Natural Convective Flow Inside an Air Space
Consider double-glazed window plates with spacing of 12.7 mm and height of 0.6 m kept at temperatures of 17°C and 0°C. Calculate the natural convective heat transfer coefficient.
Given: Spacing L = 0.0127 m, height H = 0.60 m
Find: h_{con} using Equation 12.25 for natural internal flow over plates
Lookup values: From property tables of air (Table A1) at a mean temperature of (0°C + 17°C)/2 = 8.5°C: \rho = 1.271 kg/m^{3}, \mu = 1.75 × 10^{−5} Pa ⋅ s, c_{p} = 1004 J/(kg ⋅ K), k = 0.0246 W/(m · K),
u = 1.40 \times 10^{-5} m^{2}/s, \alpha = 1.95 \times 10^{-5} m^{2}/s and Pr = 0.717
TABLE A.1 (IP Units) Transport Properties of Standard, Dry Air (14.7 psia) |
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°R | °F | ρ (lbm/ft3) | cp (Btu/lb · °R) | k (cp/cv) | μ x 104 (lbm/ft · s) |
180 | -280 | 0.2247 | 0.2456 | 0.0466 | |
198 | -262 | 0.2033 | 0.2440 | 1.4202 | 0.0513 |
216 | -244 | 0.1858 | 0.2430 | 1.4166 | 0.0559 |
234 | -226 | 0.1711 | 0.2423 | 1.4139 | 0.0604 |
252 | -208 | 0.1586 | 0.2418 | 1.4119 | 0.0648 |
270 | -190 | 0.1478 | 0.2414 | 1.4102 | 0.0691 |
288 | -172 | 0.1384 | 0.2411 | 1.4089 | 0.0733 |
306 | -154 | 0.1301 | 0.2408 | 1.4079 | 0.0774 |
324 | -136 | 0.1228 | 0.2406 | 1.4071 | 0.0815 |
342 | -118 | 0.1163 | 0.2405 | 1.4064 | 0.0854 |
360 | -100 | 0.1104 | 0.2404 | 1.4057 | 0.0892 |
369 | -91 | 0.1078 | 0.2403 | 1.4055 | 0.0911 |
378 | -82 | 0.1051 | 0.2403 | 1.4053 | 0.0930 |
387 | -73 | 0.1027 | 0.2403 | 1.4050 | 0.0949 |
396 | -64 | 0.1003 | 0.2402 | 1.4048 | 0.0967 |
405 | -55 | 0.0981 | 0.2402 | 1.4046 | 0.0986 |
414 | -46 | 0.0959 | 0.2402 | 1.4044 | 0.1004 |
423 | -37 | 0.0939 | 0.2402 | 1.4042 | 0.1022 |
432 | -28 | 0.0919 | 0.2401 | 1.4040 | 0.1039 |
441 | -19 | 0.0901 | 0.2401 | 1.4038 | 0.1057 |
450 | -10 | 0.0882 | 0.2401 | 1.4036 | 0.1074 |
459.7 | 0 | 0.0865 | 0.2401 | 1.4034 | 0.1092 |
468 | 8 | 0.0848 | 0.2401 | 1.4032 | 0.1109 |
486 | 26 | 0.0817 | 0.2492 | 1.4029 | 0.1143 |
504 | 44 | 0.0787 | 0.2402 | 1.4024 | 0.1176 |
522 | 62 | 0.0760 | 0.2403 | 1.4020 | 0.1208 |
540 | 80 | 0.0735 | 0.2404 | 1.4017 | 0.1241 |
558 | 98 | 0.0711 | 0.2405 | 1.4013 | 0.1272 |
576 | 116 | 0.0689 | 0.2406 | 1.4008 | 0.1303 |
594 | 134 | 0.0668 | 0.2407 | 1.4004 | 0.1334 |
612 | 152 | 0.0648 | 0.2409 | 1.3999 | 0.1364 |
630 | 170 | 0.0630 | 0.2411 | 1.3993 | 0.1394 |
648 | 188 | 0.0612 | 0.2412 | 1.3987 | 0.1423 |
666 | 206 | 0.0595 | 0.2415 | 1.3981 | 0.1452 |
684 | 224 | 0.0580 | 0.2417 | 1.3975 | 0.1479 |
702 | 242 | 0.0565 | 0.2420 | 1.3968 | 0.1508 |
720 | 260 | 0.0551 | 0.2422 | 1.3961 | 0.1536 |
738 | 278 | 0.0537 | 0.2425 | 1.3953 | 0.1563 |
756 | 296 | 0.0525 | 0.2428 | 1.3946 | 0.1590 |
774 | 314 | 0.0512 | 0.2432 | 1.3938 | 0.1617 |
792 | 332 | 0.0501 | 0.2435 | 1.3929 | 0.1643 |
810 | 350 | 0.0490 | 0.2439 | 1.3920 | 0.1670 |
100 | -173.15 | 3.598 | 1.028 | 6.929 | |
110 | -163.15 | 3.256 | 1.022 | 1.420 | 7.633 |
120 | -153.15 | 2.975 | 1.017 | 1.416 | 8.319 |
130 | -143.15 | 2.740 | 1.014 | 1.413 | 8.990 |
140 | -133.15 | 2.540 | 1.012 | 1.411 | 9.646 |
150 | -123.15 | 2.367 | 1.010 | 1.410 | 10.28 |
160 | -113.15 | 2.217 | 1.009 | 1.408 | 10.91 |
170 | -103.15 | 2.085 | 1.008 | 1.407 | 11.52 |
180 | -93.15 | 1.968 | 1.007 | 1.407 | 12.12 |
190 | -83.15 | 1.863 | 1.007 | 1.406 | 12.71 |
200 | -73.15 | 1.769 | 1.006 | 1.405 | 13.28 |
210 | -63.15 | 1.684 | 1.006 | 1.405 | 13.85 |
220 | -53.15 | 1.607 | 1.006 | 1.404 | 14.40 |
230 | -43.15 | 1.537 | 1.006 | 1.404 | 14.94 |
240 | -33.15 | 1.473 | 1.005 | 1.404 | 15.47 |
250 | -23.15 | 1.413 | 1.005 | 1.403 | 15.99 |
260 | -13.15 | 1.359 | 1.005 | 1.403 | 16.50 |
270 | -3.15 | 1.308 | 1.006 | 1.402 | 17.00 |
280 | 6.85 | 1.261 | 1.006 | 1.402 | 17.50 |
290 | 16.85 | 1.218 | 1.006 | 1.402 | 17.98 |
300 | 26.85 | 1.177 | 1.006 | 1.401 | 18.46 |
310 | 36.85 | 1.139 | 1.007 | 1.401 | 18.93 |
320 | 46.85 | 1.103 | 1.007 | 1.400 | 19.39 |
330 | 56.85 | 1.070 | 1.008 | 1.400 | 19.85 |
340 | 66.85 | 1.038 | 1.008 | 1.399 | 20.30 |
350 | 76.85 | 1.008 | 1.009 | 1.399 | 20.75 |
360 | 86.85 | 0.980 | 1.010 | 1.398 | 21.18 |
370 | 96.85 | 0.953 | 1.011 | 1.398 | 21.60 |
380 | 106.85 | 0.928 | 1.012 | 1.397 | 22.02 |
390 | 116.85 | 0.905 | 1.013 | 1.396 | 22.44 |
400 | 126.85 | 0.882 | 1.014 | 1.396 | 22.86 |
410 | 136.85 | 0.860 | 1.015 | 1.395 | 23.27 |
420 | 146.85 | 0.840 | 1.017 | 1.394 | 23.66 |
430 | 156.85 | 0.820 | 1.018 | 1.393 | 24.06 |
440 | 166.85 | 0.802 | 1.020 | 1.392 | 24.85 |
450 | 176.85 | 0.784 | 1.021 | 1.392 | 24.85 |
Source: CRC Press, Handbook of Tables for Applied Engineering Science, CRC Press, Inc., Boca Raton, FL, 1973. |
First, the Rayleigh number is determined from Equation 12.18 as
Ra = \frac{g \beta (\Delta T) L^{3}}{v \alpha}= \frac{9.81 m/s^{2} \times 0.0355 K^{-1} \times (17°C – 0°C) \times 0.0127^{3} m^{3}}{1.40 \times 10^{-5} m^{2}/s \times 1.95 \times 10^{-5} m^{2}/s}
= 4442
Next, we will determine the Nusselt number using Equation 12.27:
N u_{L} = 0.42 {Ra_{L}}^{1/4} Pr^{0.012} \left\lgroup \frac{L}{H} \right\rgroup^{0.3}= 0.42 \times 4442^{1/4} \times 0.717^{0.012} \times \left\lgroup \frac{0.0127}{0.6} \right\rgroup^{0.3} = 1.083
from which the convective heat transfer coefficient is deduced from Equation 12.16 as
Nu = \frac{h_{con} D}{k} (12.16)
h_{con} = \frac{0.0246 W/(m \cdot K) \times 1.083}{0.0127 m} = 2.10 W/(m^{2} \cdot K)Comments
The Nusselt number is close to unity, suggesting that the interpane heat transfer (neglecting the radiative component) is mostly by conduction.
The spacing is small enough to have largely suppressed the onset of a convection loop.