fluid_mechanics
392 Chapter 8 ■ Viscous Flow in Pipes Newtonian fluid, the shear stress is simply proportional to the velocity gradient, 1see Section 1.62. In the notation associated with our pipe flow, this becomes “t m dudy” t m du dr (8.6) The negative sign is included to give t 7 0 with dudr 6 0 1the velocity decreases from the pipe centerline to the pipe wall2. Equations 8.3 and 8.6 represent the two governing laws for fully developed laminar flow of a Newtonian fluid within a horizontal pipe. The one is Newton’s second law of motion and the other is the definition of a Newtonian fluid. By combining these two equations we obtain which can be integrated to give the velocity profile as follows: or du ¢p a dr 2m/ b r du ¢p 2m/ r dr u a ¢p 4m/ b r 2 C 1 where C 1 is a constant. Because the fluid is viscous it sticks to the pipe wall so that u 0 at r D2. Thus, C 1 1¢p16m/2D 2 . Hence, the velocity profile can be written as u1r2 a ¢pD2 2 bc1 a2r 16m/ D b d V c c 1 a 2r 2 D b d (8.7) Under certain restrictions the velocity profile in a pipe is parabolic. R dr r dA = 2 πr dr where V c ¢pD 2 116m/2 is the centerline velocity. An alternative expression can be written by using the relationship between the wall shear stress and the pressure gradient 1Eqs. 8.5 and 8.72 to give where R D2 is the pipe radius. This velocity profile, plotted in Fig. 8.9, is parabolic in the radial coordinate, r, has a maximum velocity, V c , at the pipe centerline, and a minimum velocity 1zero2 at the pipe wall. The volume flowrate through the pipe can be obtained by integrating the velocity profile across the pipe. Since the flow is axisymmetric about the centerline, the velocity is constant on small area elements consisting of rings of radius r and thickness dr as shown in the figure in the margin. Thus, or Q u dA rR u1r2 t wD 4m c 1 a r R b 2 d r0 u1r22pr dr 2p V c R Q pR2 V c 2 By definition, the average velocity is the flowrate divided by the cross-sectional area, V QA QpR 2 , so that for this flow 0 c 1 a r R b 2 d r dr and V pR2 V c 2pR 2 V c 2 ¢pD2 32m/ Q pD4 ¢p 128m/ (8.8) (8.9)
8.2 Fully Developed Laminar Flow 393 Poiseuille’s law is valid for laminar flow only. 16Q 0 Q ~ D 4 Q Q 0 D 0 2D 0 D As is indicated in Eq. 8.8, the average velocity is one-half of the maximum velocity. In general, for velocity profiles of other shapes 1such as for turbulent pipe flow2, the average velocity is not merely the average of the maximum 1V c 2 and minimum 102 velocities as it is for the laminar parabolic profile. The two velocity profiles indicated in Fig. 8.9 provide the same flowrate—one is the fictitious ideal 1m 02 profile; the other is the actual laminar flow profile. The above results confirm the following properties of laminar pipe flow. For a horizontal pipe the flowrate is 1a2 directly proportional to the pressure drop, 1b2 inversely proportional to the viscosity, 1c2 inversely proportional to the pipe length, and 1d2 proportional to the pipe diameter to the fourth power. With all other parameters fixed, an increase in diameter by a factor of 2 will increase the flowrate by a factor of 2 4 16—the flowrate is very strongly dependent on pipe size. This dependence is shown by the figure in the margin. Likewise, a small error in pipe diameter can cause a relatively large error in flowrate. For example, a 2% error in diameter gives an 8% error in flowrate 1Q D 4 or dQ 4D 3 dD, so that dQQ 4 dDD2. This flow, the properties of which were first established experimentally by two independent workers, G. Hagen 11797–18842 in 1839 and J. Poiseuille 11799–18692 in 1840, is termed Hagen–Poiseuille flow. Equation 8.9 is commonly referred to as Poiseuille’s law. Recall that all of these results are restricted to laminar flow 1those with Reynolds numbers less than approximately 21002 in a horizontal pipe. The adjustment necessary to account for nonhorizontal pipes, as shown in Fig. 8.10, can be easily included by replacing the pressure drop, ¢p, by the combined effect of pressure and gravity, ¢p g/ sin u, where u is the angle between the pipe and the horizontal. 1Note that u 7 0 if the flow is uphill, while u 6 0 if the flow is downhill.2 This can be seen from the force balance in the x direction 1along the pipe axis2 on the cylinder of fluid shown in Fig. 8.10b. The method is exactly analogous to that used to obtain the Bernoulli equation 1Eq. 3.62 when the streamline is not horizontal. The net force in the x direction is a combination of the pressure force in that direction, ¢ppr 2 , and the component of weight in that direction, gpr 2 / sin u. The result is a slightly modified form of Eq. 8.3 given by ¢p g/ sin u / 2t r (8.10) Thus, all of the results for the horizontal pipe are valid provided the pressure gradient is adjusted for the elevation term, that is, ¢p is replaced by ¢p g/ sin u so that V 1¢p g/ sin u2D2 32m/ (8.11) and p1¢p g/ sin u2D4 Q (8.12) 128m/ It is seen that the driving force for pipe flow can be either a pressure drop in the flow direction, ¢p, or the component of weight in the flow direction, g/ sin u. If the flow is downhill, gravity helps the flow 1a smaller pressure drop is required; sin u 6 02. If the flow is uphill, gravity works against the flow 1a larger pressure drop is required; sin u 7 02. Note that g/ sin u g¢z 1where Q τ 2 πr p π r 2 x Fluid cylinder θ (p + Δp) πr 2 r θ sin θ = γπr 2 sin θ (a) F I G U R E 8.10 (b) Free-body diagram of a fluid cylinder for flow in a nonhorizontal pipe.
- Page 366 and 367: 342 Chapter 7 ■ Dimensional Analy
- Page 368 and 369: 344 Chapter 7 ■ Dimensional Analy
- Page 370 and 371: 346 Chapter 7 ■ Dimensional Analy
- Page 372 and 373: 348 Chapter 7 ■ Dimensional Analy
- Page 374 and 375: 350 Chapter 7 ■ Dimensional Analy
- Page 376 and 377: 352 Chapter 7 ■ Dimensional Analy
- Page 378 and 379: 354 Chapter 7 ■ Dimensional Analy
- Page 380 and 381: 356 Chapter 7 ■ Dimensional Analy
- Page 382 and 383: 358 Chapter 7 ■ Dimensional Analy
- Page 384 and 385: 360 Chapter 7 ■ Dimensional Analy
- Page 386 and 387: 362 Chapter 7 ■ Dimensional Analy
- Page 388 and 389: 364 Chapter 7 ■ Dimensional Analy
- Page 390 and 391: 366 Chapter 7 ■ Dimensional Analy
- Page 392 and 393: 368 Chapter 7 ■ Dimensional Analy
- Page 394 and 395: 370 Chapter 7 ■ Dimensional Analy
- Page 396 and 397: 372 Chapter 7 ■ Dimensional Analy
- Page 398 and 399: 374 Chapter 7 ■ Dimensional Analy
- Page 400 and 401: 376 Chapter 7 ■ Dimensional Analy
- Page 402 and 403: 378 Chapter 7 ■ Dimensional Analy
- Page 404 and 405: 380 Chapter 7 ■ Dimensional Analy
- Page 406 and 407: 382 Chapter 7 ■ Dimensional Analy
- Page 408 and 409: 384 Chapter 8 ■ Viscous Flow in P
- Page 410 and 411: 386 Chapter 8 ■ Viscous Flow in P
- Page 412 and 413: 388 Chapter 8 ■ Viscous Flow in P
- Page 414 and 415: 390 Chapter 8 ■ Viscous Flow in P
- Page 418 and 419: 394 Chapter 8 ■ Viscous Flow in P
- Page 420 and 421: 396 Chapter 8 ■ Viscous Flow in P
- Page 422 and 423: 398 Chapter 8 ■ Viscous Flow in P
- Page 424 and 425: 400 Chapter 8 ■ Viscous Flow in P
- Page 426 and 427: 402 Chapter 8 ■ Viscous Flow in P
- Page 428 and 429: 404 Chapter 8 ■ Viscous Flow in P
- Page 430 and 431: 406 Chapter 8 ■ Viscous Flow in P
- Page 432 and 433: 408 Chapter 8 ■ Viscous Flow in P
- Page 434 and 435: 410 Chapter 8 ■ Viscous Flow in P
- Page 436 and 437: 412 Chapter 8 ■ Viscous Flow in P
- Page 438 and 439: 414 Chapter 8 ■ Viscous Flow in P
- Page 440 and 441: 416 Chapter 8 ■ Viscous Flow in P
- Page 442 and 443: 418 Chapter 8 ■ Viscous Flow in P
- Page 444 and 445: 420 Chapter 8 ■ Viscous Flow in P
- Page 446 and 447: 422 Chapter 8 ■ Viscous Flow in P
- Page 448 and 449: 424 Chapter 8 ■ Viscous Flow in P
- Page 450 and 451: 426 Chapter 8 ■ Viscous Flow in P
- Page 452 and 453: 428 Chapter 8 ■ Viscous Flow in P
- Page 454 and 455: 430 Chapter 8 ■ Viscous Flow in P
- Page 456 and 457: 432 Chapter 8 ■ Viscous Flow in P
- Page 458 and 459: 434 Chapter 8 ■ Viscous Flow in P
- Page 460 and 461: 436 Chapter 8 ■ Viscous Flow in P
- Page 462 and 463: 438 Chapter 8 ■ Viscous Flow in P
- Page 464 and 465: 440 Chapter 8 ■ Viscous Flow in P
392 Chapter 8 ■ Viscous Flow in Pipes<br />
Newtonian <strong>fluid</strong>, the shear stress is simply proportional to the velocity gradient,<br />
1see Section 1.62. In the notation associated with our pipe flow, this becomes<br />
“t m dudy”<br />
t m du<br />
dr<br />
(8.6)<br />
The negative sign is included to give t 7 0 with dudr 6 0 1the velocity decreases from the pipe<br />
centerline to the pipe wall2.<br />
Equations 8.3 and 8.6 represent the two governing laws for fully developed laminar flow of<br />
a Newtonian <strong>fluid</strong> within a horizontal pipe. The one is Newton’s second law of motion and the<br />
other is the definition of a Newtonian <strong>fluid</strong>. By combining these two equations we obtain<br />
which can be integrated to give the velocity profile as follows:<br />
or<br />
<br />
du ¢p<br />
a<br />
dr 2m/ b r<br />
du ¢p<br />
2m/ r dr<br />
u a ¢p<br />
4m/ b r 2 C 1<br />
where C 1 is a constant. Because the <strong>fluid</strong> is viscous it sticks to the pipe wall so that u 0 at<br />
r D2. Thus, C 1 1¢p16m/2D 2 . Hence, the velocity profile can be written as<br />
u1r2 a ¢pD2<br />
2<br />
bc1 a2r<br />
16m/ D b d V c c 1 a 2r 2<br />
D b d<br />
(8.7)<br />
Under certain restrictions<br />
the velocity<br />
profile in a pipe<br />
is parabolic.<br />
R<br />
dr<br />
r<br />
dA = 2 πr<br />
dr<br />
where V c ¢pD 2 116m/2 is the centerline velocity. An alternative expression can be written by using<br />
the relationship between the wall shear stress and the pressure gradient 1Eqs. 8.5 and 8.72 to give<br />
where R D2 is the pipe radius.<br />
This velocity profile, plotted in Fig. 8.9, is parabolic in the radial coordinate, r, has a maximum<br />
velocity, V c , at the pipe centerline, and a minimum velocity 1zero2 at the pipe wall. The volume<br />
flowrate through the pipe can be obtained by integrating the velocity profile across the pipe.<br />
Since the flow is axisymmetric about the centerline, the velocity is constant on small area elements<br />
consisting of rings of radius r and thickness dr as shown in the figure in the margin. Thus,<br />
or<br />
Q u dA <br />
rR<br />
u1r2 t wD<br />
4m c 1 a r R b 2<br />
d<br />
r0<br />
u1r22pr dr 2p V c R<br />
Q pR2 V c<br />
2<br />
By definition, the average velocity is the flowrate divided by the cross-sectional area,<br />
V QA QpR 2 , so that for this flow<br />
0<br />
c 1 a r R b 2<br />
d r dr<br />
and<br />
V pR2 V c<br />
2pR 2<br />
V c<br />
2 ¢pD2<br />
32m/<br />
Q pD4 ¢p<br />
128m/<br />
(8.8)<br />
(8.9)