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LES of a bi-periodic turbulent flow with effusion 3 Isothermal Flow measurements Non-isothermal Wall data JCF and FC Andreopoulos & Rodi (1984) (I) Goldstein (1971) (I) Pietrzyk et al. (1989) (I) Eriksen & Goldstein (1974) (I) Fric & Roshko (1994) (I) Ammari et al. (1990) (I) Kelso et al. (1996) (I) Smith & Mungal (1998) (I) MacManus & Eaton (2000) (S) Peterson & Plesniak (2004a) (S/H/I) FCFC Yavuzkurt et al. (1980a,b) (I) Metzger et al. (1973) (I) Gustafsson (2001) (I) Mayle & Camarata (1975) (I) Miron (2005) (I) Crawford et al. (1980) (I) Cho & Goldstein (1995a,b) (S/H/I) Rouvreau (2001) (I) Dorignac et al. (2005) (S) Table 1. Major experimental studies concerning jets in crossflow (JCF), film cooling (FC) and full-coverage film cooling (FCFC), depending on if the injection (I), the suction (S) or the hole (H) are studied. The classification depends on the thermal characteristics (isothermal/non-isothermal) and on the type of data provided. Flow measurements: spatially resolved data is provided, e.g. temperature, velocity or vorticity fields and profiles; Wall data: integrated or local wall data is provided, e.g. adiabatic or overall cooling effectiveness, or heat transfer coefficient. Note that no references were found with flow measurements in a non-isothermal case. Isothermal Non-isothermal JCF and FC Yuan et al. (1999) (I) Walters & Leylek (2000) (H/I) Schlüter & Schönfeld (2000) (I) Tyagi & Acharya (2003) (H/I) Cortelezzi & Karagozian (2001) (I) Renze et al. (2006) (H/I) Prière et al. (2005) (I) Iourokina & Lele (2006) (S/H/I) MacManus & Eaton (2000) (S) Peet (2006) (S/H/I) FCFC no reference found Papanicolaou et al. (2001) (I) Harrington et al. (2001) (I) Table 2. Major numerical studies concerning jets in crossflow (JCF), film cooling (FC) and full– coverage film cooling (FCFC), depending on if the injection (I), the suction (S) or the hole (H) are studied. The classification depends on the thermal characteristics (isothermal/non-isothermal) of the configuration. from the canonical configurations of JCF in several aspects (see the review by Margason (1993) for more details about canonical JCF): (a) While single canonical JCF is usually designed to penetrate in the main flow and enhance mixing, the purpose of effusion jets is to create a film to protect the wall from the hot gases. Many jets are used to form the film, and they are oriented so that cooling air stays next to the wall, without mixing with the main flow. Note that both configurations are encountered in gas turbines: contrary to the small cooling jets that protect the wall, JCF called dilution jets are designed to penetrate the combustion chamber to dilute the combustion products in the secondary zone, (b) In FCFC, the crossflow is not a simple boundary layer as for JCF studies but results from the interaction between all the jets located upstream,
4 S. Mendez and F. Nicoud (c) The inclination of the jets in FCFC application is smaller than in JCF, modifying the penetration of the jets as well as the interaction with the main flow (see for example Bergeles, Gosman & Launder 1976, 1977), (d) Because of the small length-to-diameter ratio of the holes used in FCFC applications, the flow on the injection side is strongly related to the flow in the aperture and on the suction side (Iourokina & Lele 2006; Peterson & Plesniak 2004a; Walters & Leylek 2000). This is particularly striking in studies about discharge coefficient, where the velocity in the supply channel is one of the main parameters (Champion et al. 2005; Gritsch et al. 2001). In views of these differences, extrapolating the results from canonical JCF studies to gain insight into FCFC would not be justified and specific FCFC configurations must be considered. This is in line with Walters & Leylek (2000) who insist on the importance of reproducing the exact geometry for film cooling studies. The aim of this study is to generate detailed data numerically and to reach a better understanding of turbulent flows with effusion, a first step towards the development of appropriate wall models for FCFC. Ideally, relevant data to build FCFC models would contain detailed information about the dynamical and thermal behaviours of the flow on both sides of the plate and would correspond to a realistic FCFC configuration, viz. with a large array of holes submitted to non-isothermal flow conditions. From tables 1 and 2, such data does not exist. Detailed flow measurements in non-isothermal situations have never been performed and the complete configuration (suction side/hole/injection side, as in Cho & Goldstein 1995a,b) has been rarely considered. Only Peet (2006), Iourokina & Lele (2006) and Peterson & Plesniak (2004a) detail the flow on the suction side, in the aperture and on the injection side. However, only one row of holes is considered and all the flow on the suction side is forced through the holes, as in FC applications. Few studies concern the suction side of the plate: MacManus & Eaton (2000) treat the suction of a laminar boundary layer by an isolated hole and a small array of holes, in an isothermal configuration. Dorignac et al. (2005) propose global measurements and correlations of the Nusselt number on the suction side of a multi-perforated plate. However, the aspiration is performed from a medium at rest, which is not representative of the real conditions in the casing of a gas turbine. Most of the experimental studies concerning discrete-hole film cooling address the case of a single row of holes (cooling application for turbine blades) so that only few studies dealing with several rows configurations are available. All the spatially resolved aerodynamic measurements available correspond to large-scale isothermal flows (Gustafsson 2001; Miron 2005; Yavuzkurt, Moffat & Kays 1980a,b). Moreover, experimental studies addressing the thermal behaviour (evaluation of cooling effectiveness or heat transfer coefficient at the wall) do not provide any flow measurements (Cho & Goldstein 1995a,b; Crawford, Kays & Moffat 1980; Mayle & Camarata 1975; Metzger, Takeuchi & Kuenstler 1973) or insufficiently resolved ones (Rouvreau 2001). Note however the very interesting work by Cho & Goldstein (1995a,b), who estimated the local wall heat transfer on the back surface (suction side), the holes and the exposed surface (injection side) on both FC and FCFC configurations. Numerical capabilities have increased during the last years and RANS simulations of FCFC with several rows (7 for Papanicolaou et al. (2001), 10 for Harrington et al. (2001) and 12 rows for Errera & Chemin (2004)) have been performed. These simulations prove the ability of numerical codes to reproduce effusion flows. However, the idea of designing wall models by using RANS based data remains questionable. As long as only a few numbers of holes are considered, Large-Eddy Simulations (LES) can be performed in place of RANS calculations in order to gain insight into the jet-mainstream interaction. Recently,
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UNIVERSITE MONTPELLIER II SCIENCES
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Table des matières Remerciements 7
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Remerciements Cette thèse a été
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Liste des symboles Lettres romaines
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Introduction générale La volonté
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Chapitre 1 Contexte industriel et s
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1.1 Les turbines à gaz pour les tu
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1.1 Les turbines à gaz a) b) GAZ C
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1.2 La simulation numérique des é
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1.3 Objectifs et plan de la thèse
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Chapitre 2 L’écoulement autour d
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2.1 Présentation de la configurati
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2.2 Perte de charge au passage d’
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2.3 La multi-perforation : aspects
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2.4 Caractérisation aérodynamique
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Page 67 and 68: 2.5 Modélisation de la multi-perfo
Page 69 and 70: Chapitre 3 Simulations des grandes
Page 71 and 72: 3.2 Simulations des Grandes Echelle
Page 73 and 74: 3.3 Le code de calcul AVBP 3.3.1 As
Page 75 and 76: 3.3 Le code de calcul AVBP dans le
Page 77 and 78: 3.3 Le code de calcul AVBP de sa st
Page 79 and 80: Chapitre 4 Simulations numériques
Page 81 and 82: 4.1 Quelles simulations pour la mod
Page 83 and 84: 4.2 Choix de la méthode de simulat
Page 85 and 86: 4.2 Choix de la méthode de simulat
Page 87 and 88: 4.3 Sensibilité des simulations au
Page 97 and 98: Chapitre 5 Simulations numériques
Page 99: 2 S. Mendez and F. Nicoud COMBUSTIO
Page 103 and 104: 6 S. Mendez and F. Nicoud CALCULATI
Page 105 and 106: 8 S. Mendez and F. Nicoud Name Numb
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Page 109 and 110: 12 S. Mendez and F. Nicoud main, it
Page 111 and 112: 14 S. Mendez and F. Nicoud 1.0 a 1.
Page 113 and 114: 16 S. Mendez and F. Nicoud ROWS 1 3
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Page 119 and 120: 22 S. Mendez and F. Nicoud & Mahesh
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Page 135 and 136: 38 S. Mendez and F. Nicoud Mendez,
Page 137 and 138: Chapitre 6 Un modèle adiabatique p
Page 139 and 140: ρ Mass density, kg/m 3 P T V i τ
Page 141 and 142: cence of the jets. This is particul
Page 143 and 144: Simulations. The small-scale LES re
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Page 147 and 148: pressure drop of 41 Pa is effective
Page 149 and 150: Region total plate hole solid wall
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This equality is almost verified at
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V U σ V inj jet cotan(α′ ) V U
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PERIODIC Z INFLOW 1 WALL 24 OUTFLOW
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part of the plate. Downstream of th
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streamwise momentum flux. As a cons
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8 Fric, T. and Roshko, A., “Vorti
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Discussion sur la modélisation de
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20 15 10 y/d 5 0 -5 -10 0.0 0.2 0.4
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Chapitre 7 Simulations numériques
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Primary flow (burnt gases) Secondar
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Figure 7: Nusselt number over the s
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the perforated plate. A Large-Eddy
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Les tableaux de flux permettent de
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Conclusion générale Dans cette é
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Conclusion générale En ce qui con
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Bibliographie AKSELVOLL, K. & MOIN,
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BIBLIOGRAPHIE CORON, X. 2001 Étude
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BIBLIOGRAPHIE HALE, C. A., PLESNIAK
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BIBLIOGRAPHIE LIEUWEN, T. & YANG, V
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BIBLIOGRAPHIE MOST, A. & BRUEL, P.
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BIBLIOGRAPHIE SCHILDKNECHT, M., MIL
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Annexes
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ARTIFICIAL VISCOSITY MODELS A.2.1 T
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ARTIFICIAL VISCOSITY MODELS - 4 th
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ARTIFICIAL VISCOSITY MODELS As a co
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ARTIFICIAL VISCOSITY MODELS 202
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