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28 Chapter 3 Heat exchanger design and construction l~ClIlijClIlax~O.l, l:S;C/ClIlin:S;oo and 1:s;Ntu:S;100. For C/Cmin>5 the solution is very close tothelimitingsolutionofC/ClIlin=00 andhencetothatofadirecttypecounterflowheat exchanger. 3.4.4 Heat transfer and flow friction data The total heat transfer resistance between the fluid streams is made up of: convective heat transfer between the gas and the perforated plates; and conduction along the screens, and across the separator. The convective heat transfer process and flow friction characteristics of a matrix heat exchanger are complex. The flow cross section changes substantially, continuously, between that ofthe mesh or perforated plate and that of the spacer. Consequently, the fluid undergoes alternate expansion and contraction as it flows through the exchanger. Two stacking arrangements for the perforated plates or wire mesh are possible, the perforations of adjoining plates being aligned or staggered. Mikulin et al.[83] and Venkatarathnam and Sarangi[84] suggest that for the staggered case, and the aligned case where spacer thickness is greater that the pore diameter, the boundary layer is interrupted at every screen maintaining developing flow. In the aligned case, if the spacer thickness is less than or equal to the pore diameter the flow through the perforations tends to become developed turbulent flow, with a secondary recirculation or stagnant zone occurring in the gaps. 3.4.4.1 Convective heat transfer Convective heat transfer occurs at the front and back faces of the plates and in the tubular surface of the perforations. The fluid impinging continuously on the front face of the plates gives heat transfer coefficients that are an order of magnitude higher than those normally associated with gaseous heat transfer. Heat transfer data and empirical correlations for perforated plates have been determined by McMahon et al.[70], Mikulin et al.[83], Orlov et al.[85], Shevyakova and Orlov[86], and Hubbell and Cain[87]. These are tabulated in Table 3.1. Heat transfer data and empirical correlations for wire mesh have been determined by Coppage and London[88], Tong and London[89], and Mikulin and Shevich[90]. The general approach has been to find an empirical relation of the form Nu=C Re n (3.6) to fit the data, where C and n are functions of geometric parameters and Re is based on the flow velocity in the perforation and the perforation diameter as the characteristic dimension. For this work the equation (3.7) derived by Venkatarathnam[80], combining empirical equations for heat transfer from impinging jets on facing and lee sides of a plate and the cylindrical surface of perforations, has been used for the design of the perforated plates. This was done with correlation of the experimental work to hisPDF Image | CO2 removal from air for alkaline fuel cells operating with liquid H2
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