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1990] and 434 [Diehl and Bodmann, 1990] for different times to rupture. In our case the lifetime of 105 hours was taken, since this is the longest lifetime for which the material data were reported. This constitutes component lifetimes of about 11.5 years. Given these material data it was possible to develop the temperature and stress dependent heat exchanger geometry. The temperature and stress dependent geometry of the PCHE heat exchanger used in this work includes evaluation of the plate thickness and the channel pitch. Hesselgraves [Hesselgraves, 2001] recommends the following formula for the minimum wall thickness tf: (9-1) where ∆p is the pressure differential between the hot and cold fluid (in this work 20 MPa is used), NF is the number of “fins” per meter and σD is the allowable stress, which is taken as the Alloy 800 stress rupture strength. The number of “fins” per meter means in the case of PCHE the number of channel walls per meter, since PCHE does not have typical fins. The fin thickness is depicted in Figure 9.2. The design pressure of 20 MPa is conservative for the helium indirect cycle since during normal operation the pressure difference between primary and secondary sides is 12 MPa (20 MPa for CO2 minus 8 MPa for helium) and 20 MPa only during transients involving depressurization of the power cycle. In the case of the lead alloy indirect cycle the situation is different since the lead alloy is at atmospheric pressure and thus the heat exchnager will be at all times under 20 MPa pressure. The channel pitch P is then calculated from: P=dc +tf (9-2) where dc is the channel diameter (2 mm) and tf is the fin thickness, which in this case is the wall thickness between the channels. An iteration loop is required since the number 215 tf=1 ⎛⎜σD +1⎞⎟N ⎜⎝∆p ⎟⎠FPDF Image | Advanced Nuclear Power Technology Program A Supercritical Carbon Dioxide Cycle for Next Generation Nuclear Reactors
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