atomic energy of canada limited fluid modeling of critical
TRANSCRIPT
Atomic Energy of Canada Limited
FLUID MODELING OF CRITICAL HEAT FLUX
IN UNIFORMLY HEATED ANNULI
by
S.Y. AHMAD and D.C. GROENEVELD
Paper 1-8 presented atthe International Symposium on Two-phase Systems
held at Technion City, Haifa, Israel, August 29-September 2, 1971
Chalk River, Ontario
January 1972
AECL-4070
ATOMIC ENERGY OF CANADA LIMITED
FLUID MODELING OF CRITICAL HEAT FLUXIN UNIFORMLY HEATED ANNULI
S.Y. Ahmad and D.C. Groeneveld
Paper 1-8 presented at the International Symposium onTwo-phase Systems held at Technion City, Haifa,
Israel, August 29—September 2,1971
ABSTRACT
This paper presents the results of an experimental and analytical program to developFreon—water modeling of critical heat flux in annular geometries. Experimental criticalheat flux data were obtained with Freon-12 over a wide range of pressure and mass flux.These were compared with water data using Ahmad's compensated distortion model. Acritical heat flux correlation for annular geometries which is independent of fluid typeswas developed from the Freon data and subsequenUy applied to published water data. Itis concluded that adequate modeling of critical heat flux in an annular geometry can beobtained, provided the size of the model and prototype is identical.
Chalk River Nuclear LaboratoriesChalk River, Ontario
January 1972
AECL-4070
MODELAGE PAR FLUTOE DES ECOULEMENTS THERMIQUES CRITIQUES
DANS DES ANNEAUX UNIFORMEMENT CHAUFFES
par
S.Y. Ahmad et D.C. Groeneveld
Communication 1-8 presentee au Symposium internationalsur les systemes biphases tenu a Technion City, Haifa,
Israel, du 29 aout au 2 septembre 1971
Resume
On presente, dans ce rapport, les resultats d'un programme experimental etanalytique destine a mettre au point le modelage par eau-freon des ecoulementsthermiques critiques passant dans des geometries annulaires. Des donnees experimentalesconcernant ces ecoulements ont ete obtenues avec du freon-12 dans une vaste gamme depressions et d'ecoulements massifs. Elles ont ete comparees aux donnees relatives a l'eauau moyen du modele de distorsion compensee de Ahmad. Une correlation de Pecoulementthermique critique, valable pour les geometries annulaires et ne dependant pas des typesde fluides, a ete realisee a partir des donnees obtenues avec le freon et ulterieurementappliquee aux donnees relatives a l'eau deja publiees. La conclusion est que Ton peutconfectionner der, modeles adequats pour les ecoulements thermiques critiques dans unegeometrie annulaire, a condition que les dimensions des modeles soient identiques a cellesdes prototypes.
L'Energie Atomique du Canada, LimiteeLaboratoires Nucleaires de Chalk River
Chalk River, Ontario
AECL-4070
NOMENCLATURE
CHF Critical beat flux
D Hydraulic equivalent diameter
D he
F
G
Hg
Hf
H i n
AHg
A H i n
L
P
W*
x i n
x o u t
- 4 x flow area/wetted perimeter
Heated equivalent diameter '*- 4 x flow area/heated perimenter
Scaling factor
Mass flux
Enthalpy of saturated vapor
Enthalpy of saturated liquid
Enthalpy of liquid at inlet
"VH inInlet subcooling (- H f - H j n)
Heated length
Pressure
Reduced power number defined in equation (5)
Quality at inlet
Quality at outlet
Greek Symbols
"L
"t
"L
"g
Density of liquid phase
Density of vapor phase
Viscosity of liquid phase
Viscosity of vapor phase
(ft)
(ft)
-
(Ib/h.ft2)
(Btu/lb)
(Btu/lb)
(Btu/lb)
(Btu/ib)
(Btu/lb)
(ft)
(psia)
-
-
-
(lb/ft3)
(ib/ft3)
(lb/h.ft)
(lb/h.ft)
0 Critical heat flux (CHF)
X Latent heat of vaporization ( - H g - H f )
'''CHF C H F m o°eling parameterdefined in equation (3)
(h2ft3;ib.ft)
(Btu/h.ft2)
(Btu/lb)
Note:
Error (%) - 1 0 0
- 1 0 0
^predicted
^measured Jw+measured ~ ^predicted*]
{W+raeisured calculated from equation (5))
^predicted c a ' c u l a t e d f™"1 equation (9))
. / £ Error3
lo. of observations
Average error- £ ' E r f o r l
No. of observations
ATOMIC ENERGY OF CANADA LIMITED
MODELING OF CRITICAL HEAT FLUXIN UNIFORMLY HEATED ANNULI
S.'jf. Ahmad and D.C. Groeneveld
INTRODUCTION
Measurements of critical heat flux (CHF1) condi-tions for a given nuclear fuel channel are usuallyobtained from out-reactor loops using a similar testsection geometry. Heat generation in the reactor fuelis simulated by high heat flux electrical heatersequipped with dryout detectors. To reduce theexpense of CHF testing of full-scale fuel channels,studies have been made to scale down the electricalpower requirements of such loops [1] . Two methodshave been used.
(1) The critical power for dryout in simple geome-tries can be scaled down by using the samecoolant at the same conditions in a smaller-scaletest section. Half-size experimental set-ups haveresulted in a 70% saving in power [2 ] . However,evidence exists [3] that this scaling method maynot work well if applied to annuli or multi-rodbundles.
(2) The critical power of a steam—water system canbe scaled down by using a liquid with a lowerlatent heat of vaporization but the samevapor/liquid density-ratio as the original coolant[4,5]. Liquids which have been used to success-fully scale down the CHF are Freon-12,Freon-112 and Freon-22.
There are two main advantages in using Freon tomodel CHF conditions in boiling water at reactorcoolant conditions:
(1) The scaling factor for critical heat flux for waterat 1000 psia is approximately 18. Thus the testsection power of a Freon system will be only ~6% of that of an equivalent water system.
(2) Freon-12 at 155 psia and 112°F has been usedto scale critical heat flux in steam—water mix-
1 Other terms used to denote CHF: dryout heatflux, burnout heat flux.
tures at 1000 psia and 545°F. At these lowertemperatures and pressures loop constructioncosts are reduced considerably and visualizationstudies can be conducted. Visualization isparticularly helpful in dry patch, flow regime,instability, crossflow and void-distributionstudies.
The use of Freon to model CHF behaviour of highpressure water in tubes has proven accurate, simpleand inexpensive [6,7]. If the technique could be assuccessfully applied to annular geometries, it wouldthen be possible to extend it with greater confidenceto more complex geometries such as rod bundles.
Freon CHF data for annuli have not been exten-sively reported. A few results (17 points) in graphicalform are given in reference [8] for 155 psia only.Stevens et al. [9] reported 79 dryout points for anannuius 12 ft long, at pressures of 114 and 155 psia,and the range of mass flux from 0.66 to 1.65 x 106
lb/h.ft2.
The present investigation presents data for 418Freon dryout points for two 72 in. long annuli(shroud diameter 0.875 in., and rod diameters of 0.55and C.41 inches) within the pressure range of 90 to245 psia and mass flux range of 0.1 to 2.4 x 10s
lb/h.ft2. These results are compared with the waterdata of references [ 10] and [ 11 ] .
EXPERIMENTAL EQUIPMENT AND PROCEDURE
Freon-12 Loop
A schematic of the Freon-12 loop is shown inFigure 1. The Freon flow entering the pump isapproximately 30°F subcooled. The pump outletpressure is reduced from 310 psia to the approximatedesired pressure by a throttle valve located before thepreheaier of the test section. The test section outletpressure is kept constant by maintaining the pressurein the jet condenser with a pressure controller which
operates a three-way valve in the bypass. The testsection pressure was increased by throttling of thetest section outlet. Increasing the throttling at thepreheater inlet reduced the test section pressure. Toavoid vapor voids at the pump inlet the Freon waspressurized to at least 85 psia.
LIQUIDEIPKSIOH
SUBCOOLER
JET CONDENSER
SUBCODLED LIQUID
TIO PH1SE IIITURE
INLET r \ _TEMP. K~/
PRE-HEtTEflv---
BTPiSS
Figure 1 — Freon-12 Loop Schematic
Test Section
The test section consisted of a central heater and aconcentric 0.875 in. unheated shroud. Two heatersizes were used: 0.550 in. and 0.410 in. diameter. Thetotal heated length was 72.00 in. Nichrome V wasselected as the heater element material because of itslow temperature coefficient of resistance. A 50V1000 Amp SCR regulated DC power supply suppliedthe test section power.
Instrumentation
Dryout was detected by three thermocoupleswhich were embedded in the heater sheath near theoutlet, Vi in. upstream of the heated end.
Test section and bypass flows were measured byturbine flow meters. Inlet and outlet pressures wereindicated by a Heise-Bourdon-tube pressure gauge.
All measurements were converted to mV signals,then fed to a digital on-line computer and printed outin engineering units.
Experimental Procedure
After the loop was brought to operating pressurethrough the use of the expansion tank heater, therequired flow and inlet temperatures were esta-blished. The test section power was then raised to70% of the estimated dryout power and increased bysmall steps until dryout was obtained.
The power was consequently backed off 5% anddryout was again approached at a very slow rate. Atthe appearance of the first temperature spikescharacteristic of dryout, measurements were made,then the power was backed off, new operatingconditions were established, and the same procedurewas repeated.
EXPERIMENTAL RESULTS
A total of 418 CHF tests were done with the twoannular test sections. The following operating con-ditions were covered.
THREE I MYiLYE Outlet pressure range
Mass fluxInlet subcooling
: 90, 154 and 240 psia: 0.1 to 2.4 x 106 lb/h.ft2
: 0.7 to 18 Btu/lb
The critical conditions are tabulated in Table Al(Appendix). In 15 repeat tests the maximum diffe-rence in CHF was 1.5%.
CORRELATION OF FREON DATA AND COM-PARISON WITH PUBLISHED WATER DATA
The objective of doing CHF experiments with amodeling fluid such as Freon is to determine whetherthe behaviour of the prototype" fluid (in this casewater) can be accurately predicted from modelingdata.
Two modeling approaches have recently beenproposed:
(a) the scaling factor method [6,7 ], and
(b) the compensated distortion modeling technique[12].
The latter has been adopted here because of itsgenerality.
It was shown in reference [12] that the appli-cation of a general dimensional analysis to the theoryof models [13], in which many dimensionless groupsmust be made equal, leads to excessively restrictiveexperimental conditions. One of the solutions to thisproblem suggested by Murphy [13] is to compensate
The conventional modeling term for the physicalsystem for which predictions are to be made.
for an inequality in one dimensionless group byintroducing a controlled distortion in another.Applying this technique, Ahmad [12] showed thatCHF behaviour can be modeled if the followingcriteria are satisfied:
and
W/GX)
<L/D>n
prototype (0/GX) model . . . (1)
) = ( " L ^ m
(AHg/X)p - (AHg/X)m
<*CHF>
(independent
variables). . . (2)
where ^CJJF is a "critical heat flux modeling para-
meter" defined as
''CHF
On this basis Ahmad [12] derived the followingprediction equation, which b applicable to bothmodeling and prototype fluids:
. . . (3)
• (4)
where W , the reduced power number, is defined as
w + „ Power number 4L»/GXDhe X g u t - X m
Maximum power number AH- /X - X
and E+ = F (i/<CHF, L/D, AHin/X)
For the present analysis the following functional formwas assumed, i.e.,
in
. . . ( 5 )
. . . ( 6 )
. . . ( 7 )
W + = | l - e
where E = ^ J J J . ( L / D ) d
and a, b, c, d, g and f are constants to be determinedfrom the Freon data of Table A l .
By plotting data on a log—log graph die value of Twas first determined. The rest of the constants werethen optimized to yield minimum root mean square(iros) error. The resulting correlation is as follows:
-(8)
.(8a)
w + f _ ^ 0 . 0 2 5 ( p L / V l ) 0 - 2 6 6 .E.
where E
The above equation correlates the Freon data witha rms error of 6% within ±15% — shown in Figure 2.
Since correlation equation (9) should be applicableto both modeling and prototype fluids, it wascompared with water data of references [10] and[11]. Table 1 gives the range of parameters used in(a) developing correlation equation (9) from theFreon data, and (b) comparing equation (9) withwater data. The results of the comparison betweenwater data and equation (9) are shown in Figure 3. Itcan be seen that the rms error in correlating 233water data is only 8% and all data fall within ±15%.
TABLE 1. Range of Parameters for Freon and Water Data
Parameters
*CHF
PL">g
AHin/X
L/D
Source and RunNumber
Total Numberof Data
Freon-12(used in development
of equation (9))
1.68 to 32.9(Mass flux: 0.096 to2.39x10' Ib/h-ft2)
11.5 to 38(Outlet pressure:88 to 244 psia)
0.0148 to 0.368(Inlet subcooling:0.71 to 17.6 Btu/Ib
155 to 222(Hydraulic diameter;
0.335 to 0.465 in.Length: 72 in.)
Present investigation:Table AL
Runs 1 to 418
418
Water
3.86 to 71.9(Mass flux: 0.3 to6.2 xlO6 lb/h.ft7)
13.1 to 38.3(Outlet pressure:
599 to 1406 psia)
0.003 to 0.614(Intet subcooiing:2 to 400 Blu/lb)
140 to 216(Hydraulic diameter
0.25 to 0.50 in.Length: 36 to 108 in.
lief. [10]: Runs 303 to434, 455 to 477, 510 to531, 550 to 556 and 584
to 605.Ref . [ l l ] as reported
in[141:Runs759to785.
233
DISCUSSION AND CONCLUSION
It is evident from Figures 2 and 3 that thecompensated distortion model of reference [12] issuccessful for annular geometries. Comparison ofFigures 2 and 3 shows that the trend — as predictedby correlation equation (9) - i s similar for bothmodeling and prototype data. The rms errors are 6%for Freon and 8% for water, both within thedeviation of ±15%. Higher rms errors are to be
expected with water because
(a) there is greater scatter in water data
(b) the range of parameters for water data hasexceeded the range of validity of the correlation(see Table 1)
(c) water data were not used in the development ofthe correlation.
FREOH 12 DATAR.H.S. ERROR = bX TOTAL NO. OF POINTS = 118
1.00
WATER DATA
R.M.S. ERROR = 8S TOTAL NO. OF POINTS = 233
0.25 0 . 5 0 Q.75
MEASURED REDUCTED POWER NUMBER
1 . 0 0
Figure 2 — Comparison Between Prediction of Equa-tion (9) and Freon 12 Data
Although the intention of the present investigationwas not to present a CHF correlation for annuli, it isinteresting to compare the present correlation withthat of Bamett. From 724 reliable experimental data,Barnett [15] developed a CHF correlation (for waterflowing in annuli at 1000 psia) with a rms error of5.9%. Since the water data of reference [11] werenot used in the development of Barnett's correlation,and since the correlation equation (9) was developedfrom Freon data only, the water data of reference[11] were used as a basis for comparing the twocorrelations. The results of comparison are presentedin Table 2; it shows that (a) the error trends for thetwo correlations are remarkably similar, and (b) themaximum difference in predicted CHF between thetwo correlations is only 6%.
These encouraging results suggest that the dimen-sionless groups identified by Ahmad in reference
0.75—
0.50 h~
0.25—
0.25 Q.5Q Q.75
MEASURED REDUCED POWER NUMBER
Figure 3 — Comparison Between Prediction of Equa-tion (9) and Water Data References [10] and [11]
[12] and combined in the form of equation (9) forannuli, give a generalized correlation for bothFreon-12 and water, and possibly other fluids as well.The limitations imposed on the accuracy of thistechnique are those of experimentation and thecorrelation function used.
Finally, an estimate of the accuracy of thecompensated distortion modeling technique [12] wasobtained. For accurate modeling, the four modelingdesign criteria outlined in equation (2) must besatisfied. These criteria are approximately satisfiedfor the 14 pairs of Freon/water data shown in Table3. To compensate for any mismatch of parameters,correlation equation (9) was compared with both theFreon and the water data. The difference in the errorsbetween Freon and water data eliminates the errorintroduced by the correlating function, and *;hus givesan indication of the accuracy of the modelingtechnique. It can be seen from Table 3 that for anidentical annular geometry, the average error betweenFreon and water data is only 4% and the maximumerror does not exceed 6.5%. For pairs 11 and 13 thewater data are inconsistent. Hence these were notincluded in the comparison.
In summary it may be concluded that
(1) Accurate modeling of CHF in annuli can beachieved if the physical size of the model is
1.00
identical to the prototype — this is consistent TABLE 3. Estimation of the Accuracy of Modeling Technique
(2)
will
Fori me inn
annulai
lings u i ousveua miu iviauueui L d l -
: geometries, CHF correlationsobtained solely from modeling experiments cansatisfaprm-ilv nrpHirf. f!HF for nrototvnps.
TABLE 2. Comparison Between Barnett's [15] Correlation and Equation (9)
1000 psia water data of ref. [11] as reported in ref. [14]. Shroud dia. - 0.607,Rod dia.
RunNo.
759
760
761
762
763764
765766767
768
769
770
771
772
773
774
775
776
777
778
779
780
781
782
783
784
785
- 1.053
MassFlux106lbruft2
0.498
0.499
0.503
0.513
0.514
0.522
0.5230.5280.529
0.533
0.793
0.808
0.8160.991
1.0071.021
1.4771.479
1.480
1.4831.489
1.493
1.9301.971
2.419
2.441
2.480
; Length - 72 in.
InletSub-coolingBtu/lb
93
2
176
38
93
114
4147
67
36
72
113
44
78
117
51
14
75
119
45
128
39
113
73
57
17
120
Total No. of Data 27
MeasuredCHF
106 Btuh.ft2
0.521
0.398
0.637
0.470
0.520
0.564
0.4010.643
0.491
0.455
0.653
0.722
0.613
0.757
0.866
0.718
0.718
0.889
1.011
0.813
1.050
0.792
L064
0.961
0.942
0.771
1.141
% Error in Predicting CHFfrom
Barnett's [ 15 J CorrelationCorrelation Equation (9)
-14.3
-14.7
-14.0
-10.2
-16.3
-13.9
-16.9- 8.7
-16.4
-15.1
- 5.3
- 8.3
- 3.4
- 0.5
0.2
2.6
9.2
3.6
0.5
6.9
1.1
6.8
- 1.9
3.5
3.3
7.1
- 1.2
-13.4
-11.7
-16.7
- 7.5
-15.0
-13.4
-13.2- 9.5
-13.9
-11.7
0
- 4.7
2.8
5.1
3.8
8.9
14.8
9.1
3.9
12.9
3.9
12.9
1.6
8.8
8.7
10.8
- 4.5
Maximum difference between
two correlations * 6%
Pah-
No.
1
2
34
5ao78
9
10
11
12
13
14
Test Section:
Shroud dia. - 0.875 in.Heated length = 72 in.
Freon Data (Table Al)(Rod dia. •
Run No.
1
2
34
5ctD
78
9
10
11
12
13
14
* 0.55 in.)
% Error ofEquation (9)
(EF)
3.6
-1 .5
1.30.8
0.5
0.2-5.8
2.6
0.9
L3
5.2
4.3
3.1
-4.8
} "L'P8, ~20
Water Data [10)(Rod dia.
Run No.
303
304
305308
309
310312316
317
318
321
322
325
326
(*Water data inconsistent with each other -
flux for constant inlet subcooling)
- 0.54 in.)
% Error ofEquation(9)
( % )
-2.9
0.9
-3.9-2.2
-2.6
-3.4-5.25.0
-2.6
-5.0
-2.8
-0.5
11.6
- L 4
AbsoluteDifference
in Error
EU - lEm -E 1
%
6.5
2.4
5.23.0
3.1
3.60.6
2.4
3.5
6.3
8.0*
4.8
8.5*
5.4
CHF increases with decreasing mass
REFERENCES
[I] P.G. Barnett, "The scaling of forced convectionboiling heat transfer," AEEW-R-134,1963.
[2]G.J. Kirby, "The scaling of burnout data for asingle fluid at a fixed pressure," AEEW-M-696,1966.
[3] G.F. Stevens and R.V. Macbeth, "The use ofFreon-12 to model forced convection bumout inwater: The restriction on the size of the model,"ASME Paper 70-HT-20,1970.
[4] P.G. Bamett, "An experimental investigation todetermine the scaling laws of forced convectionboiling heat transfer. Part 1: Preliminaryexamination using burnout data for water andArcton-12," AEEW-R-363,1964.
[5] P.G. Bamett and R.W. Wood, "An experimentalinvestigation to determine the scaling laws offorced convection boiling heat transfer. Part 2:An examination of burnout data for water,Freon-12 and Freon-21 in uniformly heatedround tubes," AEEW-R-443,1965.
[6] G.F. Stevens and G.J. Kirby, "A quantitativecomparison between burnout data for water at1000 psia and Freon-12 at 155 psia,"AEEW-R-327,1964.
[7] D.C. Groeneveld, "Similarity of water and Freondryout data for uniformly heated tubes," ASMEPaper 70-HT-27,1970.
[8] G.F. Stevens and R.W. Wood, "A comparisonbetween burn-out data for 19-rod cluster test-sections cooled by Freon-12 at 155 psia, and bywater at 1000 psia in vertical upflow,"AEEW-R-468,1966.
[9] G.F. Stevens, R.W. Wood and J. Pryzbylski, "Aninvestigation into the effects of a cosine axialheat flux distribution in a 12 ft. long annulususing Freon-12," AEEW-R-609,1968.
[10] E. Janssen and J.A. Kervinen, "Burnout condi-tions for single rod in annular geometry, waterat 600 to 1400 psia," GEAP-3899,1963.
[ I I ] D.F. Judd and R.H. Wilson, "Non-uniform heatgeneration experimental programme. Quarterlyprogress report No. 9," BAW-3238-10,1965.
[12] S.Y. Ahmad, "Fluid to fluid modeling of criticalheat flux —A compensated distortion model,"AECL-3663,1971.
[13] G. Murphy, "Similitude in engineering," TheRonald Press Co., New York, N.Y., pp. 57,107,1950.
[14] P.G. Bamett, "A comparison of the accuracy ofsome correlations for burnout in annuli and rodbundles," AEEW-R-558,1968.
[15] P.G. Bamett, "A correlation of burnout data foruniformly heated annuli and its use for pre-dicting burnout in uniformly heated rod bun-dles," AEEW-R-463,1966.
APPENDIX
TABLE Al
Freon-12 Critical Heat Flux Data in Uniformly Heated Annuli
Shroud dia.
No.
12345
6789
10
11121314IS
1617181920
2122232425
Outlet
psla
154153154153153
154156155152153
156155153155154
8889939493
89928890
155
- 0.875
Mass
10*lbh . f t '
0.7540.7290.7520.7340.737
0.7420.3781.1370.7460.737
1.1471.1320.9490.3770.198
0.3950.5860.7950.9841.185
0.2060.4140.5940.7740.099
Inches;
Inlet
coolingBtu/lb
3.303.148.213.706.99
9.255.362.083.586.27
3.866.973.134.527.60
2.062.754.294.434.49
2.262.822.282.749.93
Rod dla
CHF
10*Btuh.ft"
3.49113.26084.17253.42553.9158
4.27412.70613.65543.42793.B352
4.11254.70983.68582.65472.1198
2.55083.15533.69694.22274.5692
1.82592.53743.08503.54051.5470
. - 0.550 Inches;
Exit
X
2 3 .2 2 .2 0 .2 2 .2 0 .
1 9 .3 5 .1 6 .2 2 .2 1 .
1 5 .1 3 .1 8 .3 6 .5 4 .
3 3 .2 6 .1 9 .1 7 .1 4 .
4 7 .3 0 .2 5 .2 1 .8 1 .
3359048079
4471605241
6852874702
5734663771
1769977205
No.
2627282930
3132333435
3637383940
4142434445
4647484950
Outlet
psla
154154155154153
155156153155154
15415415 3154152
153153157154156
155153153152153
Heated length
Mass
10'lbh.fc'
0.1010.1000.0990.0960.104
0.2030.2030.1970.1970.199
0.1950.40 30.3950.3940.401
0.4050.3830.6020.5960.597
0.5990.5890.6030.7990.774
-
Inlet
coollnjBtu/lb
8.6 .4 .2 .0 .
9 .8 .6 .3 .2 .
1 .9 .8 .6 .3 .
2 .1 .9 .8 .6 .
4 .2 .198
5569296185
3854109142
1643005380
2907933391
3250807914
72 Inches
CHF
10* Btuh.ft'
1 .1.1 .1 .1.
2 .2 .2 .2 .2 .
1.3 .2 .2 .2 .
2 .2 .3 .3 .3 .
3 .2 .2 .4 .4
43684810404428232424
23923833209304200715
B54007519724869 75532
395230 329734856S5590
1738B2198440461?3657
ExitQuality
Z
7 4 .8 1 .8 2 .80 .7 4 .
5 2 .5 8 .5 9 .5 8 .6 0 .
58 .3 1 .3 2 .3 4 .3 3 .
3 3 .3 6 .2 3 .2 5 .2 5 .
2 5 .2 5 .261720
6882381139
8197897415
3404992239
3425626914
7181642872
Shroud dia.
RunNo.
5152535455
5657585960
6162636465
6667686970
7172737475
OutletPress .
psia
155155154153155
153154155154156
152155155156152
155154155157157
157157152154153
-
HF
0 .0 .0 .0 .1.
0 .0 .0 .01
11111
11111
11111
0.875
a B S
5820804799782002
9959869879B5023
183185190199181
182414
.379
.373
.365
.371
.386
.602
.604
.597
inches;
InletSub-coolingBtu/lb
6 .4 .2 .1 .9 .
86421
98742
19875
32986
7815785046
7588408493
4476056077
8580
. 85
.49
.07
. 2 8
. 3 1
.44
.65
.60
Rod dia. - 0.550 Inches;
CHF
10*Btuh . f t '
4 .3 .3 .3 .5 .
4 .4 .4 .33
55443
36554
44665
05246238430622440326
73155553052470125211
35263849832343689869
76560348
.6856
.3589
.5763
.3061
.1354
.3279
.0787
.2767
ExitQuality
Z
18.8621.0122.1623.4114.39
13.9516.5917.9618.6418.37
11.2112.6212.7515.0316.29
16.878.939.78
10.9511.96
13.9314.76
7.558.028.73
RunNo.
7677787980
8182838485
8687888990
9192939495
96979899
100
OutletPress.
psla
156157157155152
155156158155156
154156155156154
153153156158156
154157157159237
Heated length -
MassFlux
10h.
1 .1 .1 .1 .1 .
1 .1 .1 .12
12112
22222
22220
"lbf t '
5 8 1567537776801
768784770983008
962007991994175
181207159
.151
.403
.377
.360
.341
.365
.101
nletub-oollngtu/lb
4.833.692.57
10.068.52
7.264.733.939.588.69
7.245.453.662.929.78
8.587.014.783.669.11
7.665.524.003.14
17.45
72 inches
CHF
lO'Btuh.ft '
4.74584.57154.22676.81196.3232
5.89934.93704.83627.01936.6546
5.89025.26604.80344.65417.06436.72773.95905.09584.93816.97466.33745.48375.05034.81571.7892
EiltQuality
I
10.1511.7412.775.706.47
7.748.83
10.134.704.94
5.636.568.569.442.483.664. 146.157. B51.532.724.536. 307.17
89.86
APPENDIX
TABLE Al
Freon-12 Critical Heat Flux Data in Uniformly Heated Annuli
Sh
No.
101102103104105
106107108109110
111112113114115
116117118119120
121122123124125
roud dla
psia
237237236238238
2402342372 392 39
238237238240237
235237238237240
23923B2 392402 38
0.87
10' lbh .
0 .0 .0 .0 .
f t '
10009 70 9 8099
0.102
0 .0 .0 .0 .0 .
0 .0 .0 .0 .0
0 .0 .0 .0 .0
00000
118111208203191
20420620S210210
40 340240039639 8
606600602601601
5 inchea
coolingBtu/lb
1 3 .9 .7.6 .4 .
21
1613
9
75421
1613
984
171310
86
3089993811
6528750047
6680216930
466160
. 0 826
63. 6 304
. 2 8
. 4 0
Rod d
Cat
10'Btuh . f t '
1 .1 .1 .1 .1 .
11222 .
21111
33322
54333
6434545850594 7003681
31003566576944501455
18389930941781056940
83605645056570653873
.347461628119
.3888
.0763
l a . > 0 .
Exit
1
8 9 .9 2 .929287 .
7384535860
6056585654
3334343134
2626242323
3496725508
900 3378643
3779760878
43814885
. 0 0
. 1 9
. 4 5
.26
.04
. 1 6
550 i
S o .
126127128129130
131132133134135
136137138139140
141142143144145
146147148149150
aches;
Ou t le t
psia
237239238238239
23723823823B241
2412382332382 39
2382402402402 39
2342 39241237
.240
ieated
Haas
lO'lbh.
0 .0 .0 .0 .0 .
0 .0 .0 .0 .1.
1.0 .1.1 .1.
1 .0 .1 .1 .1 .
11111
f t '
576783797794798
797792795787002
004988026023012
02598219 8195175
194181226212231
1ength •
Inlet
coolingBtu/lb
3171310
8
6421
16
1610
864
21
1714
9
76422
. 8 1
. 5 4
. 7 3
. 0 0
. 4 3
. 6 1
. 4 2
. 4 4
. 3 1
. 8 9
. 1 4
. 1 6
. 4 3
. 3 3
. 0 3
. 7 8
. 4 4
. 3 5
. 2 0
. 8 1
. 9 4
. 5 4
. 8 4. 6 9. 1 3
72
10.1 •
26543
33226
65433
327o5
44433
inche
*H V.HIT
"DtuIP^.7274.0494.2234.2417.9880
.5736
.1308
.8373
.6484
.6408
.14 70
.2364
.6012
.9809
.4409
.2900
.9313
.2804
.2742
.2020
.7845
.4562
.0268
.3706
.0395
s
Quality
:
25.8018.5718.1217.2318.09
18.1818.9920.3521.2712.09
14.2416.6214.4114.5515.87
17.1118.34
7.197.86
11.15
11.9513.3013.3914.2013.22
Shroud dia
RunNo.
151152153154155
156157158159160
161162163164165
166167168169170
171172173174175
OutletPress .
psia
239240240238238
240241238241239
2372402 362372 36
236237238235236
2352 362362332 39
H
0.875 Inche:
as 8Flux
10h7
1 .1 .1 .1 .1 .
1 .I .1 .1 .1 .
1 .1 .1 .1 .1 .
I .1 .1.12 .
1 .11 .11
' l b
418384361390393
419393396616587
5735746 0 3588585
5739 8 19709670 2 3
8318047799 76S76
InletSub-coolingBtu/lb
1 6 .1 4 .1 0 .
8 .6 .
4 .2 .I .
16 .1 2 .
9 .8 .5 .4 .2 .
I .1 5 .1 3 .
7 .5 .
4 .3 .0 .
1 6 .1 3 .
8016196032
3496786983
8444791426
4478349292
4475715765
; Rod dla.
CHF
10h.
7.6 .5 .5 .4 .
4 .3 .3 .8 .7 .
6 .5 .4 .4 .3 .
3 .8 .7.6.5 .
4 .4 .3 .8 .7
"Btuf t 2
75299940757136167414
24367743535720683464
18066394494523024354
5B356516976919724371
70033665639686615723
» 0
ExitQuality
Z
3 .6 .8 .9 .
1 1 .
1 2 .1 3 .1 4 .
1 .6 .
7.7.7 .
1 0 .1 0 .
1 3 .- 1 .
1 .5 .6 .
4 .9 .
1 3 .- 2 .- 1 .
9654955810
3221354327
49969 13672
2176069480
8742075 313
550 Inches;
RunNo.
176177178179180
181182183184185
186187188189190
191192193194
OutletCress.
psla
240242240241241
239241241240241
240235240244239
238237240242
Repeats*
195/3196/5197/12198/13199/14
153155157153152
Heated
MassFlux
10h.
1.1.21.1
12222
22222
2222
00100
' l bf t z
9 869670089 869 88
982180173191170
19420339 3392380
349258241255
.743
.745
.125
.933
.374
length =
InletSub-coolingBtu/lb
1 0 .a.4 .6 .2 .
1 .1 6 .10
8 .6
24
1610
8
5433
87734
0538265441
5954311267
6410385622
95008023
.0918
. 0 720
. 2 2
72 inches
CHF
10i.
6 .6 .5 .5 .4 .
4 .96 .6 .5
45976
5544
44532
-Btu-UT-
63251134072552524566
36371494695729957101
55420883553102053374
76661404504086 70
.21641358
.1783
.9442
.6461
ExitQuality
Z
2 .4 .9 .6 .
1 1 .
1 2 .- 4 .
0 .3 .4 .
9 .7.
- 5 .- 1 .
1.
5 .7.6 .8
2122162037
8772162201
4058485889
3190711086
09894270
0400209209
APPENDIX
TABLE Al
Freon-12 Critical Heat Flux Data in Uniformly Heated Annuli
Sh
RunNo.
20020120220 3204
20520620720 8209
210211212213214
215216217218219
220221222223224
roud d i a
Press.
psia
155154154155154
155154154155155
154157
9091
118
118185188186185
219217216217214
. - 0.81
FluxlO6lbh . f t !
0.7280.7600.7590.7630.763
0.7611.1091.1141.1431.106
1.1030.3520.7380.3410.741
0.7360.7390.7350.7350.74S
0.7280.7290.7360.7341.110
5 inches
Sub-coalingBtu/lb
2 .4 .7.
1 0 .1 1 .
1 2 .2 .4 .8 .
10 .
9 .4 .4 .4 .7 .
2 .3 .
1 2 .1 4 .1 4 .
8 .1 2 .15 .16 .1 1 .
1884606291
6022947286
7359035663
6015349748
8375082657
• Rod c
CHF
lO'Btuh.Ft 2
4 .4 .5 .6 .6 .
6 .4 .5 .6 .7.
7.3 .4 .3 .5 .
4 .4 .7.7.7 .
5 .6 .8 .8 .7.
09448162621746857918
99215178532695085804
39125056758957667801
41231786012812148612
67319216313334566365
l a . - 0.
ExitQuality
Z
16.6614.2913.0911.4410.56
10.3510.859.0B6.155.00
6.5328.2114.6727.2613.75
16.3215.5612.698.11
12.36
13.3412.1714.6312.574.09
410 i
No.
225226227228229
230231232233234
2 35236237238239
240241242243244
245246247248249
aches;
Outlet
psia
21B215219219215
216154155157155
155155156155156
154154156158155
155155154
8991
Seated
Haas
10'lbh .
1 .1 .1 .1 .1 .
I .0 .0 .0 .0 .
0 .0 .0 .1 .0 .
0 .0 .J.1 .1 .
0 .0 .0 .0 .0 .
ft2"
10310310 5109111
110747745741743
74373636 7133754
7497 35144150152
957382199102341
length -
Inlet
coolingBtu/lb
9 .B.6 .3 .2 .
9 .3 .3 .8 .3 .
6 .9 .5 .2 .2 .
3 .6 .3 .7.
1 2 .
3 .6 .7.3 .4 .
3509759935
7350407797
5981686814
7937495968
4566885756
72
10.i .
66544
74464
56344
45568
43313
Inches
:HF
•Btu
756339499089
.91842 839
.03614065
.4796
.0409
.5740
.4500
.2603
. 7584
.6831
.1341
.6153
.2751
.0806
.7022.9980
.8432
.9841
.2162
.9613
.5766
Exit
t
5 .6 .7.9 .
10 .
5 .15 .1 5 .1 3 .1 5 .
1 4 .1 3 .2 7 .1 0 .16 .
1 5 .1 4 .
9 .7.5 .
1 2 .264 4 .5727
5879756865
6617807126
720 318232 2
6253863414
22008 0B926
Shroud dla
RunMo.
250251252253254
255256257258259
26026126 2263264
265266267268269
270271272273274
OutletPres s .
psia
929291
100100
98100
888992
92102102104103
157157155155157
1S6154154154156
H
0.875 Inches;
M BFlux
10h .
0 .0 .0 .1 .1 .
1 .1 .0 .0 .0 .
0 .1 .1 .1 .1 .
0 .0 .0 .0 .0 .
c.0 .0 .0 .0
• l bf t T
4 1 1606807027212
390543206410608
801017187414592
102102103103106
101204208206208
InletSub-coolingBtu/lb
34 .44 .5
56122
33444
98632
18642
9326179706
4004923794
11924B9997
866555
.90
.85
. 8 5
. 0 8
.40
. 3 6
.74
Rod dia.
CHF
10h .
3 .4 .4 .5 .5 .
6 .6 .2 .3 .4 .
4 .5 .5 .5 .6 .
2 .22 .22
23322
*Btuf t *
69113731B06161066545
193555496969563S1993
47493185068997043154
49823641298914471362
14361993177091428342
- 0.
ExitQuality
231612
97
54
402418
1311
654
7269696969
7442444345
C
. 3 3
. 9 1
. 8 1
. 9 8
. 1 3
. 8 2
. 0 3
. 1 7
. 8 9
. 1 0
. 3 9
. 0 3. 8 1. 7 9. 9 4
. 0 4
. 4 1
. 9 8
. 4 2
. 0 6
. 7 9
. 6 3
. 2 6
. 8 9
. 1 4
410 inches:
RunNo.
2752762772782 79
2802B1282283284
2852862872882B9
290291292293294
29529629 7298299
OutletPress .
psia
157153155154153
155155155156157
155156156153155
1*4154154156155
156155155157155
leated
MassFlux
1Ch .
0 .0 .0 .0 .0 .
00000
00000
00001
11111
• l bf t *
210415415412412
410411597598599
594593602825824
818829812
.B23018
.034
.039
.026
.047
.031
length •
InletSub-coolingBcu/lb
1 .9 .8 .6 .4 .
21987
43198
64219
87431
6127515512
6945625610
1503346149
8421658064
. 8 6
.12
. 5 9. 3 1.76
72 inches
CHF
10h .
2 .4 .4 .4 .3 .
3 .3 .5 .5 .4 .
4 .3 .3 .6 .6 .
5.4447
66544
*Btuf t 2
71765570406007956561
45152385545436419831
24439788585661001818
7107872337 7910021861
96303212338789623631
ExitQuality
X
4 4 .2 3 .2 3 .2 4 .2 4 .
2 6 .2 6 .16 .17 .17 .
1 8 .19 .1 9 .1 1 .1 1 .
1 2 .131415
8.
89
101112
7612232395
01?028114 4
5 90 8455781
9579910103
3014620829
APPENDIX
TABLE Al
Freon-12 Critical Heat Flux Data in Uniformly Heated Annuli
Shroud dia
BunHo.
300301302303304
305306307308309
310311312313314
315316317318319
320321322323324
OutletPress.
psifl
156157155155158
155154154158158
15715 8155156156
15 7157156153155
159153155159238
- 0.875 Inches;
HaasFlux
10h .
1 .1 .1 .1 .1 .
1 .1 .1 .1 .1 .
1 .1 .1 .1 .1 .
1 .
' l bf t 7
2052062 0 11972 1 3
20039 7402396390
3923 9 1615597607
6091.6111 .1 .1 .
1 .1 .1 .10
607805808
777788795790105
InletSub-coollr.gBtu/lb
9 .8 .7 .4 .3 .
2 .9 .
a.7.4 .
3 .2 .9 .8 .7 .
4 .3 .1 .
1 0 .9 .
7 .4 .2 .1 .
17
9181164458
0235961289
2834686700
5704820532
1012549321
10h .
7 .7 .6 .5 .5 .
4 .7.7 .6 .5 .
5 .4 .8 .7 .7 .
6 .5 .4 .
Bod
CHF
*BtuTt5"
68532873656148341066
512070 86531693339868
10767054082260740801
000631648013
8.08067.
7 .5 .542
8676
19629794233293338797
dia. - C
ExitQuality
J
5 .5 .7 .8 .8
102 .356
780
0485076086
0 890070578
431339
1.393
567
- 2- 1
1466
77
19
235062
. 2 434
69. 6 3. 0 0. 5 9. 1 3
.410
RunNo.
3253263273283 2 9
330331332333334
335336337338339
34034134234 3344
34534634 7348349
Lnches;
Press.
psia
238237236240240
239237237239238
2402382 39236237
2 39237237236238
238236240238•237
Heated
Flux10 "lbh
00000
00000
00000
00000
00000
. f t 2
.104
.103
.10 3
.102
.105
.124
.207
.206
.207
.205
.205
.206
.206
.210
.410
.409
.'.08
.40 7
.403
.418
.416
.405
.613
.598
.593
length -
Sub-coolingBtu/lb
1 2 .9 .7 .5 .2 .
1 .1 7 .1 3 .
9 .8 .
6 .3 .2 .1 .
1 7 .
1 3 .9 .8 .6 .3 .
2 .0 .
J.713
9
6571848727
7837368008
3378314647
9 374143386
4089641 868
72 inches
CH?
10'Btuh
22222
23333
22225
54433
32665
. f t 2
.5485
.4107
.3339
.2237.1442
.1643
.9327
.5422
.1823
.0090
.8728
.6492
.4817
.4484
.8602
.2057
.3328
.0000
.6058
.2555
.0271
.7790
.8278
.3567
.2470
ExitQuali ty
J
7 4 .7 6 .7 6 .7 7 .7 9 .
6 8 .4 1 .4 2 .4 1 .4 3 .
4 4 .4 5 .4 4 .4 4 .2 2 .
2 3 .
5509868971
3497949561
6908938744
442 3 . 4 22 3 .232 4 .
2 5 .2 6 .
91616
506704
0 135143426
Shroud dia
RunN o .
350351352353354
355356357358359
360361362363364
365366367368369
370371372373374
OutletPress.
psia
237239240237237
238238240238237
238240237236237
236238237236237
240239237236237
. - 0.875 inches
HaasFlux
10'lbh.ft2
0.6010.6000.6120.6000.602
0.8260.8220.8230.8190.821
0.8230.8241.0291.0331.031
1.0291.0371.1961.2181.212
1.2161.2191.4101.4081.402
InletSub-coolingBtu/lb
8.206.424.132.631.18
13.4210.008.456.374.11
2.541.748.066.224.19
2.70l . / I8.196.564.32
2.921.866.264.232.71
; Rod dia. - 0
CHF
10*Btuh.ft2
4.92324.53483.95023.51043.0758
7.56556.3016S.75475.19774.4425
3.92433.65986.18875.60844.8877
4.3048?-93066.38325.9i435.15.'7
4.62274.19-16.11355.39654.7552
ExitQuality
Z
16.6317.7818.0418.5918.56
9.7510.7311.2412.8613.72
14.3414.71
7.979.37
10.77
11.5812.044.916.368.49
9.6010.314.816.968.32
410 inches; Heated le
RunNo.
375376377378379
330381382383384
385386387
Repeats
388/205389/202390/200391/206392/209
393/211394/288395/310396/322397/312
OutletPress.
psia
2372332362352 36
236235234235236
237339235
157157155157155
154157162158154
MassFlux
106 lbh . f t 2
1.4111.6221.6251.6071.622
1.6151.6191.8561.8171.80 3
1.7651.7631.782
0.7380.7370.7321.0791.104
0.3500.8261.3981.7981.622
ngth -
InletSub-coolingBtu/lb
2.749.858.556.624.26
2.731.91
10.128.306.51
4.763.452.36
12.967.892.172.67
10.92
4.1410.03
3.202.83
10.34
72 inches
CHF
10*Btuh . f t 2
4.32607.50416.97996.40765.5841
4.93804.65887.85227.06846.4452
5.739 35.25764.8734
7.05315.63233.92804.58097.8029
3.44686.61325.03875.10508.1336
ExitQuality
Z
6.90-1.47-0.13
2.615.28
6.897.84
-3.65-1.26
1.15
3.466.106.32
11.0713.4615.7210.695.68
28.5110.81
7.375. 19
-0.80
10
APPENDIX
TABLE Al
Freon-12 Critical Heat Flux Data in Uniformly Heated Annuli
Shroud dia.
Run;io.
398/314399/317400/311401/308402/306
403/257404/382405/236406/235407/233
408/234409/232410/231411/240412/241
4i.3/243414/242415/245416/237417/246
418/247
OutletPress.
psia
158156153154156
892 39158157153
154155154155156
15415415415 4156
155
- 0.875 inches
HaasFlux
10t .
1.1 .1 .1 .1 .
0 .1000
00000
1A000
0
Mbf t 2
59360740 3405400
2058237377 34740
740748747744746
.132135
.942
.370
.384
.198
n l eub-
c
cool ingtu/lb
7.2 .1.6 .
10
31010
7a
33336
63345
7
*(Run a/b indicates thatof Run b)
7616799403
3141281925
9471
.50
.80
.45
. 9 3
. 4 1
.19
.26
. 3 4
.79
Run
; Rod
CKP
10a.
7 .4 .4 .6 .7.
2 .7 .6.55
44445
64433
3
a
*Btuf t 2
24607600598483749731
83796932373735146858
5 3005130406548762587
29959428
.6593
.4510
.3964
.1511
dia. • 0.410 inches; Heated length « 72 inches
ExitQuality
2
2 .6 .8 .4 .2 .
4 0 .- 4121312
1515151513
79
122622
44
Ls repeat
3089719929
3933754889
17311712
. 9 5
. 5 6
. 6 8
. 2 6
. 3 7
. 6 4
. 0 8
11