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Glycerin \(\left(c_{p}=2400 \mathrm{~J} / \mathrm{kg} \cdot \mathrm{K}\right)\) at \(20^{\circ} \mathrm{C}\) and \(0.5 \mathrm{~kg} / \mathrm{s}\) is to be heated by ethylene glycol $\left(c_{p}=2500 \mathrm{~J} / \mathrm{kg} \cdot \mathrm{K}\right)\( at \)60^{\circ} \mathrm{C}$ in a thin-walled double-pipe parallel-flow heat exchanger. The temperature difference between the two fluids is \(15^{\circ} \mathrm{C}\) at the outlet of the heat exchanger. If the overall heat transfer coefficient is $240 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}\( and the heat transfer surface area is \)3.2 \mathrm{~m}^{2}$, determine \((a)\) the rate of heat transfer, \((b)\) the outlet temperature of the glycerin, and \((c)\) the mass flow rate of the ethylene glycol.

Short Answer

Expert verified
Question: Determine the rate of heat transfer (a), the outlet temperature of glycerin (b), and the mass flow rate of ethylene glycol (c) in a parallel-flow heat exchanger given the properties and flow rates of glycerin and ethylene glycol. Answer: (a) The rate of heat transfer is 18932.16 W. (b) The outlet temperature of glycerin is 43.14°C. (c) The mass flow rate of ethylene glycol is 0.381 kg/s.

Step by step solution

01

Overall heat transfer equation

For a heat exchanger, the overall heat transfer is given by: \(Q = U \cdot A \cdot \Delta T_{lm}\) Where: \(Q\) is the rate of heat transfer, \(U\) is the overall heat transfer coefficient, \(A\) is the heat transfer surface area, \(\Delta T_{lm}\) is the logarithmic mean temperature difference. Now, we are given \(U = 240 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}\) and \(A = 3.2 \mathrm{~m}^{2}\). We need to find \(\Delta T_{lm}\) to calculate the rate of heat transfer \((a)\).
02

Calculate logarithmic mean temperature difference

Since it's a parallel-flow heat exchanger, we have: \(\Delta T_{1} = T_{h1} - T_{c1} = 60 - 20 = 40^{\circ} \mathrm{C}\) \(\Delta T_{2} = T_{h2} - T_{c2}\) From the problem statement, \(T_{h2} - T_{c2} = 15^{\circ} \mathrm{C}\). Now using the formula for logarithmic mean temperature difference: \(\Delta T_{lm} = \frac{\Delta T_{1} - \Delta T_{2}}{ln(\frac{\Delta T_{1}}{\Delta T_{2}})}\) \(\Delta T_{lm} = \frac{40 - 15}{ln(\frac{40}{15})} = 24.71^{\circ} \mathrm{C}\)
03

Calculate the rate of heat transfer (a)

Now that we have the logarithmic mean temperature difference, we can find the heat transfer rate: \(Q = U \cdot A \cdot \Delta T_{lm}\) \(Q = 240 \cdot 3.2 \cdot 24.71 = 18932.16 \mathrm{~W}\)
04

Calculate the outlet temperature of glycerin (b)

We are given the mass flow rate of glycerin, \(m_{c} = 0.5 \mathrm{~kg} / \mathrm{s}\) and its specific heat capacity, \(c_{p} = 2400 \mathrm{~J} / \mathrm{kg} \cdot \mathrm{K}\). We can now find the outlet temperature of glycerin using the equation: \(Q = m_{c} \cdot c_{p} \cdot (T_{c2} - T_{c1})\) Solving for \(T_{c2}\): \(T_{c2} = \frac{Q}{m_{c} \cdot c_{p}} + T_{c1} = \frac{18932.16}{0.5 \cdot 2400} + 20 = 43.14^{\circ} \mathrm{C}\)
05

Calculate the mass flow rate of ethylene glycol (c)

We are given the specific heat capacity of ethylene glycol, \(c_{p} = 2500 \mathrm{~J} / \mathrm{kg} \cdot \mathrm{K}\). We can now find the mass flow rate of ethylene glycol, \(m_{h}\), using the equation: \(Q = m_{h} \cdot c_{p} \cdot (T_{h1} - T_{h2})\) First, we find \(T_{h2}\) using the relationship: \(T_{h2} = T_{c2} + 15 = 43.14 + 15 = 58.14^{\circ} \mathrm{C}\) Now, solving for \(m_{h}\): \(m_{h} = \frac{Q}{c_{p} \cdot (T_{h1} - T_{h2})} = \frac{18932.16}{2500 \cdot (60 - 58.14)} = 0.381 \mathrm{~kg} / \mathrm{s}\) In conclusion, we have: (a) The rate of heat transfer is \(18932.16 \mathrm{~W}\). (b) The outlet temperature of the glycerin is \(43.14^{\circ} \mathrm{C}\). (c) The mass flow rate of the ethylene glycol is \(0.381 \mathrm{~kg} / \mathrm{s}\).

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Most popular questions from this chapter

A shell-and-tube (two shell passes) heat exchanger is to heat $0.5 \mathrm{~kg} / \mathrm{s}\( of water \)\left(c_{p}=4200 \mathrm{~J} / \mathrm{kg} \cdot \mathrm{K}\right)$ by geothermal brine flowing through the shell passes. The heated water is then fed into commercial warewashing equipment. The National Sanitation Foundation (NSF) standard for commercial warewashing equipment (ANSI/NSF 3) requires that the final rinse water temperature be between 82 and \(90^{\circ} \mathrm{C}\). The geothermal brine enters and exits the heat exchanger at 98 and \(90^{\circ} \mathrm{C}\), respectively. The water flows through a thin-walled tube inside the shell passes. The tube diameter is \(25 \mathrm{~mm}\), and the tube length per pass is 4 \(\mathrm{m}\). The corresponding convection heat transfer coefficients on the outer and inner tube surfaces are 450 and $2700 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}$, respectively. The estimated fouling factor caused by the accumulation of deposit from the geothermal brine is \(0.0002\) \(\mathrm{m}^{2} \cdot \mathrm{K} / \mathrm{W}\). If the water enters the heat exchanger at \(20^{\circ} \mathrm{C}\), determine the number of tube passes required inside each shell pass to heat the water to \(86^{\circ} \mathrm{C}\) so that it complies with the ANSI/ NSF 3 standard.

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.

A performance test is being conducted on a doublepipe counterflow heat exchanger that carries engine oil and water at a flow rate of $2.5 \mathrm{~kg} / \mathrm{s}\( and \)1.75 \mathrm{~kg} / \mathrm{s}$, respectively. Since the heat exchanger has been in service for a long time, it is suspected that fouling might have developed inside the heat exchanger that could affect the overall heat transfer coefficient. The test to be carried out is such that, for a designed value of the overall heat transfer coefficient of $450 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}\( and a surface area of \)7.5 \mathrm{~m}^{2}\(, the oil must be heated from \)25^{\circ} \mathrm{C}$ to \(55^{\circ} \mathrm{C}\) by passing hot water at $100^{\circ} \mathrm{C}\left(c_{p}=4206 \mathrm{~J} / \mathrm{kg} \cdot \mathrm{K}\right)$ at the flow rates mentioned above. Determine if the fouling has affected the overall heat transfer coefficient. If yes, then what is the magnitude of the fouling resistance?

Hot water coming from the engine is to be cooled by ambient air in a car radiator. The aluminum tubes in which the water flows have a diameter of $4 \mathrm{~cm}$ and negligible thickness. Fins are attached on the outer surface of the tubes in order to increase the heat transfer surface area on the air side. The heat transfer coefficients on the inner and outer surfaces are 2000 and \(150 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}\), respectively. If the effective surface area on the finned side is 12 times the inner surface area, the overall heat transfer coefficient of this heat exchanger based on the inner surface area is (a) \(760 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}\) (b) \(832 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}\) (c) \(947 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}\) (d) \(1075 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}\) (e) \(1210 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}\)

Consider two double-pipe counterflow heat exchangers that are identical except that one is twice as long as the other one. Which heat exchanger is more likely to have a higher effectiveness?

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