The first part of our study introduces a new method for rapidly generating an "improved" Stribeck curve (i.e. Stribeck+ curve) that, compared to traditional Stribeck curves, shows a more complete tribological picture of the chemical mechanical planarization (CMP) process. The method significantly reduces the consumables and time required to obtain the curve compared to traditional means. Results of the Stribeck+ curve are consistent with individual tests using several different consumables combinations. All copper CMP Stribeck+ examples clearly indicate the lubrication mechanism and transitions thereof between different polishing conditions. Variability in COF as well as a much wider range in U/P are also explored. In the second part of our study, the Stribeck+ curve is successfully applied to silicon dioxide CMP processes to characterize the tribology of such processes under different process conditions and consumables. Results show our Stribeck+ curve methodology to be capable of rapidly determining and differentiating the tribological mechanism among all cases studied. The Stribeck+ curve helps indicate process stability as shown by the spread of the COF vertical clusters. The Stribeck+ curve also confirms a previously known effect that the greater the ratio of pad’s up-features to the total pad area, the greater the probability of wafer hydroplaning. As the third part of our study, we investigate the effect of different pad surface micro-textures on the tribological, thermal and kinetic attributes during copper CMP. Different micro-textures are generated by two different chemical vapor deposited (CVD) diamond-coated conditioner discs (i.e. Disc A and Disc B). Results show that while pad temperature and removal rate increase with polishing pressure and sliding velocity on both discs, Disc B generates consistently lower removal rates and COF than Disc A. To fundamentally elucidate the cause(s) of such differences, pad surface contact area and topography are analyzed using laser confocal microscopy. The comparison of the pad surface micro-texture analysis indicates that Disc A causes a pad surface with a smaller abruptness (λ) and much more solid contact area which results in a higher removal rate. In contrast, Disc B generates less contact areas and COF. A two-step modified Langmuir–Hinshelwood model is employed to simulate copper removal rates as well as chemical and mechanical rate constants. The simulated chemical to mechanical constant ratios indicate that Disc A produces a more mechanically limited process under all conditions tested. In the fourth part of our study, the position of a slurry injection system (SIS) is optimized to achieve a more cost-effective and environmentally benign CMP process using a widely-adopted ceria-based "reverse slurry". Here, SIS is configured with different angles in order to investigate slurry dilution characteristics caused by residual pad rinsing with ultrapure water (UPW) that is known to affect silicon dioxide removal. UPW dilution effect on removal rate, coefficient of friction and pad surface temperature is explained by maintaining a constant dilution ratio for each of the SIS configuration tests. Results indicate that SIS negative rotation angles increase the actual slurry dilution ratio on top of the polishing pad. This generates more Ce3+ which boosts removal rates. Application of negatively rotated SIS allows significantly lower slurry flow rates and/or shorter polishing times leading to more environmental friendly semiconductor manufacturing processes. Finally, it is confirmed that variations in SIS configuration has no impact on silicon dioxide to silicon nitride removal rate selectivity. In the fifth and final part of our study, the silicon dioxide removal rate using a "reverse" ceria-based slurry is investigated under four different combinations of conditioning modes and slurry application methods. In a “reverse” slurry, addition of water acts to promote material removal. Overall, the process using ex-situ conditioning with the SIS results in the highest removal rate, while the process using in-situ conditioning with the conventional point application (PA) generates the lowest removal rate. This study explains the differences in silicon dioxide removal rate based on the variations of the actual slurry dilution ratio on the pad associated with conditioning and slurry application methods. Frictional analysis and Stribeck+ curves are employed to elucidate the tribological characteristics. Results show that the conditioning modes and the slurry application methods vary the extent of the polishing vibrations. Silicon dioxide removal rate is found to linearly correlate with the extent of COF fluctuation. The work underscores the importance of optimum slurry flow dynamics and injection geometry to obtain a more cost-effective and environmentally benign CMP process.

The ability of a lubricating oil to reduce friction in mechanical surfaces which are in relative sliding motion depends on the base oil behaviour. Previous studies have demonstrated that temperature has a significant influence on the friction behaviour of mineral and synthetic base oils by using a laboratory based friction testing machine. However, the effect of a constantly changing load under different temperature conditions has not been explored fully. In this study, the effect of an increasing load on the friction behaviour of four six different mineral base oils and a polyalphaolefin (PAO) base oil were studied using the SRV4® tribometer. The sliding surfaces were AISI 52100 steel ball and disc. The average loads (range: 50 – 250 N), temperatures (range: 40 – 120 oC), relative humidity of 20 % and a sliding speed of 0.2 m.s-1 were selected as the test conditions. The seven base oils were selected from four API base oil groups. Stribeck curves were used as a tool to characterize the friction behaviour of the base oils. The results show that for all the base oils, the coefficient of friction and the Stribeck parameter decrease gradually with the increase in applied normal load under constant temperature conditions. The increase in temperature increased the coefficient of friction and decreased the Stribeck parameter at each load stage. The external friction mechanisms dominated the friction behaviour under all test conditions. Viscosity showed a strong influence on the film forming characteristics of the seven base oils only at 40 and 60 oC. Between 80 and 120 oC, the oil-surface interactions were predominant. The results further demonstrated that effect of an increasing temperature on the coefficient of friction was bigger between 80 and 100 oC for all Group III base oils and was consistent between 40 and 120 oC for the Group III+ and PAO base oil. The highly saturated (PAO and Group III+) base oils have demonstrated good thermal stability and less reactivity compared to the less saturated base oils (GI and GIII) under all test conditions. The friction behaviour of the PAO base oil was the most affected by the presence of dissolved water. The presence of water proved to increase the friction at the sliding steel interfaces. / Dissertation (MEng)--University of Pretoria, 2018. / Chemical Engineering / MEng / Unrestricted

In Tribology, the well-known Stribeck curve is often used to relate friction behaviour to the properties of a system. Richard Stribeck, (Jacobson, 2003), (Stribeck, 1902) developed these curves while researching various bearings and found that the Stribeck curve can be generated for all tribological contacts of the Hertzian type. These curves give a relation between the coefficient of friction and the Sommerfeld number for a lubricant and given surfaces. All his test work was done on contacts that move in a single direction, unidirectional motion. This leaves the question, could Stribeck curves be applied to reciprocating contacts and how does linear velocity affect wear in these contacts? This research project is aimed to further the knowledge on how linear velocity affects reciprocating contacts with a focus on Stribeck curves and lubricity. Tests were conducted on two reciprocating instruments using ball and disk configurations. Two parameters were varied to change the linear velocity, namely oscillating frequency, and stroke length. To shift focus away from viscosity, n-Hexadecane was used as the base fluid due to its lack of lubrication properties. To improve the base fluid lubricity 3 carboxylic acids with 3 different chain lengths were used as additives. / Dissertation (MEng (Chemical Engineering)) Univercity of Pretoria, 2021. / Chemical Engineering / MEng (Chemical Engineering) / Restricted

Denna rapport undersöker hastighetsberoende friktionsbeteende i zinkpleterade 8.8 M12x1.75 skruvförband med en klämlängd på 82 mm och ett åtdragningsmoment på 120 Nm. Totalt 84 åtdragningar genomförs med nya skruvar, brickor och muttrar för varje åtdragning med utrustning tillhandahållen av Atlas Copco. All data importeras och analyseras i Matlab. Analysen visar att inom en standard avvikelse från medelvärdet kan klämkraften variera med så mycket som 90% beroende på var inom det 10-200 rpms hastighetsspannet skruven drogs åt. Vidare framgår även att restmomentet är mycket beroende av den hastighet som skruven drogs åt vid, med ett restmoment ~5 Nm över slutmomentet för 10 rpm och ~20 Nm över slutmomentet vid 200 rpm. En ursprunglig hypotes tas fram som antar att en utförlig modell av lastfördelningen i skruvensgänga och under skruvens skalle kan användas för att förutse skruvförbandets friktionsbeteende. Denna hypotes övergavs då mätresultat och analys visar att effekten av en förbättrad lastfördelningsmodell inte skulle märkas då spridningen i friktionen är för stor. / This report examines the speed dependency of frictional behavior in zinc plated 8.8 M12x1.75 bolt joints with an 82 mm clamping length at a tightening torque of 120 Nm. A total of 84 test tightenings have been performed with new bolts, nuts and washers for each tightening. The tests are performed using equipment supplied by Atlas Copco and all data is imported and analyzed in Matlab. It is found that within one standard deviation of the mean value the clamping force can vary as much as 90% depending on where in the 10-200 rpm speed range the bolt is tightened. Furthermore it is concluded that the residual torque is also highly speed dependent, registering at ~5 Nm above the final torque at 10 rpm and ~20 Nm above at 200 rpm. An initial hypothesis was developed regarding the pressure distribution in the thread and under the bolt head in the hopes that better understanding and modeling of this aspect could help predict frictional behavior in the bolt joint. This hypothesis was abandoned after it is concluded that the impact of an improved pressure model would be much too small to be noticeable due to the already large scatter in frictional coefficients.

La plupart des systèmes mécaniques contiennent des contacts lubrifiés (articulations, roulements, ...) qui sont soumis à des efforts importants. Dans ce travail expérimental, on s’intéresse à l’influence de la rugosité sur la friction dans les régimes de lubrification élastohydrodynamique (EHD), mixte, et limite dans des conditions représentatives des contacts dans un moteur de voiture. Les surfaces utilisées dans ce travail sont principalement des aciers usinés industriellement, revêtus ou non de Diamond-Like Carbon (DLC). La force de friction dans les régimes mixte et limite étant bien plus importante qu’en régime EHD, il est important de pouvoir prédire les transitions d’un régime à l’autre. Le problème est que la rugosité affecte significativement les vitesses de transition entre ces régimes, de telle manière qu’il est difficile de prédire le régime de fonctionnement d’un couple donné de surfaces. Les travaux expérimentaux s’attardant sur ce problème sont rares, et les tentatives théoriques d’inclure l’effet de rugosités aléatoires reposent sur des paramètres difficiles à mesurer à cause de leur grande dépendance vis-à-vis des conditions de filtrage, d’échantillonnage, et de leur non-stationnarité. à partir de nombreuses mesures topograhiques (interférométrie et AFM), une méthode assurant la représentativité des paramètres statistiques de rugosité est donc d’abord mise en œuvre pour caractériser des surfaces dont la rugosité va du nanomètre au micron. Des expériences de Stribeck sont ensuite menées avec ces surfaces afin de corréler leur signature morphologique à leur comportement en friction. La rhéologie sous pression de lubrifiants (poly-α oléfines) est mesurée dans un contact lisse en fonction de la pression et de la température, ce qui permet de prédire quantitativement la friction en régime élastohydrodynamique pour tout couple de surfaces, mais aussi de définir un critère non phénoménologique d’entrée en régime de lubrification mixte. à haute vitesse d’entraînement, la contrainte visqueuse décroît avec le taux de cisaillement ce qui est traditionnellement attribué à un échauffement du lubrifiant. On montre que les effets thermiques ne peuvent expliquer une telle chute et on l’explique par l’étalement du profil de pression dans le convergent, phénomène significatif quand l’épaisseur de lubrifiant devient de l’ordre d’un dixième de la taille du contact. Les résultats montrent que le produit de la viscosité dans le convergent avec la vitesse d’entraînement à la transition mixte-EHD suit une loi de puissance super-linéaire avec la rugosité, tous matériaux confondus, ce qui permet de prédire cette transition en fonction de la rugosité. La transition entre régimes mixte et limite est plus complexe et laisse apparaître un comportement clairement différent entre les contacts DLC/DLC et les contacts mettant en jeu au moins une surface d’acier. Pour les contacts DLC/DLC, la friction en régime limite correspond au cisaillement plastique du lubrifiant, ce qui explique que la rugosité n’affecte pas le frottement limite de ces contacts. Le frottement des contacts acier/acier et acier/DLC est plus important et présente deux évolutions monotones avec la rugosité composite du contact, que nous interprétons grâce à des expériences tribologiques à haut taux de glissement. Finalement, un modèle de portance mixte basé sur la théorie de Greenwood-Williamson est mis en œuvre et permet de reproduire avec une précision honorable les courbes de Stribeck obtenues expérimentalement. En particulier, ce modèle permet de déterminer les conditions d’échantillonnage optimales pour déterminer les propriétés des aspérités. / Most mechanical systems include lubricated contacts submitted to important strengths. The present work deals with the influence of surface roughness on friction in the elastohydrodynamic (EHD), mixed and boundary lubrication regimes, with operating conditions that are typically those found in an internal combustion engine. Most of the surfaces used in the experiments are machined steel, with or with a Diamond-Like Carbon (DLC) coating. Given the friction in boundary and mixed lubrication being higher than in EHD lubrication, it is crucial to predict the transitions between these regimes. These strongly depend on surface roughness. There are very few experimental works that deal with this issue, and the theoretical attempts to include the influence of random surface roughness are based on roughness parameters that are difficult to measure because of their dependence towards the sampling conditions and their non-stationarity. Based on numerous topographical surveys (using interferometry and AFM), a method is implemented to ensure the representativeness of roughness statistical parameters in order to characterize a range of surface roughnesses within the interval [0.001 ; 1] μm. Then, these surfaces are rubbed against each other using Stribeck procedures in order to correlate their morphology to their friction behaviour. The high-pressure rheology of poly-α olefins is measured in smooth contacts with respect to the pressure and the temperature. This not only allows to quantify the friction force for any contact operating in EHD lubrication, but also to set a criterion to spot the onset of mixed lubrication. At high entrainment speed, the viscous shear stress vanishes, which is often attributed to shear heating. It is shown that thermal effects can not explain such a drop of friction for our own experiments. However, the widening of the pressure profile — which becomes significant when the film thickness becomes comparable to a tenth the contact length — is more likely to explain this behaviour. Our results show that the product of the inlet viscosity with the entrainment speed, spotted at the mixed-EHD transition, follows a super linear power law with the RMS roughness, whatever the materials involved, which allows to predict whether a contact operate in mixed lubrication or not. The transition from mixed to boundary lubrication reveals material and roughness-dependent with a clearly different behaviour between DLC/DLC contacts and contacts involving at least one steel body. Regarding the DLC/DLC contacts, the boundary friction is due to the plastic shearing of the lubricant, which explains why surface roughness has no influence on boundary friction for these contacts. With Steel/DLC and steel/steel contacts, the boundary friction presents two monotonous trends versus the composite RMS roughness. Eventually, a mixed bearing model based on the Greenwood-Willimason assumptions was implemented and allowed to reproduce quite closely the experimentally obtained Stribeck curves. This implementation indicates in particular the sampling conditions that are optimal to capture relevant asperity parameters.

Numerous mechanical systems contain surfaces in partial or full sliding contact, and therefore, prone to friction-induced vibration instability. These include systems containing mechanical switches, brakes, clutches, gears, rolling contact bearings, journal bearings, robot end-effector grasp and motion, oil drills, etc. The prominent dynamic features of a mechanical system, subject to friction-induced vibration, can be captured by an appropriate equivalent mass-on-belt model. It is the goal of this research to provide a comprehensive study of friction-induced vibrations in mechanical systems by using their equivalent mass-on-belt models. Friction-induced vibration is manifested through three mechanisms termed Stribeck effect, mode-coupling and sprag-slip. Mechanical systems prone to vibrations by one or more of the three mechanisms of instability are considered and studied in detail. The mechanical systems fall into one of two groups. A system in the first group is the pseudo-rigid-body mass-on-belt representation of a compliant bistable linkage mechanism characterized by substantial geometric nonlinearity and nonlinear elasticity. A system in the second group is a mass-on-belt model that accounts for mass-belt contact stiffness. Such a system is excited primarily through mode coupling. In the first group of mechanical systems super and subcritical pitchfork bifurcation as well as Hopf bifurcation are observed. The normal force and spring pre-compression are bifurcation parameters leading to the subcritical pitchfork bifurcation and the belt velocity corresponds to the Hopf bifurcation. It is found that for a low damping and negligible spring nonlinearity, one equilibrium point dominates the steady-state response. Otherwise, the phase plane is split into two separate planes associated with the corresponding fixed point. The boundary is dictated by structural damping and spring nonlinearity. It is shown that the destabilizing mechanism in the bistable mechanisms is the Stribeck effect of friction. The dominant mode of instability for the second group of mechanical system is mode coupling instability. In this group intermittent loss of contact between the mass and the moving belt within a periodic cycle is allowed. Addition of a vibration absorber consisting of a second mass suspended from the first mass by a spring provides effective passive control of friction-induced instability due to mode-coupling. The research concludes with the study of a two mass system in which both masses are in contact with a belt and the friction force is characterized by the three regimes of lubricated contact that include boundary lubrication, mixed boundary and hydrodynamic lubrication and full hydrodynamic lubrication as sliding speed is increased. It is shown that such systems can experience periodic, quasi-periodic and chaotic vibration response.

Cette étude s'intéresse aux performances des matériaux composites Carbone/Carbone 2,5D lors d'un freinage aéronautique de basse énergie. Durant la vie avion, l'état de surface des disques de frein évolue et les performances de freinage s'en trouvent modifiées. Les études expérimentales et les modélisations réalisées ont pour buts la maîtrise et la prédiction de l'évolution des propriétés de la surface, cela en fonction à la fois des conditions tribologiques mais également de la distance dans deux environnements d'étude: à sec et lubrifié. Un premier volet de ce travail consiste à caractériser finement le comportement mécanique en compression du composite Carbone/Carbone 2,5D, afin de comprendre les répercussions du frottement en sous-couche. Après la détermination des caractéristiques élastiques du matériau, le comportement élasto-endommageable en compression est relevé. Ces caractéristiques sont implémentées dans une simulation 1D et permettent de reproduire les courbes d'essais de compression cyclique à contrainte croissante. Parallèlement, une étude du comportement tribologique du C/C 2,5D à sec via des essais courts a permis de connaître les caractéristiques des coefficients de frottement de différents états de surface. Les coefficients de frottement moyens sont mis en relation avec le paramètre de rugosité Sk. Les essais tribologiques longue distance mis en oeuvre ont modifié l'état de surface des échantillons tant sur le plan topographique que sur le plan morphologique. Des fissures en sous-couche apparaissent, conséquence des efforts tribologiques subis. Ces observations ont menés à la détermination d'un mécanisme d'évolution d'état de surface des disques en environnement sec. Enfin, deux types d'essais en environnement lubrifié ont été proposés, afin de séparer le comportement ponctuel d'un état de surface du comportement tribologique avec la distance. Premièrement, une procédure d'essais tribologiques courts a été mise en place et s'affiche comme un moyen de caractérisation d'état de surface in-situ à part entière, avec des caractéristiques des courbes de Stribeck directement liées aux états morphologiques et topographiques. Ensuite, un plan d'expérience réunit les essais longs destinés à modifier l'état de surface d'éprouvettes pour plusieurs jeux de paramètres tribologiques. Les courbes de Stribeck de ces nouveaux états de surface sont analysées. Ainsi, les états de surface expérimentaux sont comparés à ceux des disques de frein industriels. / This study focuses on the performance of 2.5D Carbon/Carbon composite materials for low energy aeronautical braking. During aircraft life, the surface condition of the brake discs evolves and the braking performances change. The experimental studies and the modelizations carried out aim in controlling and predicting the evolution of surface properties, both in terms of the tribological conditions but also of the distance in two study environments: dry and lubricated. For this purpose, a characterization of the mechanical behavior in compression of the 2.5D Carbon/Carbon composite is performed in order to understand the repercussions of friction underlayer. The elastic characteristics of the material and the elasto-damaging behavior in compression are identified. These characteristics are used in a 1D simulation, that allows reproducing the cyclic compression test curves with increasing stress. At the same time, a study of the tribological behavior of the dry 2.5D C/C composite via short tests made it possible to know the friction coefficient of different surface conditions. The average friction coefficients are related to the roughness. The long-range tribological tests used have modified the topographic and morphological surface conditions of the samples. Cracks appear at the underlayer, as a result of the tribological efforts. These observations led to the determination of a mechanism for the evolution of surface condition of discs in a dry environment. Finally, two types of lubricated environment tests have been proposed in order to separate the instantaneous behavior of a surface state from the tribological behavior with the distance. First, a short tribological test procedure is set up and is displayed as a means of in-situ surface condition characterization in its own right, with characteristics of the Stribeck curves directly related to the morphological and topographical states. Next, an experimental plan combines long tests to modify the surface condition of test pieces for several sets of tribological parameters. The Stribeck curves of these new surface states are analyzed. Experimental surface conditions are compared with those of industrial brake disks.

Le moteur à combustion, utilisé dans l’automobile est en perpétuelle évolution pour des raisons économiques et écologiques. Pour parvenir à de faibles consommations de carburant et émissions polluantes, l’un des axes étudiés est la réduction des pertes mécaniques par frottement du moteur qui constituent 15 à 20% de la consommation totale d’énergie du moteur. 50% de ces frottements proviennent des contacts Segment-Piston- Chemise et de la liaison Maneton-Bielle-Coussinet. De ce fait la compréhension de la tribologie de ce contact, l’optimisation de la lubrification et le vieillissement des lubrifiants deviennent primordiaux. L’objectif de cette thèse est d’étudier les mécanismes de lubrification de ces contacts segment/chemise et maneton/coussinet, et en particulier de comprendre l’influence du couplage additif, surface et matériau dans les différentes régimes de lubrification. Il s’agira de répondre à la question : comment maîtriser le frottement et l’usure en contrôlant la chimie du lubrifiant, la topographie et le matériau ? La démarche expérimentale choisie s’appuie sur l’analyse du comportement tribologique de deux additifs modificateurs de frottement sans cendres d’une part, puis sur l’impact du matériau et enfin sur l’influence de la topographie d’autre part. L’analyse de la cinétique d’évolution du coefficient de frottement et des traces d’usure en régime limite ont notamment permis d’identifier les mécanismes de réduction de frottement induits par les deux modificateurs étudiés. / The combustion engine used in automotive industry is constantly changing for economic and ecological reasons. To achieve low fuel consumption and pollutants emissions, one of research axes studied is the reduction of the mechanical friction loss of the motor which constitute 15-20 % of the total energy consumption of the engine. 50% of these come from friction contacts cylinder /piston rings and conrod bearing. Thereby understanding of tribology of the contact, optimizing lubrication and lubricants aging become paramount. The objective of this thesis is to study the mechanisms of lubrication of these contact (piston ring/cylinder and conrod bearing), and in particular to understand the influence of the additive coupling surface and material in the different lubrication regimes. This will answer the question : how to control the friction and wear by controlling the chemistry of the lubricant, the topography and the material ? The experimental approach chosen is based on the analysis of the tribological behavior of two friction modifiers additives ashless at first time, and on the impact of material and finally the influence of topography on the second time. XPS Analysis of the evolution of the coefficient of friction and wear track under boundary regime have enabled to identify mechanisms to reduce friction induced by the two modifiers studied.

Les garnitures mécaniques sont des composants d'étanchéité d'arbres tournants. Elles sont constituées de deux surfaces planes annulaires dont le contact est lubrifié par le fluide à étancher.L'opération de recherche « Jointlub » du département D3 de l'institut P' a développé des outils de simulation du comportement des garnitures par des méthodes analytiques, semi analytiques et numériques. En s'appuyant sur ces acquis, l'objectif de cette thèse vise à définir une méthodologie d'analyse préalable permettant l'optimisation de la modélisation du fonctionnement d'une garniture mécanique en fonction de la solution technologique choisie. Ceci consiste à proposer un procédé de choix d'outils de modélisation parmi les principaux types existants.Un ensemble d'indicateurs et de critères est développé afin de déterminer les phénomènes physiques prépondérants lors du fonctionnement d'une garniture dans des conditions données. Le modèle retenu pour la simulation devra prendre en compte les phénomènes identifiés.Des validations expérimentales ont été réalisées pour une garniture mécanique opérant dans différents régimes de fonctionnement. Une étude de l'évolution de la topographie des faces de frottement, du couple de frottement, du débit de fuite et du comportement thermique ont été effectués. Les expériences ont montré que le comportement des garnitures dépend fortement du régime de lubrification : mixte, hydrodynamique ou thermo-élasto-hydrodynamique.Les modèles théoriques ont été comparés aux résultats expérimentaux. Une bonne corrélation est obtenue dans leur domaine de validité, défini à partir des indicateurs. Des écarts plus importants sont observés lorsque les modèles sont utilisés dans des zones où ils ne prennent pas en compte l'ensemble des phénomènes physiques. Cette comparaison a montré que les indicateurs et critères de la méthode de choix proposée sont pertinents et permettent une bonne identification des phénomènes physiques à prendre en compte. / Mechanical face seals are sealing components for rotating shafts. It basically consists of two annular flat surfaces lubricated with a very thin film of sealed fluid.The "Seals lubrication" group of the Pprime institute has developed different modeling tools of mechanical face seals behavior by analytical, semi analytical and numerical methods. The objective of this thesis is to define a preliminary methodology to optimize the modeling of the mechanical seal taking into account the seal design. This analysis provides a suggestion of modeling tools among the existing types. A set of indicators and criteria are developed to determine the dominating physical phenomena during the operation of the seal under given conditions. The selected modeling tools should take into account the identified phenomena. Experimental validations were performed for a mechanical seal working in different operating conditions. Studies of the evolution of the friction faces topography, the friction torque, the leakage rate and the thermal effect were carried out. Experiments have shown that the behavior of the mechanical seal strongly depends on the lubrication regime: mixed, hydrodynamic and thermo-elasto-hydrodynamic.Theoretical models were compared with experimental results. A good correlation is obtained into their range of validity defined with preliminary analysis. Larger differences are observed when the models are used in conditions where unconsidered physical phenomena occur. This comparison showed that the indicators and criteria of the proposed method of choice are relevant and allows a good identification of the physical phenomena that should be taken into account.

A hydraulic damper plays an important role in tuning the handling and comfort characteristicsof a vehicle. Tuning and selecting a damper based on subjective evaluation, by considering theopinions of various users, would be an inefficient method since the comfort requirements of usersvary a lot. Instead, mathematical models of damper and simulation of these models in variousoperating conditions are preferred to standardize the tuning procedure, quantify the comfortlevels and reduce cost of testing. This would require a model, which is good enough to capture thebehaviour of damper in various operating and extreme conditions.The Force-Velocity (FV) curve is one of the most widely used model of a damper. This curve isimplemented either as an equation or as a look-up table. It is a plot between the maximum forceat each peak velocity point. There are certain dynamic phenomena like hysteresis and dependencyon the displacement of damper, which cannot be captured with a FV curve model, but are requiredfor better understanding of the vehicle behaviour.This thesis was conducted in cooperation with Volvo Cars with an aim to improve the existingdamper model which is a Force-Velocity curve. This work focuses on developing a damper model,which is complex enough to capture the phenomena discussed above and simple enough to beimplemented in real time simulations. Also, the thesis aims to establish a standard method toparameterise the damper model and generate the Force-Velocity curve from the tests performedon the damper test rig. A test matrix which includes the standard tests for parameterising andthe extreme test cases for the validation of the developed model will be developed. The final focusis to implement the damper model in a multi body simulation (MBS) software.The master thesis starts with an introduction, where the background for the project is described and then the thesis goals are set. It is followed by a literature review in which fewadvanced damper models are discussed in brief. Then, a step-by-step process of developing thedamper model is discussed along with few more possible options. Later, the construction of a testmatrix is discussed in detail followed by the parameter identification process. Next, the validationof the developed damper model is discussed using the test data from Volvo Hällered ProvingGround (HPG). After validation, implementation of the model in VI CarRealTime and Adams Caralong with the results are presented. Finally the thesis is concluded and the recommendations forfuture work are made on further improving the model. / En hydraulisk stötdämpare spelar en viktig roll för att fordonets hantering och komfort. Attjustera och välja en stötdämpare baserat på subjektiv utvärdering, genom att beakta olika användares åsikter, skulle vara en ineffektiv metod eftersom användarnas komfortkrav varierarmycket. Istället föredras matematiska modeller av stötdämpare och simulering av dessa modellerunder olika driftsförhållanden för att standardisera inställningsförfarandet, kvantifiera komfortnivåerna och minska testkostnaden. Detta skulle kräva en modell som är tillräckligt bra för attfånga upp stötdämparens beteende under olika drifts- och extrema förhållanden.Force-Velocity (FV) -kurvan är en av de mest använda stötdämparmodellerna. Denna kurvaimplementeras antingen som en ekvation eller som en uppslagstabell. Det är ett diagram somredovisar den maximala kraften vid varje maxhastighetspunkt. Det finns vissa dynamiskafenomen som hysteres och beroende av stötdämparens förskjutning, som inte kan fångas med enFV-kurvmodell, men som krävs för att bättre förstå fordonets beteende.Denna avhandling genomfördes i samarbete med Volvo Cars i syfte att förbättra den befintligastötdämparmodellen som är en Force-Velocity-kurva. Detta arbete fokuserar på att utveckla enstötdämparmodell, som är tillräckligt komplex för att fånga upp de fenomen som diskuteratsovan och tillräckligt enkel för att implementeras i realtidssimuleringar. Avhandlingen syftarockså till att upprätta en standardmetod för att parametrisera spjällmodellen och generera ForceVelocity-kurvan från de test som utförts på stötdämpartestriggen. En testmatris som innehållerstandardtest för parametrisering och extrema testfall för validering av den utvecklade modellenkommer att utvecklas. Det sista fokuset är att implementera stötdämparmodellen i en multi-bodysimulation (MBS) programvara.Examensarbetet inleds med en introduktion, där bakgrunden för projektet beskrivs ochdärefter definieras målen med arbetet. Det följs av en litteraturöversikt där några avanceradestötdämparmodeller diskuteras i korthet. Därefter diskuteras en steg-för-steg-process för attutveckla stötdämparmodeller tillsammans med några fler möjliga alternativ. Senare diskuteraskonstruktionen av en testmatris i detalj följt av parameteridentifieringsprocessen. Därefterdiskuteras valideringen av den utvecklade stötdämparmodellen med hjälp av testdata från VolvoHällered Proving Ground (HPG). Efter validering presenteras implementeringen av modellen iVI CarRealTime och Adams Car tillsammans med resultaten. Slutligen avslutas rapporten medslutsatser från arbetet och rekommendationer för framtida arbete görs för att ytterligare förbättramodellen.