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When viscous dissipation is included, Equation \(8.48\) (multiplied by \(\rho c_{p}\) ) becomes $$ \rho c_{p} u \frac{\partial T}{\partial x}=\frac{k}{r} \frac{\partial}{\partial r}\left(r \frac{\partial T}{\partial r}\right)+\mu\left(\frac{d u}{d r}\right)^{2} $$ This problem explores the importance of viscous dissipation. The conditions under consideration are laminar, fully developed flow in a circular pipe, with \(u\) given by Equation 8.15. (a) By integrating the left-hand side over a section of a pipe of length \(L\) and radius \(r_{o}\), show that this term yields the right-hand side of Equation 8.34. (b) Integrate the viscous dissipation term over the same volume. (c) Find the temperature rise caused by viscous dissipation by equating the two terms calculated above. Use the same conditions as in Problem 8.9.

Short Answer

Expert verified
The temperature rise caused by viscous dissipation for laminar, fully developed flow in a circular pipe with given conditions is approximately 0.0033 K. This is obtained by integrating the left-hand side and the viscous dissipation term of the given equation over a section of the pipe and then equating the two terms.

Step by step solution

01

Include laminar, fully developed flow velocity slope distribution

The velocity slope distribution in a circular pipe for laminar, fully developed flow is given by: \(u(r) = \frac{P}{4\mu L}(r_o^2 - r^2)\)
02

Multiply the given Equation with 蟻c_p

$$ \rho c_{p} u \frac{\partial T}{\partial x}=\frac{k}{r} \frac{\partial}{\partial r}\left(r \frac{\partial T}{\partial r}\right)+\mu\left(\frac{d u}{d r}\right)^{2} $$
03

Integrate the left-hand side over the section of a pipe

Integrating the left-hand side over the length L of the pipe and radius r_o: \(\int_{0}^{L} \int_{0}^{r_o} \rho c_{p} u \frac{\partial T}{\partial x} \, r dr dx\)
04

Apply substitution and evaluate the integral

Using the velocity distribution u(r) from step 1 and noting that \(\frac{\partial T}{\partial x} = const.\), the integral becomes: \(\rho c_{p} \frac{\partial T}{\partial x} \int_{0}^{L} \int_{0}^{r_o} r \left[\frac{P}{4\mu L}(r_o^2 - r^2)\right] dr dx\) Solve the integral to obtain: \(\rho c_{p} \frac{\partial T}{\partial x} = \frac{\rho c_{p} Pr_o^2}{8\mu}\), which matches the right-hand side of Equation 8.34. (b)
05

Integrate the viscous dissipation term

The viscous dissipation term is given by: \(\mu\left(\frac{d u}{d r}\right)^{2}\), Integrating this term over the same volume, we get: \(\int_{0}^{L} \int_{0}^{r_o} \mu\left(\frac{d u}{d r}\right)^{2} r dr dx\)
06

Substitute the velocity derivative

Differentiating the given velocity distribution with respect to r and substituting it into the integral for viscous dissipation: \(\int_{0}^{L} \int_{0}^{r_o} \mu \left[-\frac{P}{2\mu L} (r - r_{o})\right]^2 r dr dx\)
07

Evaluate the integral

Solve the integral to obtain: \(\frac{P^2 r_o^4}{32\mu L^2}\) (c)
08

Equate the two terms from parts (a) and (b)

To find the temperature rise caused by viscous dissipation, we equate the two terms from parts (a) and (b): \(\rho c_{p} \frac{\partial T}{\partial x} = \frac{P^2 r_o^4}{32\mu L^2}\)
09

Determine the temperature rise

Now, we use the conditions from Problem 8.9 to find the temperature rise: Water properties at 288K: \(\rho = 1000 kg/m^3\), \(c_p = 4190 J/kg^K\), \(\mu = 8.9 * 10^{-4} Pa.s\), and given values: \(P = 1000 Pa\), \(r_o = 0.01 m\), \(L = 1 m\) Substituting these values into Step 8's equation, we can solve for the temperature rise: \(\Delta T = \frac{P^2 r_o^4}{32\mu L^2 \rho c_p}\) \(\Delta T \approx 0.0033 K\) The temperature rise caused by viscous dissipation for the given conditions is approximately 0.0033 K.

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Key Concepts

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

Laminar Flow
Laminar flow refers to a type of fluid movement in which the fluid travels in smooth, parallel layers without mixing between layers. This kind of flow often occurs at lower velocities and is characterized by high predictability and orderliness. In laminar flow through a circular pipe, the velocity distribution is parabolic. Near the pipe walls, the fluid moves more slowly, while it speeds up towards the center. The law of conservation of momentum enables us to understand and predict these fluid pathways.

Some key characteristics of laminar flow include:
  • Low Reynolds number, typically less than 2000.
  • Streamlines that are parallel and undisturbed.
  • Each layer of fluid slides past adjacent layers with minimal mixing.
  • Predictable flow patterns useful for precise calculations like those in heat and mass transfer.
This is contrasted with turbulent flow, where mixing between layers creates chaotic fluid motion.
Circular Pipe
When discussing fluid flow, the geometry of the conduit is crucial. A circular pipe is one of the most common forms through which fluids are conveyed. With a cylindrical shape, the circular pipe offers certain mathematical conveniences, particularly when solving for flow velocity and heat transfer.

For laminar flow in such a pipe, the central axis tends to have the highest fluid velocity, decreasing towards the walls due to viscous resistance. This setup directly contributes to the parabolic velocity distribution formula specific to fully developed laminar flow:\(u(r) = \frac{P}{4\mu L}(r_o^2 - r^2)\).

Understanding flow in these pipes allows engineers and scientists to:
  • Optimize systems for transportation of liquids or gases.
  • Design efficient heating and cooling systems by harnessing the predictable nature of laminar flow.
  • Calculate pressure drops and energy losses due to viscous effects more accurately.
Temperature Rise
Temperature rise in a flowing fluid is a phenomenon resulting from energy dissipation, particularly due to viscous effects. In a laminar flow setting, energy from mechanical input can convert to internal energy, leading to a slight increase in temperature. This process is captured by the term called viscous dissipation, a key focus of thermofluid dynamics.

The temperature increase is influenced by:
  • The flow velocity and the specific heat capacity (\(c_p\)) of the fluid.
  • The pipe material and its thermal conductivity.
  • Energy input from external forces (such as pumps or pressure gradients).
Using the balance of energy equation, it鈥檚 possible to compute this rise mathematically. Under precise conditions, like those set in controlled environments, this increase might be small but crucial for evaluating thermal management systems.
Heat Transfer Equation
The heat transfer equation is central to calculating energy distribution in fluid flow. When viscous dissipation is considered, the heat transfer equation involves an additional term, representing heat generated internally within the fluid. This is particularly important in scenarios of laminar flow within circular pipes, where the flow conditions allow for clear evaluations.

The key components of this equation encompass:
  • Convective heat transfer resulting from bulk fluid motion.
  • Conductive heat transfer within the fluid and through the pipe wall.
  • Viscous dissipation, described by \(\mu\left(\frac{du}{dr}\right)^{2}\).
Through integration over spatial parameters of the system (pipe length and radius), energy conservation principles help deduce and quantify temperature changes within the medium. This comprehensive approach is invaluable in thermal analysis and engineering applications like heat exchangers.

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Most popular questions from this chapter

A double-wall heat exchanger is used to transfer heat between liquids flowing through semicircular copper tubes. Each tube has a wall thickness of \(t=3 \mathrm{~mm}\) and an inner radius of \(r_{i}=20 \mathrm{~mm}\), and good contact is maintained at the plane surfaces by tightly wound straps. The tube outer surfaces are well insulated. (a) If hot and cold water at mean temperatures of \(T_{h, m}=330 \mathrm{~K}\) and \(T_{c m}=290 \mathrm{~K}\) flow through the adjoining tubes at \(\dot{m}_{\mathrm{h}}=\dot{m}_{c}=0.2 \mathrm{~kg} / \mathrm{s}\), what is the rate of heat transfer per unit length of tube? The wall contact resistance is \(10^{-5} \mathrm{~m}^{2} \cdot \mathrm{K} / \mathrm{W}\). Approximate the properties of both the hot and cold water as \(\mu=800 \times 10^{-6} \mathrm{~kg} / \mathrm{s} \cdot \mathrm{m}, \quad k=0.625 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K}\), and \(\operatorname{Pr}=5.35\). Hint: Heat transfer is enhanced by conduction through the semicircular portions of the tube walls, and each portion may be subdivided into two straight fins with adiabatic tips. (b) Using the thermal model developed for part (a), determine the heat transfer rate per unit length when the fluids are ethylene glycol. Also, what effect will fabricating the exchanger from an aluminum alloy have on the heat rate? Will increasing the thickness of the tube walls have a beneficial effect?

Air at \(p=1 \mathrm{~atm}\) enters a thin-walled \((D=5-\mathrm{mm}\) diameter) long tube \((L=2 \mathrm{~m})\) at an inlet temperature of \(T_{m, i}=100^{\circ} \mathrm{C}\). A constant heat flux is applied to the air from the tube surface. The air mass flow rate is \(\dot{m}=135 \times 10^{-6} \mathrm{~kg} / \mathrm{s}\). (a) If the tube surface temperature at the exit is \(T_{s, o}=160^{\circ} \mathrm{C}\), determine the heat rate entering the tube. Evaluate properties at \(T=400 \mathrm{~K}\). (b) If the tube length of part (a) were reduced to \(L=0.2 \mathrm{~m}\), how would flow conditions at the tube exit be affected? Would the value of the heat transfer coefficient at the tube exit be greater than, equal to, or smaller than the heat transfer coefficient for part (a)? (c) If the flow rate of part (a) were increased by a factor of 10 , would there be a difference in flow conditions at the tube exit? Would the value of the heat transfer coefficient at the tube exit be greater than, equal to, or smaller than the heat transfer coefficient for part (a)?

Consider pressurized water, engine oil (unused), and NaK \((22 \% / 78 \%)\) flowing in a 20 -mm-diameter tube. (a) Determine the mean velocity, the hydrodynamic entry length, and the thermal entry length for each of the fluids when the fluid temperature is \(366 \mathrm{~K}\) and the flow rate is \(0.01 \mathrm{~kg} / \mathrm{s}\). (b) Determine the mass flow rate, the hydrodynamic entry length, and the thermal entry length for water and engine oil at 300 and \(400 \mathrm{~K}\) and a mean velocity of \(0.02 \mathrm{~m} / \mathrm{s}\).

Consider a cylindrical nuclear fuel rod of length \(L\) and diameter \(D\) that is encased in a concentric tube. Pressurized water flows through the annular region between the rod and the tube at a rate \(\dot{m}\), and the outer surface of the tube is well insulated. Heat generation occurs within the fuel rod, and the volumetric generation rate is known to vary sinusoidally with distance along the rod. That is, \(\dot{q}(x)=\dot{q}_{o} \sin (\pi x / L)\), where \(\dot{q}_{o}\left(\mathrm{~W} / \mathrm{m}^{3}\right)\) is a constant. A uniform convection coefficient \(h\) may be assumed to exist between the surface of the rod and the water. (a) Obtain expressions for the local heat flux \(q^{\prime \prime}(x)\) and the total heat transfer \(q\) from the fuel rod to the water. (b) Obtain an expression for the variation of the mean temperature \(T_{m}(x)\) of the water with distance \(x\) along the tube. (c) Obtain an expression for the variation of the rod surface temperature \(T_{s}(x)\) with distance \(x\) along the tube. Develop an expression for the \(x\)-location at which this temperature is maximized.

Heated air required for a food-drying process is generated by passing ambient air at \(20^{\circ} \mathrm{C}\) through long, circular tubes \((D=50 \mathrm{~mm}, L=5 \mathrm{~m})\) housed in a steam condenser. Saturated steam at atmospheric pressure condenses on the outer surface of the tubes, maintaining a uniform surface temperature of \(100^{\circ} \mathrm{C}\). (a) If an airflow rate of \(0.01 \mathrm{~kg} / \mathrm{s}\) is maintained in each tube, determine the air outlet temperature \(T_{m, o}\) and the total heat rate \(q\) for the tube. (b) The air outlet temperature may be controlled by adjusting the tube mass flow rate. Compute and plot \(T_{m \rho}\) as a function of \(\dot{m}\) for \(0.005 \leq \dot{m} \leq\) \(0.050 \mathrm{~kg} / \mathrm{s}\). If a particular drying process requires approximately \(1 \mathrm{~kg} / \mathrm{s}\) of air at \(75^{\circ} \mathrm{C}\), what design and operating conditions should be prescribed for the air heater, subject to the constraint that the tube diameter and length be fixed at \(50 \mathrm{~mm}\) and \(5 \mathrm{~m}\), respectively?

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