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Fluid Mechanics: Fundamentals and Applications

Yunus Cengel

Chapter 10

APPROXIMATE SOLUTIONS OF THE NAVIER–STOKES EQUATION - all with Video Answers

Educators


Chapter Questions

Problem 1

Explain the difference between an "exact" solution of the Navier-Stokes equation (as discussed in Chap. 9) and an approximate solution (as discussed in this chapter).

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Problem 2

A box fan sits on the floor of a very large room (Fig. P10-2C). Label regions of the flow field that may be approximated as static. Label regions in which the irrotational approximation is likely to be appropriate. Label regions where the boundary layer approximation may be appropriate. Finally, label regions in which the full NavierStokes equation most likely needs to be solved (i.e., regions where no approximation is appropriate).

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Problem 3

Discuss how nondimensionalization of the NavierStokes equation is helpful in obtaining approximate solutions. Give an example.

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Problem 4

What is the most significant danger associated with an approximate solution of the Navier-Stokes equation? Give an example that is different than the ones given in this chapter.

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Problem 5

What criteria can you use to determine whether an approximation of the Navier-Stokes equation is appropriate or not? Explain.

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Problem 6

In the nondimensionalized incompressible NavierStokes equation (Eq. 10-6), there are four nondimensional parameters. Name each one, explain its physical significance (e.g., the ratio of pressure forces to viscous forces), and discuss what it means physically when the parameter is very small or very large.

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Problem 7

What is the most important criterion for use of the modified pressure $P^{\prime}$ rather than the thermodynamic pressure $P$ in a solution of the Navier-Stokes equation?

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Problem 8

Which nondimensional parameter in the nondimensionalized Navier-Stokes equation is eliminated by use of modified pressure instead of actual pressure? Explain.

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Problem 9

Consider flow of water through a small hole in the bottom of a large cylindrical tank (Fig. P10-9). The flow is laminar everywhere. Jet diameter $d$ is much smaller than tank diameter $D$, but $D$ is of the same order of magnitude as tank height $H$. Carrie reasons that she can use the fluid statics approximation everywhere in the tank except near the hole, but wants to validate this approximation mathematically. She lets the characteristic velocity scale in the tank be $V=V_{\text {tank }}$. The characteristic length scale is tank height $H$, the characteristic time is the time required to drain the tank $t_{\text {drain }}$, and the reference pressure difference is $\rho g H$ (pressure difference from the water surface to the bottom of the tank, assuming fluid statics). Substitute all these scales into the nondimensionalized incompressible Navier-Stokes equation (Eq. 10-6) and verify by order-of-magnitude analysis that for $d \ll D$, only the pressure and gravity terms remain. In particular, compare the order of magnitude of each term and each of the four nondimensional parameters $\mathrm{St}, \mathrm{Eu}, \mathrm{Fr}$, and Re . (Hint: $V_{\text {jet }} \sim \sqrt{g H}$.) Under what criteria is Carrie's approximation appropriate?

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Problem 10

Consider steady, incompressible, laminar, fully developed, planar Poiseuille flow between two parallel, horizontal plates (velocity and pressure profiles are shown in Fig. $\mathrm{P} 10-10)$. At some horizontal location $x=x_1$, the pressure varies linearly with vertical distance $z$, as sketched. Choose an appropriate datum plane $(z=0)$, sketch the profile of modified pressure all along the vertical slice, and shade in the region representing the hydrostatic pressure component. Discuss.

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Problem 11

Consider the planar Poiseuille flow of Prob. 10-10. Discuss how modified pressure varies with downstream distance $x$. In other words, does modified pressure increase, stay the same, or decrease with $x$ ? If $P^{\prime}$ increases or decreases with $x$, how does it do so (e.g., linearly, quadratically, exponentially)? Use a sketch to illustrate your answer.

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Problem 12

In Chap. 9 (Example 9-15), we generated an "exact" solution of the Navier-Stokes equation for fully developed Couette flow between two horizontal flat plates (Fig. P10-12), with gravity acting in the negative $z$-direction (into the page of Fig. P10-12). We used the actual pressure in that example. Repeat the solution for the $x$-component of velocity $u$ and pressure $P$, but use the modified pressure in your equations. The pressure is $P_0$ at $z=0$. Show that you get the same result as previously. Discuss. Answers: $u=V y / h$, $P=P_0-\rho g z$

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Problem 13

Write out the three components of the Navier-Stokes equation in Cartesian coordinates in terms of modified pressure. Insert the definition of modified pressure and show that the $x$-, $y$-, and $z$-components are identical to those in terms of regular pressure. What is the advantage of using modified pressure?

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Problem 14

A flow field is simulated by a computational fluid dynamics code that uses the modified pressure in its calculations. A profile of modified pressure along a vertical slice through the flow is sketched in Fig. P10-14. The actual pressure at a point midway through the slice is known, as indicated on Fig. P10-14. Sketch the profile of actual pressure all along the vertical slice. Discuss.

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Problem 15

In Example 9-18 we solved the Navier-Stokes equation for steady, fully developed, laminar flow in a round pipe (Poiseuille flow), neglecting gravity. Now, add back the effect of gravity by re-solving that same problem, but use modified pressure $P^{\prime}$ instead of actual pressure $P$. Specifically, calculate the actual pressure field and the velocity field. Assume the pipe is horizontal, and let the datum plane $z=0$ be at some arbitrary distance under the pipe. Is the actual pressure at the top of the pipe greater than, equal to, or less than that at the bottom of the pipe? Discuss.

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Problem 16

Write a one-word description of each of the five terms in the incompressible Navier-Stokes equation,

$$
\rho \frac{\partial \vec{V}}{\partial t}+\rho(\vec{V} \cdot \vec{\nabla}) \vec{V}=\underset{\nabla}{-\vec{\nabla} P}+\rho \vec{g}+\mu \nabla^2 \vec{V}
$$

When the creeping flow approximation is made, only two of the five terms remain. Which two terms remain, and why is this significant?

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Problem 17

17 The viscosity of clover honey is listed as a function of temperature in Table P10-17. The specific gravity of the honey is about 1.42 and is not a strong function of temperature. The honey is squeezed through a small hole of diameter $D=4.0 \mathrm{~mm}$ in the lid of an inverted honey jar. The room and the honey are at $T=20^{\circ} \mathrm{C}$. Estimate the maximum speed of the honey through the hole such that the flow can be approximated as creeping flow. (Assume that Re must be less than 0.1 for the creeping flow approximation to be appropriate.) Repeat your calculation if the temperature is $40^{\circ} \mathrm{C}$. Discuss.
$$
\begin{array}{cc}
\hline T,{ }^{\circ} \mathrm{C} & \mu, \text { poise }{ }^* \\
\hline 14 & 600 \\
20 & 190 \\
30 & 65 \\
40 & 20 \\
50 & 10 \\
70 & 3 \\
\hline
\end{array}
$$

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Problem 18

For each case, calculate an appropriate Reynolds number and indicate whether the flow can be approximated by the creeping flow equations. (a) A microorganism of diameter $5.0 \mu \mathrm{~m}$ swims in room temperature water at a speed of $0.2 \mathrm{~mm} / \mathrm{s}$. (b) Engine oil at $140^{\circ} \mathrm{C}$ flows in the small gap of a lubricated automobile bearing. The gap is 0.0012 mm thick, and the characteristic velocity is $20.0 \mathrm{~m} / \mathrm{s}$. (c) A fog droplet of diameter $10 \mu \mathrm{~m}$ falls through $30^{\circ} \mathrm{C}$ air at a speed of $3.0 \mathrm{~mm} / \mathrm{s}$.

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Problem 19

Estimate the speed and Reynolds number of the sperm shown in Fig. 10-10. Is this microorganism swimming under creeping flow conditions? Assume it is swimming in room-temperature water.

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Problem 20

A good swimmer can swim 100 m in about a minute. If a swimmer's body is 1.8 m long, how many body lengths does he swim per second? Repeat the calculation for the sperm of Fig. 10-10. In other words, how many body lengths does the sperm swim per second? Use the sperm's whole body length, not just that of his head, for the calculation. Compare the two results and discuss.

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Problem 21

A drop of water in a rain cloud has diameter $D$ $=30 \mu \mathrm{~m}$ (Fig. P10-21). The air temperature is $25^{\circ} \mathrm{C}$, and its pressure is standard atmospheric pressure. How fast does the air have to move vertically so that the drop will remain suspended in the air?

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Problem 22

Discuss why fluid density does not influence the aerodynamic drag on a particle moving in the creeping flow regime.

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Problem 23

A slipper-pad bearing (Fig. P10-23) is often encountered in lubrication problems. Oil flows between two blocks; the upper one is stationary, and the lower one is moving in this case. The drawing is not to scale; in actuality, $h$ $\ll L$. The thin gap between the blocks converges with increasing $x$. Specifically, gap height $h$ decreases linearly from $h_0$ at $x=0$ to $h_L$ at $x=L$. Typically, the gap height length scale $h_0$ is much smaller than the axial length scale $L$. This problem is more complicated than simple Couette flow between parallel plates because of the changing gap height. In particular, axial velocity component $u$ is a function of both $x$ and $y$, and pressure $P$ varies nonlinearly from $P=P_0$ at $x$ $=0$ to $P=P_L$ at $x=L$. ( $\partial P / \partial x$ is not constant). Gravity forces are negligible in this flow field, which we approximate as two-dimensional, steady, and laminar. In fact, since $h$ is so small and oil is so viscous, the creeping flow approximations

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Problem 24

Consider the slipper-pad bearing of Prob. 10-23. (a) Generate a characteristic scale for $v$, the $y$-component of velocity. (b) Perform an order-of-magnitude analysis to compare the inertial terms to the pressure and viscous terms in the $x$-momentum equation. Show that when the gap is small $\left(h_0 \ll L\right)$ and the Reynolds number is small $\left(\operatorname{Re}=\rho V h_0 / \mu\right.$ $\ll 1$ ), the creeping flow approximation is appropriate. (c) Show that when $h_0 \ll L$, the creeping flow equations may still be appropriate even if the Reynolds number ( $\operatorname{Re}$ $=\rho V h_0 / \mu$ ) is not less than 1. Explain.

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Problem 25

Consider again the slipper-pad bearing of Prob. 10-23. Perform an order-of-magnitude analysis on the $y$ momentum equation, and write the final form of the $y$ momentum equation. (Hint: You will need the results of Probs. 10-23 and 10-24.) What can you say about pressure gradient $\partial P / \partial y$ ?

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Problem 26

Consider again the slipper-pad bearing of Prob. 10-23. (a) List appropriate boundary conditions on $u$. (b) Solve the creeping flow approximation of the $x$-momentum equation to obtain an expression for $u$ as a function of $y$ (and indirectly as a function of $x$ through $h$ and $d P / d x$, which are functions of $x$ ). You may assume that $P$ is not a function of $y$. Your final expression should be written as $u(x, y)=f(y, h$, $d P / d x, V$, and $\mu$ ). Name the two distinct components of the velocity profile in your result. (c) Nondimensionalize your expression for $u$ using these appropriate scales: $x^*=x / L, y^*$ $=y / h_0, h^*=h / h_0, u^*=u / V$, and $P^*=\left(P-P_0\right) h_0{ }^2 / \mu V L$.

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Problem 27

Consider the slipper-pad bearing of Fig. P10-27. The drawing is not to scale; in actuality, $h \ll L$. This case differs from that of Prob. $10-23$ in that $h(x)$ is not linear; rather $h$ is some known, arbitrary function of $x$. Write an expression for axial velocity component $u$ as a function of $y$, $h, d P / d x, V$, and $\mu$. Discuss any differences between this result and that of Prob. 10-26.

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Problem 28

For the slipper-pad bearing of Prob. 10-23, use the continuity equation, appropriate boundary conditions, and the one-dimensional Leibnitz theorem (see Chap. 4) to show that $\frac{d}{d x} \int_0^h u d y=0$.

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Problem 29

Combine the results of Probs. 10-26 and 10-28 to show that for a two-dimensional slipper-pad bearing, pressure gradient $d P / d x$ is related to gap height $h$ by $\frac{d}{d x}\left(h^3 \frac{d P}{d x}\right)$ $=6 \mu U \frac{d h}{d x}$. This is the steady, two-dimensional form of the more general Reynolds equation for lubrication (Panton, 1996).

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Problem 30

Consider flow through a two-dimensional slipper-pad bearing with linearly decreasing gap height from $h_0$ to $h_L$ (Fig. P10-23), namely, $h=h_0+\alpha x$, where $\alpha$ is the nondimensional convergence of the gap, $\alpha=\left(h_L-h_0\right) / L$. We note that $\tan \alpha \equiv \alpha$ for very small values of $\alpha$. Thus, $\alpha$ is approximately the angle of convergence of the upper plate in Fig. P10-23 ( $\alpha$ is negative for this case). Assume that the oil is exposed to atmospheric pressure at both ends of the slipper-pad, so that $P$ $=P_0=P_{\text {atm }}$ at $x=0$ and $P=P_L=P_{\text {atin }}$ at $x=L$. Integrate the Reynolds equation (Prob. 10-29) for this slipper-pad bearing to generate an expression for $P$ as a function of $x$.

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Problem 31

A slipper-pad bearing with linearly decreasing
gap height (Fig. P10-23) is being designed
for an amusement park ride. Its dimensions are $h_0=1 / 1000$ in $\left(2.54 \times 10^{-5} \mathrm{~m}\right), h_L=1 / 2000$ in $\left(1.27 \times 10^{-5} \mathrm{~m}\right)$, and $L$ $=1.0 \mathrm{in}(0.0254 \mathrm{~m})$. The lower plate moves at speed $V$ $=10.0 \mathrm{ft} / \mathrm{s}(3.048 \mathrm{~m} / \mathrm{s})$ relative to the upper plate. The oil is engine oil at $40^{\circ} \mathrm{C}$. Both ends of the slipper-pad are exposed to atmospheric pressure, as in Prob. 10-30. (a) Calculate the convergence $\alpha$, and verify that $\tan \alpha \equiv \alpha$ for this case. (b) Calculate the gage pressure halfway along the slipper-pad (at $x$ $=0.5 \mathrm{in})$. Comment on the magnitude of the gage pressure. (c) Plot $P^*$ as a function of $x^*$, where $x^*=x / L$ and $P^*=(P$ - $\left.P_{\text {atm }}\right) h_0{ }^2 / \mu V L$. (d) Approximately how many pounds of weight (load) can this slipper-pad bearing support if it is $b$ $=6.0$ in deep (into the page of Fig. P10-23)?

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Problem 32

Discuss what happens when the oil temperature increases significantly as the slipper-pad bearing of Prob. $10-31 \mathrm{E}$ is subjected to constant use at the amusement park. In particular, would the load-carrying capacity increase or decrease? Why?

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Problem 33

Is the slipper-pad flow of Prob. 10-31E in the creeping flow regime? Discuss. Are the results reasonable?

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Problem 34

We saw in Prob. 10-31E that a slipper-pad bearing can support a large load. If the load were to increase, the gap height would decrease, thereby increasing the pressure in the gap. In this sense, the slipper-pad bearing is "self-adjusting" to varying loads. If the load increases by a factor of 2, calculate how much the gap height decreases. Specifically, calculate the new value of $h_0$ and the percentage change. Assume that the slope of the upper plate and all other parameters and dimensions stay the same as those in Prob. 10-31E.

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Problem 35

Estimate the speed at which you would need to swim in room temperature water to be in the creeping flow regime. (An order-of-magnitude estimate will suffice.) Discuss.

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Problem 36

In what way is the Euler equation an approximation of the Navier-Stokes equation? Where in a flow field is the Euler equation an appropriate approximation?

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Problem 37

What is the main difference between the steady, incompressible Bernoulli equation for irrotational regions of flow, and the steady incompressible Bernoulli equation for rotational but inviscid regions of flow?

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Problem 38

In the derivation of the Bernoulli equation for regions of inviscid flow, we use the vector identity

$$
(\vec{V} \cdot \vec{\nabla}) \vec{V}=\vec{\nabla}\left(\frac{V^2}{2}\right)-\vec{V} \times(\vec{\nabla} \times \vec{V})
$$

Show that this vector identity is satisfied for the case of velocity vector $\vec{V}$ in Cartesian coordinates, i.e., $\vec{v}=u \vec{i}+v \vec{j}$ $+w \vec{k}$. For full credit, expand each term as far as possible and show all your work.

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Problem 39

In the derivation of the Bernoulli equation for regions of inviscid flow, we rewrite the steady, incompressible Euler equation into a form showing that the gradient of three scalar terms is equal to the velocity vector crossed with the vorticity vector, noting that $z$ is vertically upward

$$
\vec{\nabla}\left(\frac{P}{\rho}+\frac{V^2}{2}+g z\right)=\vec{V} \times \vec{\zeta}
$$

We then employ some arguments about the direction of the gradient vector and the direction of the cross product of two vectors to show that the sum of the three scalar terms must be constant along a streamline. In this problem you will use a different approach to achieve the same result. Namely, take the dot product of both sides of the Euler equation with velocity vector $\vec{V}$ and apply some fundamental rules about the dot product of two vectors. Sketches may be helpful.

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Problem 40

Write out the components of the Euler equation as far as possible in Cartesian coordinates $(x, y, z)$ and $(u, v, w)$. Assume gravity acts in some arbitrary direction.

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Problem 41

Write out the components of the Euler equation as far as possible in cylindrical coordinates $(r, \theta, z)$ and $\left(u_r, u_\theta\right.$, $u_z$ ). Assume gravity acts in some arbitrary direction.

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Problem 42

Water at $T=20^{\circ} \mathrm{C}$ rotates as a rigid body about the $z$-axis in a spinning cylindrical container (Fig. P10-42). There are no viscous stresses since the water moves as a solid body; thus the Euler equation is appropriate. (We neglect viscous stresses caused by air acting on the water surface.) Integrate the Euler equation to generate an expression for pressure as a function of $r$ and $z$ everywhere in the water. Write an equation for the shape of the free surface ( $z_{\text {surface }}$ as a function of $r$ ). (Hint: $P=P_{\text {atm }}$ everywhere on the free surface. The flow is rotationally symmetric about the $z$-axis.)

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Problem 43

Repeat Prob. 10-42, except let the rotating fluid be engine oil at $60^{\circ} \mathrm{C}$. Discuss.

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Problem 44

Using the results of Prob. 10-42, calculate the Bernoulli constant as a function of radial coordinate $r$.

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Problem 45

Consider steady, incompressible, two-dimensional flow of fluid into a converging duct with straight walls (Fig. P10-45). The volume flow rate is $\dot{V}$, and the velocity is in the radial direction only, with $u_r$ a function of $r$ only. Let $b$ be the width into the page. At the inlet into the converging duct ( $r$ $=R), u_r=u_r(R)$. Assuming inviscid flow everywhere, generate an expression for $u_r$ as a function of $r, R$, and $u_r(R)$ only.

Sketch what the velocity profile at radius $r$ would look like if friction were not neglected (i.e., a real flow) at the same volume flow rate.

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Problem 46

In a certain region of steady, two-dimensional, incompressible flow, the velocity field is given by $\vec{V}=(u, v)$ $=(a x+b) \vec{i}+(-a y+c x) \vec{j}$. Show that this region of flow can be considered inviscid.

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Problem 47

What flow property determines whether a region of flow is rotational or irrotational? Discuss.

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Problem 48

In an irrotational region of flow, we can write the velocity vector as the gradient of the scalar velocity potential function, $\vec{V}=\vec{\nabla} \phi$. The components of $\vec{V}$ in cylindrical coordinates, $(r, \theta, z)$ and $\left(u_r, u_\theta, u_z\right)$, are

$$
\begin{aligned}
u_r & =\frac{\partial_\phi}{\partial r} \\
u_\theta & =\frac{1}{r} \frac{\partial_\phi}{\partial \theta} \\
u_z & =\frac{\partial_\phi}{\partial z}
\end{aligned}
$$

From Chap. 9, we also write the components of the vorticity vector in cylindrical coordinates as $\zeta_r=\frac{1}{r} \frac{\partial u_z}{\partial \theta}-\frac{\partial u_\theta}{\partial z}$, $\zeta_\theta=\frac{\partial u_r}{\partial z}-\frac{\partial u_z}{\partial r}$, and $\zeta_z=\frac{1}{r} \frac{\partial}{\partial r}\left(r u_\theta\right)-\frac{1}{r} \frac{\partial u_r}{\partial \theta}$. Substitute the velocity components into the vorticity components to show that all three components of the vorticity vector are indeed zero in an irrotational region of flow.

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Problem 49

Substitute the components of the velocity vector given in Prob. 10-48 into the Laplace equation in cylindrical coordinates. Showing all your algebra, verify that the Laplace equation is valid in an irrotational region of flow.

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Problem 50

Consider the flow field produced by a hair dryer (Fig. P10-50). Identify regions of this flow field that can be approximated as irrotational, and those for which the irrotational flow approximation would not be appropriate (rotational flow regions).

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Problem 51

Write the Bernoulli equation, and discuss how it differs between an inviscid, rotational region of flow and a viscous, irrotational region of flow. Which case is more restrictive (in regards to the Bernoulli equation)?

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Problem 52

Streamlines in a steady, two-dimensional, incompressible flow field are sketched in Fig. P10-52. The flow in the region shown is also approximated as irrotational. Sketch what a few equipotential curves (curves of constant potential function) might look like in this flow field. Explain how you arrive at the curves you sketch.

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Problem 53

In an irrotational region of flow, the velocity field can be calculated without need of the momentum equation by solving the Laplace equation for velocity potential function $\phi$, and then solving for the components of $\vec{V}$ from the definition of $\phi$, namely, $\vec{v}=\vec{\nabla} \phi$. Discuss the role of the momentum equation in an irrotational region of flow.

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Problem 54

Consider the following, steady, two-dimensional, incompressible, velocity field: $\vec{V}=(u, v)=(a x+b) \vec{i}$ $+(-a y+c x) \vec{j}$. Is this flow field irrotational? If so, generate an expression for the velocity potential function.

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Problem 55

A subtle point, often missed by students of fluid mechanics (and even their professors!), is that an irrotational
(potential) region of flow is not the same as an inviscid region of flow (Fig. P10-55). Discuss the differences and similarities between these two approximations. Give an example of each.

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Problem 56

Consider a steady, two-dimensional, incompressible, irrotational velocity field specified by its velocity potential function, $\phi=5\left(x^2-y^2\right)+2 x-4 y$. (a) Calculate velocity components $u$ and $v$. (b) Verify that the velocity field is irrotational in the region in which $\phi$ applies. (c) Generate an expression for the stream function in this region.

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Problem 57

Consider a planar irrotational region of flow in the $r \theta$-plane. Show that stream function $\psi$ satisfies the Laplace equation in cylindrical coordinates.

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Problem 58

In this chapter, we describe axisymmetric irrotational flow in terms of cylindrical coordinates $r$ and $z$ and velocity components $u_r$ and $u_z$. An alternative description of axisymmetric flow arises if we use spherical polar coordinates and set the $x$-axis as the axis of symmetry. The two relevant directional components are now $r$ and $\theta$, and their corresponding velocity components are $u_r$ and $u_\theta$. In this coordinate system, radial location $r$ is the distance from the origin, and polar angle $\theta$ is the angle of inclination between the radial vector and the axis of rotational symmetry (the $x$ axis), as sketched in Fig. P10-58; a slice defining the $r \theta$ plane is shown. This is a type of two-dimensional flow because there are only two independent spatial variables, $r$ and $\theta$. In other words, a solution of the velocity and pressure fields in any $r \theta$-plane is sufficient to characterize the entire region of axisymmetric irrotational flow. Write the Laplace equation for $\phi$ in spherical polar coordinates, valid in regions of axisymmetric irrotational flow. (Hint: You may consult a textbook on vector analysis.)

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Problem 59

Show that the incompressible continuity equation for axisymmetric flow in spherical polar coordinates, $\frac{1}{r} \frac{\partial}{\partial r}\left(r^2 u_r\right)$ $+\frac{1}{\sin \theta} \frac{\partial}{\partial \theta}\left(u_\theta \sin \theta\right)=0$, is identically satisfied by a stream function defined as $u_r=-\frac{1}{r^2 \sin \theta} \frac{\partial \psi}{\partial \theta}$ and $u_\theta=\frac{1}{r \sin \theta} \frac{\partial \psi}{\partial r}$, so long as $\psi$ is a smooth function of $r$ and $\theta$.

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Problem 60

Consider a uniform stream of magnitude $V$ inclined at angle $\alpha$ (Fig. P10-60). Assuming incompressible planar irrotational flow, find the velocity potential function and the stream function. Show all your work.

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Problem 61

Consider an irrotational line source of strength $\dot{V}_L$ in the $x y$ - or $r \theta$-plane. The velocity components are $u_r=\frac{\partial \phi}{\partial r}$ $=\frac{1}{r} \frac{\partial \psi}{\partial \theta}=\frac{\dot{\mathrm{V}} / L}{2 \pi r}$ and $u_\theta=\frac{1}{r} \frac{\partial \phi}{\partial \theta}=-\frac{\partial \psi}{\partial r}=0$. In this chapter, we started with the equation for $u_\theta$ to generate expressions for the velocity potential function and the stream function for the line source. Repeat the analysis, except start with the equation for $u_r$, showing all your work.

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Problem 62

Consider an irrotational line vortex of strength $\Gamma$ in the $x y$ - or $r \theta$-plane. The velocity components are $u_r=\frac{\partial \phi}{\partial r}$ $=\frac{1}{r} \frac{\partial \psi}{\partial \theta}=0$ and $u_\theta=\frac{1}{r} \frac{\partial \phi}{\partial \theta}=-\frac{\partial \psi}{\partial r}=\frac{\Gamma}{2 \pi r}$. Generate expressions for the velocity potential function and the stream function for the line vortex, showing all your work.

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Problem 63

The stream function for steady, incompressible, twodimensional flow over a circular cylinder of radius $a$ and free-stream velocity $V_{\infty}$ is $\psi=V_{\infty} \sin \theta\left(r-a^2 / r\right)$ for the case in which the flow field is approximated as irrotational (Fig. P10-63). Generate an expression for the velocity potential function $\phi$ for this flow as a function of $r$ and $\theta$, and parameters $V_{\infty}$ and $a$.

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Problem 64

What is D'Alembert's paradox? Why is it a paradox?

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Problem 65

In this chapter, we make a statement that the boundary layer approximation "bridges the gap" between the Euler equation and the Navier-Stokes equation. Explain.

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Problem 66

For each statement, choose whether the statement is true or false and discuss your answer briefly. These statements concern a laminar boundary layer on a flat plate (Fig. P10-66C).
(a) At a given $x$-location, if the Reynolds number were to increase, the boundary layer thickness would also increase.
(b) As outer flow velocity increases, so does the boundary layer thickness.
(c) As the fluid viscosity increases, so does the boundary layer thickness.
(d) As the fluid density increases, so does the boundary layer thickness.

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Problem 67

We usually think of boundary layers as occurring along solid walls. However, there are other flow situations in which the boundary layer approximation is also appropriate. Name three such flows, and explain why the boundary layer approximation is appropriate.

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Problem 68

A laminar boundary layer growing along a flat plate is sketched in Fig. P10-68C. Several velocity profiles and the boundary layer thickness $\delta(x)$ are also shown. Sketch several streamlines in this flow field. Is the curve representing $\delta(x)$ a streamline?

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Problem 69

What is a trip wire, and what is its purpose?

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Problem 70

Air at $30^{\circ} \mathrm{C}$ flows at a uniform speed of $25.0 \mathrm{~m} / \mathrm{s}$ along a smooth flat plate. Calculate the approximate $x$-location along the plate where the boundary layer begins the transition process toward turbulence. At approximately what $x$ location along the plate is the boundary layer likely to be fully turbulent?

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Problem 71

Water flows over the fin of a small underwater vehicle at a speed of $V=6.0 \mathrm{mi} / \mathrm{h}$ (Fig. P10-71E). The temperature of the water is $40^{\circ} \mathrm{F}$, and the chord length $c$ of the fin is 1.6 ft . Is the boundary layer on the surface of the fin laminar or turbulent or transitional?

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Problem 72

Air flows parallel to a speed limit sign along the highway at speed $V=5.0 \mathrm{~m} / \mathrm{s}$. The temperature of the air is $25^{\circ} \mathrm{C}$, and the width $W$ of the sign parallel to the flow direction is 0.45 m . Is the boundary layer on the sign laminar or turbulent or transitional?

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Problem 73

Air flows through the test section of a small wind tunnel at speed $V=7.5 \mathrm{ft} / \mathrm{s}$. The temperature of the air is
$80^{\circ} \mathrm{F}$, and the length of the wind tunnel test section is 1.5 ft . Assume that the boundary layer thickness is negligible prior to the start of the test section. Is the boundary layer along the test section wall laminar or turbulent or transitional?

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Problem 74

Static pressure $P$ is measured at two locations along the wall of a laminar boundary layer (Fig. P10-74). The measured pressures are $P_1$ and $P_2$, and the distance between the taps is small compared to the characteristic body dimension $\left(\Delta x=x_2-x_1 \ll L\right)$. The outer flow velocity above the boundary layer at point 1 is $U_1$. The fluid density and viscosity are $\rho$ and $\mu$, respectively. Generate an approximate expression for $U_2$, the outer flow velocity above the boundary layer at point 2 , in terms of $P_1, P_2, \Delta x, U_1, \rho$, and $\mu$.

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Problem 75

Consider two pressure taps along the wall of a laminar boundary layer as in Fig. P10-74. The fluid is air at $25^{\circ} \mathrm{C}, U_1=10.3 \mathrm{~m} / \mathrm{s}$, and the static pressure $P_1$ is 2.44 Pa greater than static pressure $P_2$, as measured by a very sensitive differential pressure transducer. Is outer flow velocity $U_2$ greater than, equal to, or less than outer flow velocity $U_1$ ? Explain. Estimate $U_2$.

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Problem 76

In your own words, summarize the five steps of the boundary layer procedure.

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Problem 77

In your own words, list at least three "red flags" to look out for when performing laminar boundary layer calculations.

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Problem 78

Consider the Blasius solution for a laminar flat plate boundary layer. The nondimensional slope at the wall is given by Eq. 8 of Example 10-10. Transform this result to physical variables, and show that Eq. 9 of Example 10-10 is correct.

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Problem 79

For the small wind tunnel of Prob. 10-73E, assume the flow remains laminar, and estimate the boundary layer thickness, the displacement thickness, and the momentum thickness of the boundary layer at the end of the test section. Give your answers in inches, compare the three results, and discuss.

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Problem 80

One dimension of a rectangular flat plate is twice the other. Air at uniform speed flows parallel to the plate, and a laminar boundary layer forms on both sides of the plate. Which orientation-long dimension to the wind (Fig. P10-80a) or short dimension to the wind (Fig. P10-80b)has the higher drag? Explain.

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Problem 81

Two definitions of displacement thickness are given in this chapter. Write both definitions in your own words. For the laminar boundary layer growing on a flat plate, which is larger-boundary layer thickness $\delta$ or displacement thickness $\delta^*$ ? Discuss.

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Problem 82

A laminar flow wind tunnel has a test section that is 40 cm in diameter and 60 cm in length. The air is at $20^{\circ} \mathrm{C}$. At a uniform air speed of $2.0 \mathrm{~m} / \mathrm{s}$ at the test section inlet, by how much will the centerline air speed accelerate by the end of the test section?

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Problem 83

Repeat the calculation of Prob. 10-82, except for a test section of square rather than round cross section, with a $40 \mathrm{~cm} \times 40 \mathrm{~cm}$ cross section and a length of 60 cm . Compare the result to that of Prob. 10-82 and discuss.

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Problem 84

In order to avoid boundary layer interference, engineers design a "boundary layer scoop" to skim off the bound-

ary layer in a large wind tunnel (Fig. P10-84). The scoop is constructed of thin sheet metal. The air is at $20^{\circ} \mathrm{C}$, and flows at $V=65.0 \mathrm{~m} / \mathrm{s}$. How high (dimension $h$ ) should the scoop be at downstream distance $x=1.45 \mathrm{~m}$ ?

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Problem 85

A small, axisymmetric, low-speed wind tunnel is built to calibrate hot wires. The diameter of the test section is 6.0 in , and its length is 10.0 in . The air is at $70^{\circ} \mathrm{F}$. At a uniform air speed of $5.0 \mathrm{ft} / \mathrm{s}$ at the test section inlet, by how much will the centerline air speed accelerate by the end of the test section? What should the engineers do to eliminate this acceleration?

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Problem 86

Air at $70^{\circ} \mathrm{F}$ flows parallel to a smooth, thin, flat plate at $15.5 \mathrm{ft} / \mathrm{s}$. The plate is 10.6 ft long. Determine whether the boundary layer on the plate is most likely laminar, turbulent, or somewhere in between (transitional). Compare the boundary layer thickness at the end of the plate for two cases: (a) the boundary layer is laminar everywhere, and (b) the boundary layer is turbulent everywhere. Discuss.

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Problem 87

Air at $20^{\circ} \mathrm{C}$ flows at $V=5.0 \mathrm{~m} / \mathrm{s}$ parallel to a flat plate (Fig. P10-87). The front of the plate is well rounded, and the plate is 40 cm long. The plate thickness is $h=0.75 \mathrm{~cm}$, but because of boundary layer displacement effects, the flow outside the boundary layer "sees" a plate that has larger apparent thickness. Calculate the apparent thickness of the plate (include both sides) at downstream distance $x=25 \mathrm{~cm}$.

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Problem 88

Air at $20^{\circ} \mathrm{C}$ flows at $V=80.0 \mathrm{~m} / \mathrm{s}$ over a smooth flat plate of length $L=17.5 \mathrm{~m}$. Plot the turbulent boundary layer profile in physical variables ( $u$ as a function of $y$ ) at $x=L$. Compare the profile generated by the one-seventh-power law, the log law, and Spalding's law of the wall, assuming that the boundary layer is fully turbulent from the beginning of the plate.

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Problem 89

Explain the difference between a favorable and an adverse pressure gradient in a boundary layer. In which case does the pressure increase downstream? Why?

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Problem 90

Discuss the implication of an inflection point in a boundary layer profile. Specifically, does the existence of an inflection point infer a favorable or adverse pressure gradient? Explain.

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Problem 91

Compare flow separation for a laminar versus turbulent boundary layer. Specifically, which case is more resistant to flow separation? Why? Based on your answer, explain why golf balls have dimples.

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Problem 92

The streamwise velocity component of a steady, incompressible, laminar, flat plate boundary layer of boundary layer thickness $\delta$ is approximated by the simple linear expression, $u=U y / \delta$ for $y<\delta$, and $u=U$ for $y>\delta$ (Fig. P10-92). Generate expressions for displacement thickness and momentum thickness as functions of $\delta$, based on this linear approximation. Compare the approximate values of $\delta^* / \delta$ and $\theta / \delta$ to the values of $\delta^* / \delta$ and $\theta / \delta$ obtained from the Blasius solution.

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Problem 93

For the linear approximation of Prob. 10-92, use the definition of local skin friction coefficient and the Kármán integral equation to generate an expression for $\delta / x$. Compare your result to the Blasius expression for $\delta / x$. (Note: You will need the results of Prob. 10-92 to do this problem.)

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Problem 94

The Blasius boundary layer profile is an exact solution of the boundary layer equations for flow over a flat plate. However, the results are somewhat cumbersome to use, since the data appear in tabular form (the solution is numerical). Thus, a simple sine wave approximation (Fig. P10-94) is often used in place of the Blasius solution, namely, $u(y) \cong U \sin \left(\frac{\pi}{2} \frac{y}{\delta}\right)$ for $y<\delta$, and $u=U$ for $y \ll \delta$, where $\delta$ is the boundary layer thickness. Plot the Blasius profile and the sine wave approximation on the same plot, in nondimensional form ( $u / U$ versus $y / \delta$ ), and compare. Is the sine wave profile a reasonable approximation?

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Problem 95

The streamwise velocity component of a steady, incompressible, laminar, flat plate boundary layer of boundary layer thickness $\delta$ is approximated by the sine wave profile of Prob. 10-94. Generate expressions for displacement thickness and momentum thickness as functions of $\delta$, based on this sine wave approximation. Compare the approximate values of $\delta^* / \delta$ and $\theta / \delta$ to the values of $\delta^* / \delta$ and $\theta / \delta$ obtained from the Blasius solution.

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Problem 96

For the sine wave approximation of Prob. 10-94, use the definition of local skin friction coefficient and the Kármán integral equation to generate an expression for $\delta / x$. Compare your result to the Blasius expression for $\delta / x$. (Note: You will also need the results of Prob. 10-95 to do this problem.)

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Problem 97

Compare shape factor $H$ (defined in Eq. 10-95) for a laminar versus a turbulent boundary layer on a flat plate, assuming that the turbulent boundary layer is turbulent from the beginning of the plate. Discuss. Specifically, why do you suppose $H$ is called a "shape factor"?

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Problem 98

Calculate the value of shape factor $H$ for the limiting case of a boundary layer that is infinitesimally thin (Fig. P10-98). This value of $H$ is the minimum possible value.

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Problem 99

Integrate Eq. 5 to obtain Eq. 6 of Example 10-14, showing all your work.

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Problem 100

Consider a turbulent boundary layer on a flat plate. Suppose only two things are known: $C_{f . x} \equiv 0.059 \cdot\left(\operatorname{Re}_x\right)^{-1 / 5}$ and $\theta \equiv 0.097 \delta$. Use the Kármán integral equation to generate an expression for $\delta / x$, and compare your result to column (b) of Table 10-4.

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Problem 101

For each statement, choose whether the statement is true or false, and discuss your answer briefly.
(a) The velocity potential function can be defined for threedimensional flows.
(b) The vorticity must be zero in order for the stream function to be defined.
(c) The vorticity must be zero in order for the velocity potential function to be defined.
(d) The stream function can be defined only for two-dimensional flow fields.

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Problem 102

In this chapter, we discuss solid body rotation (Fig. P10-102) as an example of an inviscid flow that is also rotational. The velocity components are $u_r=0, u_\theta=\omega r$, and $u_z=0$. Compute the viscous term of the $\theta$-component of the Navier-Stokes equation, and discuss. Verify that this velocity field is indeed rotational by computing the $z$-component of vorticity.

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Problem 103

Calculate the nine components of the viscous stress tensor in cylindrical coordinates (see Chap. 9) for the velocity field of Prob. 10-102. Discuss.

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Problem 104

In this chapter, we discuss the line vortex (Fig. P10-104) as an example of an irrotational flow field. The

velocity components are $u_r=0, u_\theta=\Gamma /(2 \pi r)$, and $u_z=0$. Compute the viscous term of the $\theta$-component of the Navier-Stokes equation, and discuss. Verify that this velocity field is indeed irrotational by computing the $z$-component of vorticity.

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Problem 105

Calculate the nine components of the viscous stress tensor in cylindrical coordinates (see Chap. 9) for the velocity field of Prob. 10-104. Discuss.

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Problem 106

Water falls down a vertical pipe by gravity alone. The flow between vertical locations $z_1$ and $z_2$ is fully developed, and velocity profiles at these two locations are sketched in Fig. P10-106. Since there is no forced pressure gradient, pressure $P$ is constant everywhere in the flow ( $P=P_{\mathrm{atm}}$ ). Calculate the modified pressure at locations $z_1$ and $z_2$. Sketch profiles of modified pressure at locations $z_1$ and $z_2$. Discuss.

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Problem 107

Suppose the vertical pipe of Prob. 10-106 is now horizontal instead. In order to achieve the same volume flow rate as that of Prob. 10-106, we must supply a forced pressure gradient. Calculate the required pressure drop between two axial locations in the pipe that are the same distance apart as $z_2$ and $z_1$ of Fig. P10-106. How does modified pressure $P^{\prime}$ change between the vertical and horizontal cases?

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Problem 108

Explain why there is a significant velocity overshoot for the midrange values of the Reynolds number in the velocity profiles of Fig. 10-136, but not for the very small values of Re or for the very large values of Re.

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