Chapter 11: Problem 190
In a parallel-flow heat exchanger, the NTU is calculated to be \(2.5\). The lowest possible effectiveness for this heat exchanger is (a) \(10 \%\) (b) \(27 \%\) (c) \(41 \%\) (d) \(50 \%\) (e) \(92 \%\)
Chapter 11: Problem 190
In a parallel-flow heat exchanger, the NTU is calculated to be \(2.5\). The lowest possible effectiveness for this heat exchanger is (a) \(10 \%\) (b) \(27 \%\) (c) \(41 \%\) (d) \(50 \%\) (e) \(92 \%\)
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Get started for freeConsider a water-to-water counterflow heat exchanger with these specifications. Hot water enters at \(90^{\circ} \mathrm{C}\) while cold water enters at \(20^{\circ} \mathrm{C}\). The exit temperature of the hot water is \(15^{\circ} \mathrm{C}\) greater than that of the cold water, and the mass flow rate of the hot water is 50 percent greater than that of the cold water. The product of heat transfer surface area and the overall heat transfer coefficient is \(2200 \mathrm{~W} / \mathrm{K}\). Taking the specific heat of both cold and hot water to be $c_{p}=4180 \mathrm{~J} / \mathrm{kg} \cdot \mathrm{K}\(, determine \)(a)\( the outlet temperature of the cold water, \)(b)$ the effectiveness of the heat exchanger, \((c)\) the mass flow rate of the cold water, and \((d)\) the heat transfer rate.
A shell-and-tube heat exchanger is to be designed to cool down the petroleum- based organic vapor available at a flow rate of \(5 \mathrm{~kg} / \mathrm{s}\) and at a saturation temperature of \(75^{\circ} \mathrm{C}\). The cold water \(\left(c_{p}=4187 \mathrm{~J} / \mathrm{kg} \cdot \mathrm{K}\right)\) used for its condensation is supplied at a rate of \(25 \mathrm{~kg} / \mathrm{s}\) and a temperature of \(15^{\circ} \mathrm{C}\). The cold water flows through copper tubes with an outside diameter of \(20 \mathrm{~mm}\), a thickness of $2 \mathrm{~mm}\(, and a length of \)5 \mathrm{~m}$. The overall heat transfer coefficient is assumed to be $550 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}$, and the latent heat of vaporization of the organic vapor may be taken to be \(580 \mathrm{~kJ} / \mathrm{kg}\). Assuming negligible thermal resistance due to pipe wall thickness, determine the number of tubes required.
By taking the limit as \(\Delta T_{2} \rightarrow \Delta T_{1}\), show that when \(\Delta T_{1}=\Delta T_{2}\) for a heat exchanger, the \(\Delta T_{\mathrm{lm}}\) relation reduces to \(\Delta T_{\mathrm{lm}}=\Delta T_{1}=\Delta T_{2}\).
The condenser of a room air conditioner is designed to reject heat at a rate of \(22,500 \mathrm{~kJ} / \mathrm{h}\) from refrigerant- \(134 \mathrm{a}\) as the refrigerant is condensed at a temperature of \(40^{\circ} \mathrm{C}\). Air \(\left(c_{p}=1005 \mathrm{~J} / \mathrm{kg} \cdot \mathrm{K}\right)\) flows across the finned condenser coils, entering at \(25^{\circ} \mathrm{C}\) and leaving at \(32^{\circ} \mathrm{C}\). If the overall heat transfer coefficient based on the refrigerant side is $150 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}$, determine the heat transfer area on the refrigerant side.
A counterflow double-pipe heat exchanger with \(A_{s}=9.0 \mathrm{~m}^{2}\) is used for cooling a liquid stream \(\left(c_{p}=3.15\right.\) $\mathrm{kJ} / \mathrm{kg} \cdot \mathrm{K})\( at a rate of \)10.0 \mathrm{~kg} / \mathrm{s}$ with an inlet temperature of \(90^{\circ} \mathrm{C}\). The coolant \(\left(c_{p}=4.2 \mathrm{~kJ} / \mathrm{kg} \cdot \mathrm{K}\right)\) enters the heat exchanger at a rate of \(8.0 \mathrm{~kg} / \mathrm{s}\) with an inlet temperature of \(10^{\circ} \mathrm{C}\). The plant data gave the following equation for the overall heat transfer coefficient in $\mathrm{W} / \mathrm{m}^{2} \cdot \mathrm{K}: U=600 /\left(1 / \dot{m}_{c}^{0.8}+2 / \dot{m}_{\mathrm{h}}^{0.8}\right)\(, where \)\dot{m}_{c}\( and \)\dot{m}_{k}$ are the cold- and hot-stream flow rates in \(\mathrm{kg} / \mathrm{s}\), respectively. ( \(a\) ) Calculate the rate of heat transfer and the outlet stream temperatures for this unit. (b) The existing unit is to be replaced. A vendor is offering a very attractive discount on two identical heat exchangers that are presently stocked in its warehouse, each with $A_{s}=5 \mathrm{~m}^{2}$. Because the tube diameters in the existing and new units are the same, the preceding heat transfer coefficient equation is expected to be valid for the new units as well. The vendor is proposing that the two new units could be operated in parallel, such that each unit would process exactly one-half the flow rate of each of the hot and cold streams in a counterflow manner, hence, they together would meet (or exceed) the present plant heat duty. Give your recommendation, with supporting calculations, on this replacement proposal.
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