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3.4 Matrix heat exchangers 27 place across the spacer. He has developed an algorithm to solve these equations in an iterative manner. Venkatarathnam's analysis for the thermal performance ofMHE's has been used as the basis for designing the MHE's for this project for two reasons: (a) Venkatarathnam's analysis represents the latest and most complete work on MHE's, in terms of accounting for the discrete plate-spacer pair sets and fin effectiveness. (b) His analysis was developed specifically for thermal performance of >~90% effectiveness. He was, however, unable to manufacture an MHE of high enough effectiveness to perform suitable experimental correlation. The effectiveness of the MHE reported in his results was only 65%. Using his analysis represents an opportunity for experimental correlation to his theoretical work. Using Venkatarathnam's analysis posed some problems. The source code of the program incorporating his solution algorithm for the energy balance and heat transfer equations, as presented in his thesis, does not run. He has developed an approximate analytical solution as well. This analytical solution was used, with modification, to derive a sizing equation for designing perforated plate MHE's for this project. The matrix heat exchangers built for this project used perforated plates made from copper and spacers made from glass laminate. The thermal mass of these heat exchangers is quite high and thus warranted a comparison with regenerator performance. In regenerators, the fluid and packing temperatures depend on time in addition to position. Mathematical analysis is even more complex and as a result several approximate and numerical solutions have been developed. These have been reviewed, and a summary of design theory presented, by Coppage and London[81]. No complete analytical solution is available for the equations describing the energy balance in the gas and packing except for the case CICmin=oo. In this case the behaviour becomes identical in form to that of a direct type counterflow heat exchanger. 1-e -Nlu(l-C IC ) mm ma.'t Ntu (3.4) (3.5) 8-___--:- Ntu+l where C is the product of mass flow rate and specific heat, and the subscripts r> min' and max refer to the regenerator and the minimum and maximum value of the product for the two gas streams, respectively. The mass flow rate of the regenerator is given by the product of its mass, specific heat and the number of regenerator cycles per second. For a fixed-bed regenerator the number of regenerator cycles per second is the reciprocal of the period of one complete flow reversal. Numerical finite-difference methods have been used by Lambertson[82] and Bahnke and Howard[74] to extend the results to coverPDF Image | CO2 removal from air for alkaline fuel cells operating with liquid H2
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