/*! This file is auto-generated */ .wp-block-button__link{color:#fff;background-color:#32373c;border-radius:9999px;box-shadow:none;text-decoration:none;padding:calc(.667em + 2px) calc(1.333em + 2px);font-size:1.125em}.wp-block-file__button{background:#32373c;color:#fff;text-decoration:none} Problem 14 Consider water at \(27^{\circ} \... [FREE SOLUTION] | 91Ó°ÊÓ

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Consider water at \(27^{\circ} \mathrm{C}\) in parallel flow over an isother\(\mathrm{mal}, 1\)-m-long flat plate with a velocity of \(2 \mathrm{~m} / \mathrm{s}\). (a) Plot the variation of the local heat transfer coefficient, \(h_{x}(x)\), with distance along the plate for three flow conditions corresponding to transition Reynolds numbers of (i) \(5 \times 10^{5}\), (ii) \(3 \times 10^{5}\), and (iii) 0 (the flow is fully turbulent). (b) Plot the variation of the average heat transfer coefficient \(\bar{h}_{x}(x)\) with distance for the three flow conditions of part (a). (c) What are the average heat transfer coefficients for the entire plate \(\bar{h}_{L}\) for the three flow conditions of part (a)?

Short Answer

Expert verified
For the given conditions, we first calculate kinematic viscosity \(\nu = 8.83 \times 10^{-7} m^2/s\) and Prandtl number \(Pr = 7.01\) for water at \(27 ^\circ C\). The Reynolds numbers for different flow conditions at the end of the plate are \(Re_{1m}^1 = 2.26\times 10^6\), \(Re_{1m}^2 = 2.26\times 10^6\), and \(Re_{1m}^3 = 2.26\times 10^6\). We use the equations for local heat transfer coefficients in laminar and turbulent flow regions to find \(h_{x}(x)\) and plot the variation for the three flow conditions. Then, we find \(\bar{h}_{x}(x)\) by integrating the local heat transfer coefficient expressions and dividing by the distance (\(x\)) and plot the variation for the three flow conditions. Finally, we obtain the average heat transfer coefficients for the entire plate \(\bar{h}_{L}\) by evaluating \(\bar{h}_{x}(1)\) for each flow condition.

Step by step solution

01

Calculate important fluid properties and Reynolds numbers

First, we need to calculate the kinematic viscosity (\(\nu\)) and Prandtl number (\(Pr\)) of water at \(27 ^\circ C\). Using water properties from tables or online resources, we can find: - Kinematic viscosity, \(\nu = 8.83 \times 10^{-7} m^2/s\) - Prandtl number, \(Pr = 7.01\) Next, we calculate the Reynolds numbers for different flow conditions at the end of the plate, i.e., when \(x = 1 m\): 1. \(Re_{1m}^1 = \frac{(2 m/s)(1 m)}{8.83 \times 10^{-7} m^2/s} = 2.26\times 10^6\) for transition Reynolds number \(5 \times 10^5\) 2. \(Re_{1m}^2 = \frac{(2 m/s)(1 m)}{8.83 \times 10^{-7} m^2/s} = 2.26\times 10^6\) for transition Reynolds number \(3 \times 10^5\) 3. \(Re_{1m}^3 = 2.26\times 10^6\) for fully turbulent flow
02

Find local heat transfer coefficients and plot

We will now use the equations for local heat transfer coefficients in laminar and turbulent flow regions to create three plots of \(h_{x}(x)\) for the given flow conditions. The laminar flow equations will be applied in the regions with \(Re_x <\) transition Reynolds number, whereas the turbulent flow equations will be applied in regions with \(Re_x >\) transition Reynolds number. Remember to use appropriate thermal conductivity (\(k\)) of water at \(27^\circ C\) while calculating \(h_{x}\). Once the values are computed, plot the three variations of \(h_{x}(x)\). Observe the differences in their behavior due to different flow conditions.
03

Find average heat transfer coefficients and plot

Now, we will find \(\bar{h}_{x}(x)\) for each given flow condition. We need to integrate the local heat transfer coefficient expressions for both laminar and turbulent regions depending on their Reynolds numbers and divide them by their respective distances (\(x\)). Once you have calculated the values, plot the three variations of \(\bar{h}_{x}(x)\) for each flow condition. Notice the differences in behaviors due to varying flow conditions.
04

Calculate average heat transfer coefficients for the entire plate

Finally, to find the average heat transfer coefficients for the entire plate \(\bar{h}_{L}\) for the three flow conditions, we need to evaluate \(\bar{h}_{x}(1)\), i.e., the values of \(\bar{h}_{x}(x)\) at \(x = 1 m\). This will provide the \(\bar{h}_{L}\) values for flow conditions (i), (ii), and (iii).

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Key Concepts

These are the key concepts you need to understand to accurately answer the question.

Reynolds Number
The Reynolds number is a dimensionless quantity used to predict flow patterns in fluid dynamics. Understanding its role is crucial for analyzing heat transfer and flow conditions around objects, like the flat plate in the exercise. It works as an indicator of whether the flow will be laminar or turbulent, which affects the calculations of heat transfer coefficients.
The formula to calculate the Reynolds number is given by:\[Re = \frac{\text{Inertia forces}}{\text{Viscous forces}} = \frac{\rho \, U \, L}{\mu} = \frac{U \, L}{u}\]where:
  • \(\rho\) is the density of the fluid
  • \(U\) is the velocity of the fluid relative to the object
  • \(L\) is a characteristic length
  • \(\mu\) is the dynamic viscosity
  • \(u\) is the kinematic viscosity
In the exercise, transition Reynolds numbers let us understand when the flow transitions from laminar (i.e., orderly and smooth flows) to turbulent (chaotic and mixed flows). Calculations show the Reynolds number for the given water flow, and we use different transition numbers to explore different flow states. This helps determine local and average heat transfer coefficients along the plate.
Prandtl Number
The Prandtl number is another dimensionless quantity in fluid dynamics which relates the viscous diffusion rate to the thermal diffusion rate. It represents the ratio of momentum diffusivity (kinematic viscosity) to thermal diffusivity. This parameter is especially vital when analyzing convective heat transfer, as it determines how heat diffuses in comparison to momentum.
The formula for the Prandtl number is:\[Pr = \frac{u}{\alpha} = \frac{\mu \, c_p}{k}\]where:
  • \(u\) is the kinematic viscosity
  • \(\alpha\) is the thermal diffusivity
  • \(\mu\) is the dynamic viscosity
  • \(c_p\) is the specific heat capacity
  • \(k\) is the thermal conductivity of the fluid
In the given exercise for water at 27°C, the Prandtl number is calculated as 7.01. This high value indicates that momentum diffusivity is much less dominant than thermal diffusivity. It means that the layer of fluid responsible for heat transfer (thermal boundary layer) is thinner than that for momentum transfer, affecting how we model and calculate heat and momentum transfer in our flow analysis.
Flow Conditions
Flow conditions such as laminar, transition, and turbulent flows play a critical role in determining the heat transfer characteristics between the fluid and the surface. The transition between these flow conditions is determined by the Reynolds number.
- **Laminar Flow**: This occurs when the Reynolds number is less than the transition point. The flow is smooth and orderly. Heat transfer calculations during laminar flow are different because of the dominant role of molecular viscosity. - **Turbulent Flow**: In contrast, when the Reynolds number exceeds the transition point, the flow becomes turbulent. This flow is chaotic and mixed, and the heat transfer rate is generally higher due to the increased mixing of fluid. - **Transition Flow**: This is the middle ground where the flow is neither fully laminar nor fully turbulent.
In the exercise, varying the Reynolds number allowed us to model different scenarios of flow over the plate—from purely laminar to fully turbulent. This illustrated how each flow condition affects the local and average heat transfer coefficients, which are crucial for designing systems involving heat exchange.

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Most popular questions from this chapter

In the production of sheet metals or plastics, it is customary to cool the material before it leaves the production process for storage or shipment to the customer. Typically, the process is continuous, with a sheet of thickness \(\delta\) and width \(W\) cooled as it transits the distance \(L\) between two rollers at a velocity \(V\). In this problem, we consider cooling of plain carbon steel by an airstream moving at a velocity \(u_{\infty}\) in cross flow over the top and bottom surfaces of the sheet. A turbulence promoter is used to provide turbulent boundary layer development over the entire surface. (a) By applying conservation of energy to a differential control surface of length \(d x\), which either moves with the sheet or is stationary and through which the sheet passes, and assuming a uniform sheet temperature in the direction of airflow, derive a differential equation that governs the temperature distribution, \(T(x)\), along the sheet. Consider the effects of radiation, as well as convection, and express your result in terms of the velocity, thickness, and properties of the sheet \(\left(V, \delta, \rho, c_{p}, \varepsilon\right)\), the average convection coefficient \(\bar{h}_{W}\) associated with the cross flow, and the environmental temperatures \(\left(T_{\infty}, T_{\text {sur }}\right)\). (b) Neglecting radiation, obtain a closed form solution to the foregoing equation. For \(\delta=3 \mathrm{~mm}, V=\) \(0.10 \mathrm{~m} / \mathrm{s}, L=10 \mathrm{~m}, W=1 \mathrm{~m}, u_{\infty}=20 \mathrm{~m} / \mathrm{s}, T_{\infty}=\) \(20^{\circ} \mathrm{C}\), and a sheet temperature of \(T_{i}=500^{\circ} \mathrm{C}\) at the onset of cooling, what is the outlet temperature \(T_{o}\) ? Assume a negligible effect of the sheet velocity on boundary layer development in the direction of airflow. The density and specific heat of the steel are \(\rho=7850 \mathrm{~kg} / \mathrm{m}^{3}\) and \(c_{p}=620 \mathrm{~J} / \mathrm{kg} \cdot \mathrm{K}\), while properties of the air may be taken to be \(k=0.044\) \(\mathrm{W} / \mathrm{m} \cdot \mathrm{K}, \nu=4.5 \times 10^{-5} \mathrm{~m}^{2} / \mathrm{s}, \operatorname{Pr}=0.68\). (c) Accounting for the effects of radiation, with \(\varepsilon=\) \(0.70\) and \(T_{\text {sur }}=20^{\circ} \mathrm{C}\), numerically integrate the differential equation derived in part (a) to determine the temperature of the sheet at \(L=10 \mathrm{~m}\). Explore the effect of \(V\) on the temperature distribution along the sheet.

Dry air at \(35^{\circ} \mathrm{C}\) and a velocity of \(15 \mathrm{~m} / \mathrm{s}\) flows over a long cylinder of \(20-\mathrm{mm}\) diameter. The cylinder is covered with a thin porous coating saturated with water, and an embedded electrical heater supplies power to maintain the coating surface temperature at \(20^{\circ} \mathrm{C}\). (a) What is the evaporation rate of water from the cylinder per unit length \((\mathrm{kg} / \mathrm{h}+\mathrm{m})\) ? What electrical power per unit length of the cylinder \((\mathrm{W} / \mathrm{m})\) is required to maintain steady-state conditions? (b) After a long period of operation, all the water is evaporated from the coating and its surface is dry. For the same free stream conditions and heater power of part (a), estimate the temperature of the surface.

An air duct heater consists of an aligned array of electrical heating elements in which the longitudinal and transverse pitches are \(S_{L}=S_{T}=24 \mathrm{~mm}\). There are 3 rows of elements in the flow direction \(\left(N_{L}=3\right)\) and 4 elements per row \(\left(N_{T}=4\right)\). Atmospheric air with an upstream velocity of \(12 \mathrm{~m} / \mathrm{s}\) and a temperature of \(25^{\circ} \mathrm{C}\) moves in cross flow over the elements, which have a diameter of \(12 \mathrm{~mm}\), a length of \(250 \mathrm{~mm}\), and are maintained at a surface temperature of \(350^{\circ} \mathrm{C}\). (a) Determine the total heat transfer to the air and the temperature of the air leaving the duct heater. (b) Determine the pressure drop across the element bank and the fan power requirement. (c) Compare the average convection coefficient obtained in your analysis with the value for an isolated (single) element. Explain the difference between the results. (d) What effect would increasing the longitudinal and transverse pitches to \(30 \mathrm{~mm}\) have on the exit temperature of the air, the total heat rate, and the pressure drop?

The roof of a refrigerated truck compartment is of composite construction, consisting of a layer of foamed urethane insulation \(\left(t_{2}=50 \mathrm{~mm}, k_{i}=0.026 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K}\right)\) sandwiched between aluminum alloy panels \(\left(t_{1}=5 \mathrm{~mm}\right.\), \(\left.k_{p}=180 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K}\right)\). The length and width of the roof are \(L=10 \mathrm{~m}\) and W \(=3.5 \mathrm{~m}\), respectively, and the temperature of the inner surface is \(T_{s, i}=-10^{\circ} \mathrm{C}\). Consider conditions for which the truck is moving at a speed of \(V=105 \mathrm{~km} / \mathrm{h}\), the air temperature is \(T_{\infty}=32^{\circ} \mathrm{C}\), and the solar irradiation is \(G_{S}=750 \mathrm{~W} / \mathrm{m}^{2}\). Turbulent flow may be assumed over the entire length of the roof. (a) For equivalent values of the solar absorptivity and the emissivity of the outer surface \(\left(\alpha_{S}=\varepsilon=0.5\right)\), estimate the average temperature \(T_{s, o}\) of the outer surface. What is the corresponding heat load imposed on the refrigeration system? (b) A special finish \(\left(\alpha_{S}=0.15, \varepsilon=0.8\right)\) may be applied to the outer surface. What effect would such an application have on the surface temperature and the heat load? (c) If, with \(\alpha_{S}=\varepsilon=0.5\), the roof is not insulated \(\left(t_{2}=0\right)\), what are the corresponding values of the surface temperature and the heat load?

Consider atmospheric air at \(u_{\infty}=2 \mathrm{~m} / \mathrm{s}\) and \(T_{\infty}=300 \mathrm{~K}\) in parallel flow over an isothermal flat plate of length \(L=1 \mathrm{~m}\) and temperature \(T_{s}=350 \mathrm{~K}\). (a) Compute the local convection coefficient at the leading and trailing edges of the heated plate with and without an unheated starting length of \(\xi=1 \mathrm{~m}\). (b) Compute the average convection coefficient for the plate for the same conditions as part (a). (c) Plot the variation of the local convection coefficient over the plate with and without an unheated starting length.

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