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Manifolding and MHD issues

Manifolding and MHD issues. M. S. Tillack, S. Malang, X. R. Wang. ARIES Project Meeting 31 May – 1 June, 2012. Next Steps for MHD and thermal hydraulics (from January Project Meeting). Provide final guidance on MHD D p. Select the FW channel depth. Choose k for inlet/outlet manifolds.

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Manifolding and MHD issues

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  1. Manifolding and MHD issues M. S. Tillack, S. Malang, X. R. Wang ARIES Project Meeting 31 May – 1 June, 2012

  2. Next Steps for MHD and thermal hydraulics(from January Project Meeting) • Provide final guidance on MHD Dp. • Select the FW channel depth. • Choose k for inlet/outlet manifolds. • Need full definition of flow paths, flow control • Provide temperature boundary conditions for thermal stress analysis. • Full heat transfer analysis • Start analysis of DCLL (ACT-3) blanket.

  3. Added Topics • Definition of ACT1 flow loop pressures and temperatures,power conversion system parameters. • Further definition of lower manifold region. • Proposed use of “flow balancing”.

  4. We have minimized 3D MHD effects throughout the SCLL blanket, except inlet FW manifolds Radial paths Radial variation in field and velocity 90˚ bend 180˚ bends No problem Minor problem Curved flow Radial variation in field and velocity Radial contraction Central duct OK. Annular channels require control. Manifolding and distribution No problem Field entrance and exit TF unavoidable, PF can be reduced

  5. New access pipe routing reduces PF fields experienced by the fluid

  6. Central manifolds use successive splits plus toroidal movements with poloidal component Good (IB now has 8 parallel ducts) • Coaxial pipes everywhere • Gradual toroidal motions • Symmetric splts (some extra Dp, but flow balanced) • FW manifolds are a problem.Electrodes are recommended.

  7. “Flow balancing” technique forces equal potential between parallel channels • Higher velocity channels generate excess current that pumps the lower-velocity channels. • Effectiveness is related to the additional 3d pressure drop. • Compatibility of PbLi with W has been studied (Feuerstein, J. Nuc Mater 1996) up to 600 C. M. S. Tillack and N. B. Morley, “Flow Balancing in Liquid Metal Blankets,” Fusion Eng. Design27 (1995) 735-741.

  8. Heat exchanger Pressures and pressure drops for the ARIES SCLL IB blanket Dp = 0.25 MPa 0.25 (outboard Dpmhd will be lower) p > 0 4 m (0.4 MPa) Dptop = 0.1 MPa 0.95 0.85 Dpbulk = 0 8 m (0.8 MPa) DpFW = 0.2 MPa 1.65 1.95 Dpout = 0.2 MPa Dpin = 0.45 MPa 2.4 4 m (0.4 MPa) 1.45 1.2 MPa pump 1.6 2.8 1.85 1.85

  9. Semi-empirical formulation of 3D MHD effects Dp3d = k N (rv2/2) where N = Ha2/Re, and k is a semi-empirical constant (z=kN)` • For flows with geometrical changes in a uniform magnetic field 0.25 < k < 2. • For a change in transverse field strength k~0.1–0.2 (depending on the abruptness of the change in B). • For an inlet or outlet manifold, Smolentsev et al used k=1.5. • Depends on wall conductance, pipe shape (e.g. circular or rectangular) and other details. I.R. Kirillov, C.B. Reed, L.Barleon, K. Miyazaki, “Present understanding of MHD and heat transfer phenomena for liquid metal blankets, “Fusion Eng and Design 27 (1995) 553-569. S. Smolentsev, C. Wong, S. Malang, M. Dagher, M. Abdou, “MHD considerations for the DCLL inboard blanket and access ducts,” Fusion Eng and Design 85 (2010) 1007–1011.

  10. Final design of blanket based on 2 MPa internal pressure (1 cm annular cooling channel depth for all) 45 cm 30 cm 35 cm Inboard(8 per sector) Outboard I(12 per sector) Outboard II(12 per sector)

  11. Convective heat transfer with laminar slug flow Energy balance equation (internal energy e=rCpT): Exact solution for constant velocity on a semi-infinite plane is equivalent to transient 1D conduction: slug Example slug result: T vs. z/v for several x, q”=0.2 MW/m2, v=4.2 m/s,L=8.3 m

  12. Computational approach for variable flow FW and SW flows are mixed to create uniform central duct inlet temperature

  13. 1-dimensionalized FW velocity profile <v> = 2.66 m/s in FW channel Worst case profile that conserves <v> All other channels have constant velocity (0.094 m/s center, 0.266 m/s SW)

  14. Results (radial profiles)

  15. Results (axial profiles)

  16. Temperature restrictions on components reduces the power cycle performance Heat exchanger temperatures on the primary and secondary sides

  17. Power flows and bulk coolant temperatures in ARIES ACT SCLL 1030 C hot (ACT-1b strawman) 1000 C 1565 MW 6 MW 740 C PbLi HX FW blanket h=58% cold 325 MW 710 C divertors 800 C hot pump heat pump heat 700 C He HX 17 MW 680 C 600 C 228 MW hot shields 650 C cold compressors to He HX recuperator 600 C from PbLi HX Heat sink 1000 C turbine

  18. Brayton cycle efficiency and power core inlet temperature 1000 C turbine inlet temperature 1050 C turbine inlet temperature ARIES-AT operating point

  19. Next step activities • Update ACT1 MHD, thermal-hydraulic and geometric parameters (after final strawman is available). • Recalculate MHD, thermal-hydraulic and geometric parameters for ACT2 (after strawman is available). • Start analysis of DCLL (ACT-3) blanket. • Overall configuration will be very similar to ACT1 • Manifolding will be simpler

  20. Extras

  21. 3D MHD is the dominant force acting upon the coolant in insulated channel blankets FW blanket inertia gravity wall shear 3D MHD ru2 rgL suB2L/Ha kN (ru2)/2 160,000 8x105 190,000 3x106 100 8x105 475 7x105 conservative u dissipative L g A

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