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HiRadMat Window Design report v2.0 1Michael MONTEIL- 16 March 2010

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Specifications v2.0 Interface between machine vacuum and Atmospheric pressure 10 -8 mbar / P atm Protective atmosphere !!! Diameter 60 mm (Updated) Thickness 5 mm (Updated) Resist to a proton beam size on the window : 1 = 0.5 mm Beam Size at the TT66 Vacuum Window, C. Hessler, 26.02.2010 2Michael MONTEIL- 16 March 2010

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Window geometry – C-C option Carbon/Carbon composite: 1501 G from SGL Cylindrical window Diameter 80 mm (Updated) – Aperture 60 mm (Updated) Thickness: 0.5 cm (Updated) Aperture ( flange internal diameter ): 60 mm (Updated) 3Michael MONTEIL- 16 March 2010

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Solutions #1 for C-C tightness problem: Differential vacuum (V1.0) 1 Window C-C – Pumping speed needed: 8.4 x 10 9 l/s … 2 Windows C-C with differential pumping – Pumping speed needed: 8.4 x 10 3 l/s … 3 Windows C-C with differential pumping – Pumping speed needed: 8.4 x 10 1 l/s OK 4Michael MONTEIL- 16 March 2010

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Solutions #1 for C-C tightness problem: Differential vacuum (New values V2.0) 1 Window C-C – Pumping speed needed: 2.3 x 10 8 l/s … 2 Windows C-C with differential pumping – Pumping speed needed: 8.94 x 10 2 l/s OK ! 3 Windows C-C with differential pumping – Pumping speed needed: 13 l/s Too low ?! 5Michael MONTEIL- 16 March 2010

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Solutions #1 What about radiations in this area ? – Possible maintenance needed on the roots pump… Protective atmosphere Decreasing pressure in Vacuum side with serial pumps Michael MONTEIL- 16 March 20106

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7 P2 : Roots pump 100 –> 1500 m 3 /h 10 -3 -> 10 Bar P3 : Ion pump 400 l/s Reference

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Solutions #2 for C-C tightness problem: Add a Graphite foil (v1.0) 8Michael MONTEIL- 16 March 2010 Solution #3 : Tight steelring with a C-C plate (v1.0)

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Solution #4 : Beryllium Metal -> Tight !! No differential pumping Simple window assembly Thin thickness Toxicity Price Michael MONTEIL- 16 March 20109

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Solution #5 : Be + C-C Solution #4 but the pressure load is supported by a C-C plate Simple window assembly Thin thickness (no differential pumping…) Be cannot pollute vacuum unless C-C fail Tight Price… but compare to intermediate Vac. Pumps price ? Michael MONTEIL- 16 March 201010

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Solutions - Sum-up #1: C-C (Differential pumping) – Protective atm (Nitrogen ?) – Radiations? #2: C-C + Graphite foil (useless now) #3: Tight steel ring with a C-C plate #4: Beryllium – Safety problem #5: C-C + Beryllium Michael MONTEIL- 16 March 201011

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ANSYS Study - Solutions #1 stresses and deflection - C-C under P = 1.4atm Linear circular fixed support 2 planes of symmetry Geometry – Diameter 80 mm – Thickness: 5 mm – Aperture: 60 mm Pressure 1.4 bar 12Michael MONTEIL- 16 March 2010

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ANSYS Study - Solutions #1 stresses and deflection - C-C under P = 1.4atm Orthotropic properties : 18 plies [0°/90°…] Smooth and continuous temperature distribution Through-thickness energy deposition Coefficient of Thermal Expansion varying with temperature and directions 13Michael MONTEIL- 16 March 2010

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C-C - Pressure load - Deflection 14Michael MONTEIL- 16 March 2010 7.4 μm

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C-C - Pressure load – Von-Mises 15Michael MONTEIL- 16 March 2010 5.9 Mpa

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C-C - Pressure load – Tsaï-Wu 16Michael MONTEIL- 16 March 2010

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C-C - Thermal load ANSYS input = FLUKA output Radial C-C | 1 = 0.5 mm | 1.7e11 p+ | 288 bunches Axisymmetrical radial temperature field Depth R (cm) T (°C) Z (cm) T (°C) 17Michael MONTEIL- 16 March 2010

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C-C - Pressure + Thermal load – Deflection 18Michael MONTEIL- 16 March 2010 10.6 μm

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C-C - Pressure + Thermal load – Von-Mises 19Michael MONTEIL- 16 March 2010 31 Mpa

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C-C - Pressure + Thermal load – Tsaï- Wu 20Michael MONTEIL- 16 March 2010

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ANSYS Study - Solutions #4 stresses and deflection - Be under P = 1.4atm Linear circular fixed support 2 planes of symmetry Geometry – Diameter 80 mm – Thickness: 0.254 mm – Aperture: 60 mm Pressure 1.4 bar 21Michael MONTEIL- 16 March 2010

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ANSYS Study - Solutions #4 stresses and deflection - Be under P = 1.4atm Smooth and continuous temperature distribution Through-thickness energy deposition Coefficient of Thermal Expansion varying with temperature Be: – Poissons ratio = 0.1 – High R e = 275 Mpa – High R m = 551 MPa 22Michael MONTEIL- 16 March 2010

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Be - Pressure load - Deflection 23Michael MONTEIL- 16 March 2010 8.1 mm

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Be - Pressure load – Von-Mises 24Michael MONTEIL- 16 March 2010 319 Mpa

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Be - Pressure load – Safety factor Ult. Strength Michael MONTEIL- 16 March 201025 1.7

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Be - Thermal load ANSYS input = FLUKA output Be | 1 = 0. 5 mm | 1.7e11 p+ | 288 bunches Axisymmetrical radial temperature field Z (cm) T (°C) 26Michael MONTEIL- 16 March 2010 Z (cm) Radial Be T (°C)

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Be - Pressure + Thermal load – Deflection 27Michael MONTEIL- 16 March 2010 8 mm

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Be - Pressure + Thermal load – Von-Mises 28Michael MONTEIL- 16 March 2010 315 Mpa

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Be - Pressure + Thermal load – Safety factor Ult. Strength Michael MONTEIL- 16 March 201029 1.7

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ANSYS Study - Solutions #5 stresses and deflection - C-C+Be under P = 1.4atm 2 Studies – C-C (See Solution #4) Pressure load Pressure + Temperature loads – Be (Following slides) Flattered on a C-C plate (Fixed support) and apply pressure load on the other side Flattered on a C-C plate (Fixed support) and apply pressure load on the other side + Temperature load 2 planes of symmetry Geometry – Diameter 80 mm – Thickness C-C: 5 mm Be: 0.254 mm – Aperture: 60 mm Pressure 1.4 bar 30Michael MONTEIL- 16 March 2010

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ANSYS Study - Solutions #5 stresses and deflection - C-C+Be under P = 1.4atm Smooth and continuous temperature distribution Through-thickness energy deposition Coefficient of Thermal Expansion varying with temperature 31Michael MONTEIL- 16 March 2010

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32 Be (flatter on C-C) - Pressure load – Deformation

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Be (flatter on C-C) - Pressure load – Von-Mises Michael MONTEIL- 16 March 201033

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Thermal load ANSYS input = FLUKA output Radial C-C C-C + Be | 1 = 0.5 mm | 1.7e11 p+ | 288 bunches Axisymmetrical radial temperature field Depth C-C T (°C) Z (cm) T (°C) 34Michael MONTEIL- 16 March 2010 Z (cm) Radial Be

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Be (flatter on C-C) - Pressure + Thermal load – Deflection Michael MONTEIL- 16 March 201035 x 2.6e+002

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Be (flatter on C-C) - Pressure + Thermal load – Von-Mises Michael MONTEIL- 16 March 201036

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Be (flatter on C-C) - Pressure + Thermal load – Safety factor Ult. Strength Michael MONTEIL- 16 March 201037

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To do : Rough mechanical design – Solution #1 C-C with differential pumping Maybe coating 15 cm length between upstream and downstream sides – Solution #5 C-C + Be Order quotes of Be Same design that window in TI8, TI2, TT41 (Design by Kurt Weiss, Luca Bruno and Jose Miguel Jimenez) but replacing the Ti foil by a Be foil Nickel-coating to prevent oxidation on Be ? 15 cm length between upstream and downstream sides 38Michael MONTEIL- 16 March 2010

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Back up slides Michael MONTEIL- 16 March 201040

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C-C 1.4 bar diameter 146 mm (v1.0) Michael MONTEIL- 16 March 201041

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Pressure load - Deflection 42Michael MONTEIL- 16 March 2010

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Pressure load – Von-Mises 43Michael MONTEIL- 16 March 2010

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Pressure load – Tsaï-Wu 44Michael MONTEIL- 16 March 2010

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Thermal load ANSYS input = FLUKA output Radial C-C | 1 = 0.25 mm | 1.7e11 p+ Axisymmetrical radial temperature field Depth R (cm) T (°C) Z (cm) T (°C) 45Michael MONTEIL- 16 March 2010

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Pressure + Thermal load – Deflection 46Michael MONTEIL- 16 March 2010

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Pressure + Thermal load – Von-Mises 47Michael MONTEIL- 16 March 2010

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Pressure + Thermal load – Tsaï-Wu 48Michael MONTEIL- 16 March 2010

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Be Only Pressure 1 bar instead of 1.4 bar Michael MONTEIL- 16 March 201049

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Pressure load - Deflection 50Michael MONTEIL- 16 March 2010

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Pressure load – Von Mises 51Michael MONTEIL- 16 March 2010

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Pressure load – Safety factor Ult. Strength Michael MONTEIL- 16 March 201052

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Thermal load ANSYS input = FLUKA output C-C | 1 = 0.25 mm | 1.7e11 p+ Axisymmetrical radial temperature field Z (cm) T (°C) 53Michael MONTEIL- 16 March 2010 Z (cm) Radial Be T (°C)

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Pressure + Thermal load – Deflection 54Michael MONTEIL- 16 March 2010

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Pressure + Thermal load – Von-Mises 55Michael MONTEIL- 16 March 2010

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Pressure + Thermal load – Safety factor Ult.Strength Michael MONTEIL- 16 March 201056

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