournantes et fixes pouvant conduire à des phénomènes vibratoires instables. La démarche proposée s’appuie sur un modèle hybride qui introduit de manière simplifiée une roue aubagée et un carter flexible à un modèle de ligne d’arbres. Une formulation dite 3D du contact a également été implémentée, elle intègre la cinématique des différents organes du modèle et introduit de manière précise la géométrie locale de la zone de contact. Le comportement du modèle lors de contacts aubes-carter est alors étudié en distinguant les analyses menées en supposant un contact permanent et celles autorisant l’intermittence des contacts. Les résultats obtenus mettent en évidence l’importance des couplages introduits dans l’apparition des phénomènes instables et la pertinence de la formulation 3D dans la prédiction de la stabilité du système. / This work aims to predict the dynamic stability of a turbofan engine submitted to light contacts between blade tips and casing. Reducing the clearance between the rotating blades and the casing improves indeed the performances of turbomachines ; however, it also increases the possible contacts between rotating and stationary parts, which can cause unstable dynamic behavior. The approach is based on a hybrid model which introduces a simplified bladed wheel and a flexible casing to a rotor-shaft model. A 3D contact formulation has also been implemented ; it considers the model kinematic and introduces the local geometry of the contact area. The model behavior with blade-to-casing contacts is analyzed through two approaches : the first one assumes permanent contacts while the other one allows contact intermittence. The results highlight the importance of couplings in the outbreak of unstable phenomena and the relevance of the 3D contact formulation in predicting the stability of the system.

Using MATLAB and a National Instruments data acquisition card, a signal processing program meant to monitor the behavior of rotordynamic systems in real-time was developed and tested. By using traditional analysis methods in this field of engineering, commonly desired data representations such as bode, polar, orbit, full spectrum plots were able to be produced to a very high accuracy. Additional capabilities offered by this application are slow roll compensation, synchronous and sub-synchronous filtering, and true three dimensional plotting. The verification of this program was done by comparing the results to the ones acquired with Bently Nevada’s “Automated Diagnostics for Rotating Equipment” (ADRE) system. In addition to a data acquisition program, theoretical models of the two-disk rotor were created to estimate the unknown physical parameters of the system. By simulating the rotor with and without gyroscopic effects included, estimates for the stiffness, damping, eccentricity, initial phase, and initial skew values present in the system were determined.

No description available.

No description available.