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European Atomic Energy Community - EURATOM abi ­*­

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FIAT SpA, Sezione Energia Nucleare -

Società ANSALDO SpA - Genova

J W I ^ J C I ­ Ì ·

FORCED CONVECTION BURNOUT AND

HYDRODYNAMIC INSTABILITY

™ " EXPERIMENTS f

FOR WATER AT HIGH PRESSURE Part IV : BURNOUT EXPERIMENTS IN A DOUBLE CHANNEL TEST

SECTION WITH TRANSVERSELY VARYING HEAT GENERATION

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A. CAMPANILE, G. GALIMI and M. GOFFI

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1968

(SORIN, Centro Ricerche Nucleari, Saluggia-Italy)

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LEGAL NOTICE

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1

This document was prepared under the sponsorship of the Commission of the European Communities.

HÍ»;ÕÍÍ*l&lk-',Íá!^f

,i!í^'M'!ffi Neither the Commission of the European Communities, its

contractors nor any person acting on their behalf :

Make any warranty or representation, express or implied, with respect to the accuracy, completeness, or usefulness of the information contained in this document, or that the use of any information, apparatus, method, or process disclosed in this document may not infringe privately owned rights ; or

i Assume any liability with respect to the use of, or for damages

resulting from the use of any information, apparatus, method or process disclosed in this document.

m

EUR 3881 e F O R C E D CONVECTION B U R N O U T A N D H Y D R O D Y N A M I C I N S T A ­BILITY E X P E R I M E N T S FOR W A T E R A T HIGH P R E S S U R E P a r t IV : B U R N O U T E X P E R I M E N T S IN A D O U B L E CHANNEL·

T E S T SECTION W I T H T R A N S V E R S E L Y V A R Y I N G H E A T G E N E R A T I O N

by A. C A M P A N I L E , G. C A L I M I and M. G O F F I (SORIN, Cent ro Ricerche Nuclear i , Sa luggia — I ta ly ) European Atomic E n e r g y Communi ty — E U R A T O M F I A T SpA, Sezione Energ ia Nucleare — Torino Società A N S A L D O SpA — Genova Cont rac t No. 008-61-12 P N U Brussels , F e b r u a r y 1968 — 36 P a g e s — 13 F igu res — F B 50

Expe r imen t s have been carr ied out on a complex geomet ry test section consis t ing of two h e a t i n g rods coaxially mounted in two adjacent and communica t ing flow channels .

EUR 3881 e F O R C E D CONVECTION B U R N O U T A N D H Y D R O D Y N A M I C I N S T A ­BILITY E X P E R I M E N T S FOR W A T E R AT HIGH P R E S S U R E P a r t IV : B U R N O U T E X P E R I M E N T S IN A D O U B L E C H A N N E L

T E S T S E C T I O N W I T H T R A N S V E R S E L Y V A R Y I N G H E A T G E N E R A T I O N

by A. C A M P A N I L E , G. GALIMI and M. G O F F I ( S O R I N , Cent ro Ricerche Nuclear i , Sa luggia — I ta ly ) European Atomic E n e r g y Communi ty — E U R A T O M F I A T SpA, Sezione Energ ia Nucleare — Torino Società A N S A L D O SpA — Genova Cont rac t No. 008-61-12 P N U Brussels , F e b r u a r y 1968 — 36 P a g e s — 13 F igu res — F B 50

Expe r imen t s have been carr ied out on a complex geome t ry test section consis t ing of two h e a t i n g rods coaxially mounted in two adjacent and communica t ing flow channels .

Several conditions of differential heating in the two channels were tested to the aim of investigating the effect on burnout limits of possible variations of local flow velocity and fluid enthalpy due to transverse flow redistribution and mixing.

Several conditions of differential heating in the two channels were tested to the aim of investigating the effect on burnout limits of possible variations of local flow velocity and fluid enthalpy due to transverse flow redistribution and mixing.

EUR 3881 e

European Atomic Energy Community - EURATOM

FIAT SpA, Sezione Energia Nucleare - Torino Società ANSALDO SpA - Genova

FORCED CONVECTION BURNOUT AND HYDRODYNAMIC INSTABILITY

EXPERIMENTS FOR WATER AT HIGH PRESSURE

Part IV : BURNOUT EXPERIMENTS IN A DOUBLE CHANNEL TEST SECTION WITH TRANSVERSELY VARYING HEAT GENERATION

by

A. CAMPANILE, G. GALIMI and M. GOFFI (SORIN, Centro Ricerche Nucleari, Saluggia-Italy)

1968

Contract No. 008-61 -12-PNII

SUMMARY

Experiments ha\-e been carried out on a complex geometry test section consisting of two heating rods coaxially mounted in two adjacent and communicating flow channels.

Several conditions of differential heating in the two channels were tested to the aim of investigating the effect on burnout limits of possible variations of local flow velocity and fluid enthalpy due to transverse flow redistribution and mixing.

KEYWORDS

HEATING ENTHALPY BURNOUT VELOCITY MOCKUP COOLANT LOOPS FLUID FLOW TESTING

TABLB DES HATIÜEES

Page

1. Introduction 5 2. Test section 5 3. Control of the subchannels geometrical symmetry . . 8 4. Burnout experiments 10

4.1* Hange of parameters 10 4.2. Burn-out data presentation 10

5. Bemärks 11 Bibliography ^

rOKCED CONVECTION BURNOUT AND HYDRODYNAMIC INSTABILITY EXPERIMENTS FOR WATER AT HIGH PRESSURE^*'

1. Introduction

The flow passage of an open lattice core, with rod bundle type fuel elements, consists of non circular channels bound­ed by fuel rods each having connections with the neighbouring channels through the gap between the rods.

Several factors may contribute to set-up non uniform tran­sverse conditions in a matrix of fuel rods and coolant chan­nels, namely:

- Radial flux distribution - ilux peaking - Dimensional tolerances and deformations - Fuel loading variations - Inlet flow differences - Presence of non fueled reis (cluster centrei).

To the purpose of investigating possible influences of transversally unbalanced conditions existing in adjacent chan neis an experimental study has been carried-out by SORIN un­der the research and development contract between EURATOM-FIAT and Ansaldo for nuclear ship propulsion.

The experiments were performed on the SORIN pressurized water loop described in detail in réf. /Î/·

Pig. 1 shows a schematic diagram of the loop .

2. Test section

The investigation on the influence of transverse shift of flow upon the burnout in subchannels of a rod cluster fuel

Manuscript received on December 12, 196?.

6 -

assembly, was performed in a test section consisting of two adjacent and communicating channels with provision for dif­ferential heating in the two channels.

Each channel had a heater rod in axial position. The perimetral conteur of the flow duct, hereafter referred to as the shell,was shaped as to simulate the configuration of the flow area associated with two fuel rods in a rod bundle (Fig. 2) . It was suitably designed to have heat generation practically in the curved section only of the containment wall.

This was achieved by brazing, in a controlled atmosphere furnace, four quarters and two halves of stainless steel tubes, 1 mm thick, to very thin stainless steel strips, 0.18mm thick.

The corrugation of the thin strips observed in the prelimi­nary specimens ¿2/ was considerably reduced by improving the technique of fastening the various parts in the furnace.

Stainless steel discs were brazed at each end of the shell to allow connection to the electrical power connectors.

The heater rods consisted of two stainless steel tubes 10.2mm O.K., 1mm thick, internally provided with four thin stainless steel wires welded to the tube walls at the entrance, the exit, the mid point and 10 mm upstream of the exit end of the heated length. The wires were used as voltage taps for voltage drop measurement as well as for burnout detection by means of a bridge type detector .

The heater rods were centralized in each subohannel by pas sing them through positioning holes of an entry and exit grid plates. All the parts at different voltage were suitably in sulated by using sintered aluminium oxide rings.

In addition, to eliminate the risk for the rods to get in touch with perimetral walls, each of them was held in po sition by means of two sets of three adjustable ceramic pins at 120° located at 1/3 and 2/3 of the entire heated length (Fig. 3).

The heating current to the three resistors of the test channel,namely the two rods and the shell, was supplied from a d-c rectifier rated for 600 kW.

The rod purposely selected to be overloaded up to the burnout treshold, hereafter referred to as "burnout roa", was spring loaded to prevent it from bowing during the burnout tests.

In order to obtain present ratios of the shell and adjacent rod heat flux to burnout rod heat flux, provision was made to allow feeding of the heating elements at dif­ferent voltage through a suitable setting of the variable resistors R.. and Rp (Fig. 4) ·

The electrical connectors were made of stranded oopper cable enclosed in flexible stainless steel corrugated tubes. This arrangement presented enough flexibility to leave the heated elements free to expand.

The channel, with the rods positioned in the end terminal grid plates, was enclosed in a thin cylindrical shell, and the space in between was filled with aluminum oxide fragments to the purpose of thermally insulating the channel and prevent ing intense conveotion of the stagnant external water. Fig. 5 shows a close-up view of the exit section of the channel.

The entire assembly was inserted in a test section housing designed to withstand the pressure.

The housing was made of a 4" schedule 80 stainless steel pipe connecting two terminal stainless steel heads maohined to provide flanged electrically insulated passages for the electrical connectors.

The manufacturing difficulties of the channel and the limited size of the controlled atmosphere furnace, reduced the available heated length of the test section to 590 mm.

Water flow was measured by a turbine flow meter as well as an orifice plate, the former allowing recording of the water flow signals.

Two sheat type thermocouples were used for water inlet temperature measurements, whereas five thermocouple of the same type were located at different positions of the exit flow area enabling an evaluation of the water temperature tranverse distribution.

Fig. 6 indicate the relevant dimensions of the ohannel flow area and the positions of the five thermocouples locat ed at the channel exit.

3. Control of the subchannels geometrical symmetry

The tests preliminary performed and referred to in a previous paper /!ƒ, were considered as a check on the over all feasibility of the mixing experiments in the designed test apparatus.

In fact,in the course of the above runs, a primary tran sverse geometrical asymmetry was discovered in the two adjacent channels through the check of some distributions of the exit water temperatures over the flow area obtained from experiments

9 -

with symmetric heat generation. This primary asimmetry could be charged to several geo­

metrical imperfections observed in the earlier prototypes of the channel.

The improvement of the manufacturing technique of the channel and the use of a second set of ceramic spacers, allowed to achieve the symmetry requirements for the com­plex flow passage in cold conditions. As a check of the overall reliability of the experimental set up in hot condi tions, tests were made aiming at the control of channel symmetry with the fluid circulating at the operating pres­sure and temperature.

In these check runs the water exit temperature distribu tion was assumed as experimental evidence of the transverse symmetry of the system.

The following check tests were performed:

- steady-state tests with heating limited alternatively to the two rods.

steady-state tests with simultaneous symmetric heat gene ration limited to the two rods.

steady-state test with heating limited to the channel walls only.

Figs. 7 and 8 show the results obtained for 3 typical check runs giving for each detection point of the exit flow area the ratio θ of the local to the average ooolant temperature rise.

These plots show the existence of a fairly good degree of symmetry in the channel.

- 10

4. Burnout experiments

4.1. Range of parameters

The following range of parameters was covered in the present experiments: - Mass flow rate: 49 - 230 gr/cm sec - Pressure : 52-139 ata - Inlet temperature: 190 - 329°C.

As for the heat flux ratios, namely the burnout heater heat flux to other heaters heat flux ratio, several values were tested ranging from 0 to 1.

4.2. Burn-out data presentation

Burn-out data have been reported in Tables I through V and plotted in Fig. 9 through 13. The symbols Φ_ Q , Φ. and Φ„ appearing in these representation indicate respec­tively:

Φ_, _ = burnout heat flux of the "burnout rod" u.U. Φ. = heat flux of the "adjacent rod" Φ3 = heat flux of the "shell".

The power is generated in the shell both in the curved sections as well as in the flat thin strips.

The last term contributes only for 15$ of the total shell power.

11 -

As for the shell heat flux Φ3, their values have been computed accounting only for the power and the surface of curved section of the duct.

In Fig. 9 through 13 burnout heat flux values are report ed as a function of the coolant inlet temperature for the different heating conditions tested.

5. Remarks

Fig. 12 shows how, for the same inlet conditions, the heat flux on the burnout rod decreases with increasing the power generated on the shell.

Examination of the Figg. 9 through 11 suggests that, for equal inlet conditions of the coolant, the burnout heat flux on the so called "burnout rod" is unaffected by the degree of heating of the adjacent rod.

The same conclusion may be drawn from the results repre­sented in Fig. 13.

This result could be explained assuming that a mutual oom pensation sets in along the channel between the effects of flow redistribution and thermal mixing.

However, the independency of the critical power on the B.O. rod with respect to the conditions in the adjacent channel, has been verified on such a large variety of coolant flow rate and enthalpy conditions, that it seems unlikely that redistribution and mixing effects might have balanced through out the tests. It is more reasonable to admit that, on short heating lengths, as the one tested in our experiments, the mixing and redistribution effects do not have any relevant

12

influence on the behaviour of at least a portion of the coolant cell associated to the burnout rod.

On the other hand, some experimental B.O. data of preliminary tests conducted with the test section here described, showed that the burnout heat flux on the "burnout rod" was to a certain extent affected by the degree of heating of the "adjacent rod". The trend observed was a small decrease of the burnout heat flux on the B.O. rod with increasing the heat flux of the adjacent rod.

However, in the course of the systematic experiments, whose results are here reported, this effect was never confirmed so that the preliminary data were considered rather related to some imperfections present in the first assembly.

Therefore, before drawing any conclusion on the results here reported, it is worth to obtain additional experimental evidences about the effect of transverse transport of fluid upon the critical heat flux. This work should be carried out in a different test channel, having the same lattice parameters as the one described in this report, in order to be able to find out whether the trend suggested by the data here presented is affected or not by the particular structure of the tested channel.

It is anticipated to perform experiments with transverse distribution of heat generation in a 9 rod bundle test section next to be tested in the SORIN pressurized water loop.

- 13

Acknowledgements

Appreciation is expressed for the constant coopération of Mr. Morocutti of the Euratom.

The fruitful discussions with Mr. Previti of the FIAT Atomio Power Department are gratefully acknowledged.

Thanks are also due to the Metallurgy and Ceramios Laboratory of the FIAT APD for having made the task of brazing the various parts of the flow channel.

The authors are indebted to Mr. Sonavero, Mr. Fumerò, Mr. Mina-zio, Mr. Passavanti and other members of the SORIN Heat Transfer Laboratory for the fine work performed throughout the present experimental program.

Finally the help offered by the SORIN workshop in manufacturing the test seotion is acknowledged.

14

Bibliography

¿Vf F. Biancone, A. Campanile, G. Galimi, M. Goffi, "Forced convection burnout and hydrodynamic i n s t a b i l i t y ex­periments for water a t high p re s su re . Pa r t I : Presen t a t i on of data for round tubes with uniform and non­uniform power d i s t r i b u t i o n " , Report EUR 2490.e, 1965.

¿2/ A. Campanile, G. Galimi, M. Goffi, " Inves t iga t ion of burn out hea t f lux in a double adjacent and communicating channels t e s t sec t ion with t ransverse ly varying heat genera t ion" , Contr ibut ion to the Round Table of the European Two-Phase Flow Group - Section 4 . 1 . - C.C.R. I s p r a , 1 4 - 1 7 June 1966.

TABLE I

Burn-out dataiheating on burnout rod only.

Run

18(21-2-67)

58(26-7-67)

74(7-12-66)

120(26-7-67)

56(9-12-66)

64(21-2-67)

74(18-1-67)

20(19-7-67)

22(19-7-67)

45(7-12-66)

69(24-7-67)

106(26-7-67)

49(9-12-66)

Pressure a t a

132

132

130

132

131

133

132

132

132

130

134

132

132.5

Flow IA

880

855

943

1030

1020

2650

2640

2670

2670

2700

2800

3060

3195

Mass flow r a t e

gr/cm2sec

51.6

50.1

52.2

53.9

51.9

154.6

152.4

154.2

152.3

147.9

153.5

155.7

160.9

I n l e t subcooling

«»C

93.7

92.7

60.3

38.0

27.6

91.1

84.2

83.7

76.7

55.8

57.9

28.2

25.6

I n l e t temperature

oc

236.7

237.7

269

292.5

302.3

240

246.2

246.7

253.7

273.5

273.7

302.2

305.3

Power kW

49.6

47.4

43.1

33.8

34.0

71.2

63.0

66.4

64.4

58.2

57.9

47.2

44.3

Φ B.O. Watt/om2

262.3

250.7

228.0

178.8

179.8

376.6

333.2

351.2

340.6

307.8

301.5

249.6

234.3

Ul I

Follows Table

Run

54(18-1-67)

45(26-7-67)

50(21-2-67)

90(7-12-67)

01(26-7-67)

6(21-2-67)

20(9-12-66)

I .

Pressure a ta

133

132

131.5

132

132

132

132

Flow 1/h

3180

3880

3800

3875

4325

4400

4670

Mass flow r a t e

gr/cm^sec

155.8

228.1

219.6

214.4

219.8

221.9

230.0

I n l e t subcooling

°C

18.1

94.2

84.9

61.3

27.8

26.0

18.7

I n l e t temperature

°C

313.0

236.2

245.2

269.2

302.6

304.5

311.8

Power kW

41 .0

84.1

83

71.2

53.5

50.8

48.7

Φ B.O. 2

Watt/cm

216.9

444.8

439.0

376.6

283.0

268.7

257.6

TABLE I I

Run

22(21-7-67)

48(21-7-67)

58(24-7-67)

40(21-7-67)

58(21-7-67)

17(26-7-67)

30(26-7-67)

44(24-7-67)

40(26-7-67)

16(24-7-67)

81(21-7-67)

89(21-7-67)

23(24-7-67)

Pressure a t a

134

135

134

134

136

133

133

134

131

132

133

136

130

Flow

iA

870

900

2800

3910

4010

850

2610

2830

3890

340

950

1015

2640

Burn-out datacheat ing

Mass flow r a t e

gr/cm2sec

50.6

50.3

151.7

221.4

221.4

50.0

151.2

154.5

227.7

49.4

53.1

53.3

152.4

I n l e t subcooling

°C

88 .6

85.7

52.3

73.8

62.3

95.1

85.8

56.1

91.1

95.0

66.3

41.5

82.3

on both r o d s .

I n l e t temperature

°C

243

264.5

279.3

257.8

270.5

236.0

245.2

275.5

238.7

235.5

264.7

291.2

247.0

Total power

kW

73.4

66.5

94.2

119.4

111.2

84.1

122.9

107.8

153

92.3

80.1

66.2

130.3

B.O. rod power

kW

46

41.9

57.3

74.8

69.3

46.3

67.1

59.2

82.8

47.1

40.8

33.9

66.7

Φ B.O.

Watt/cm2

243.3

221.6

303.1

395.6

366.5

244.9

354.9

313.1

437.9

249.1

215.8

179.3

352.8

ΦΑ Φ

B.O

0.595

0.587

0.644

0.596

0.604

0.816

0.832

0.821

0.848

0.959

0.963

0.953

0.953

■vi

I

Follows Table II.

Run

48(20-7-67)

62(20-7-67)

74(20-7-67)

35(24-7-67)

67(21-7-67)

96 (21-7 -67)

P r e s s u r e a t a

134

134

134.5

131

134

132

Flow 1/h

2640

2930

3350

3840

3980

4430

Mass flow r a t e

gr /cm sec

150.1

160.5

163.8

224 .6

217.3

221.3

I n l e t subcoo l i ng

°C

75 .9

57 .6

17 .7

90 o 6

56.1

22 .5

I n l e t t e m p e r a t u r e

°C

255.7

274 .0

314.2

239.2

275.5

308.0

T o t a l power

kW

127.4

117.2

8 3 . 5

168.0

132.0

100 .6

B.O. r o d power

kW

64 .6

59 .3

4 2 . 6

85 .1

65.8

51

Φ B.O. 2

Watt/cm

341.7

313 .6

225 .3

450.1

348 .0

269.7

Φ A

Φ B.O

0.972

0 .976

0 .960

0 .974

1 .006

0 .972

00 I

TABLE I I I

Burn-out da ta :hea t ing on the B.O, rod and on the s h e l l .

Run

53 (3 -7 -67 )

5 ( 3 - 7 - 6 7 )

6 (3 -7 -67)

35 (3 -7 -67 )

50 (3 -7 -67 )

47(13-7-67)

58(13-7-67)

16(13-7-67)

40(13-7-67)

32(13-7-67)

P r e s s u r e a t a

130

132

132

134.5

135.5

133

132

134

132

134

Flow 1/h

2435

2440

2630

3010

2980

2330

2535

2570

2770

2980

Mass flow r a t e

g r / cm 2 sec

139.6

138.0

145.5

151.0

135.5

135.0

141.0

140 .6

138.8

136.4

I n l e t s u b c o o l i n g

°C

7 8 . 3

72 .0

60.9

24 .9

16 .7

86 .1

64.0

57.1

23 .5

2 .45

I n l e t t e m p e r a t u r e

°C

251.0

258 .4

269 .6

307 .0

315.8

245 .0

266 .5

274.5

307 .0

329 .2

T o t a l power

kW

119.9

112.2

112.3

8 5 . 0

7 3 . 3

161 .6

143.8

134.7

110.0

8 8 . 0

B.O. rod power

kW

57 .4

53 .5

5 2 . 6

40 .3

34 .7

55 .3

49 .3

47.1

38 .0

30 .2

Φ B.O. Watt/cm

303.6

283.0

278.2

213.1

183.5

292 .5

260 .7

249.1

201.0

159.7

φ 3 ΦΒ.Ο

0.445

0 .452

0 .480

0 .460

0 .450

0 .835

0 .830

0.831

0.838

0.848

TABLE IV

Burn-out da ta :hea t ing on both rods and on the s h e l l .

Run

10(19-1-67)

24(19-1-67)

37(19-1-67)

47(19-1-67)

40(17-1-67)

91(17_1_67)

117(17-1-67)

50(14-7-67)

74(14-7-67)

88 (14-7 -67)

95(14-7-67)

P r e s s u r e a t a

133.5

134.5

136

135

129.5

134.5

134

133

135

134

141

Flow iA

2600

2744

2975

3316

2750

3036

3210

2370

2460

2750

2770

Mass flow r a t e

g r / c m 2 s e c

148.6

150.7

156.4

158 .6

153 .6

156.0

155.0

135". 5

132.7

140.4

137.0

I n l e t s u b c o o l i n g

°C

79.1

59 .9

42 .3

12.7

64.9

33 .2

14 .6

7 8 . 3

51 .5

30.1

23 .9

I n l e t t e m p e r a t u r e

°C

252.2

272.0

290.5

319.5

263 .7

298.7

317 .0

252 .7

280 .7

301 .5

311 .7

T o t a l power

kW

133.8

121 .1

113.1

8 7 . 6

149

122.3

97.1

198.1

168.4

149.2

135.9

B.O. r o d power

kW

55 .5

50 .2

46 .9

35 .9

5 1 . 6

42 .5

34 .2

51 .0

4 3 . 7

38 .9

35 .2

Φ B.O. 2

Watt/cm

293 .5

265 .5

248.1

189.9

272 .9

224.8

180.9

269.7

231.1

205 .7

186.2

ΦΑ

*B.O

0 .434

0 .436

0 .437

0 .465

0.581

0 .579

0 .567

0 .890

0 .883

0 .872

0 .872

Φ3

Φ ΦΒ.Ο

0.419

0 .415

0 .412

0 .407

0 .555

0.541

0 .539

0 .856

0 .820

0 .819

0 .823

Ο

Follows Table IV.

Run

13(19-7-67)

47(18-1-67)

22(18-1-67

38(18-1-67)

Pressure a t a

130

132

135

139

Flow

iA

2630

2952

3100

3180

Mass flow r a t e

gr/cm sec

151.0

156.0

160.9

154.2

I n l e t subcooling

°C

81 .3

42.2

37.1

18

I n l e t temperature

°C

248.0

288.3

295.1

316.5

Tota l power

kW

212.7

167.0

158.6

130.9

B.O. rod power

kW

54.9

43.9

41.7

34.4

Φ B.O.

Watt/cm

290.4

232.2

220.5

181.9

ΦΑ Φ

B.O

0.903

0.863

0.868

0.869

-îiL Φ

B.O

0.852

0.823

0.815

0.808

ι

ro

TABLE Y

Burn-out data hea t ing on both r o d s .

Run

7(20-7-67)

18(20-7-67)

30(20-7-67)

74(2-8-67)

1

Pressure a t a

52.5

53

55

53

Flow iA

1775

1785

1890

1975

Mass flow r a t e

gr/cm2sec

110.7

106.4

107.7

110.7

I n l e t subcooling

°C

75.7

44.3

20.0

9.6

I n l e t temperature

°C

190.0

222.0

248.7

256.7

Tota l power

kW

158.6

134.2

113.4

74.6

B.O. rod power

kW

79.3

68.2

57.6

39

Φ ΦΒ.Ο. Watt/cm2

419.4

360.7

304.6

206.3

ΦΑ Φ B.O

1

0.968

0.969

0.913

ro

23

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® PRESSURE

© TEMPERATURE

Fig . 1 - Flow diagram.

- 24 -

SORIN SALUGGIA

SEZIONE DI PROVA N°4 CONTORNO DEL CANALE RISCALDATO.

SCALA CS '/

DIS. ^gp

DATA

/9f4 N.· SOM 9?i

Fig. 2 - Cross section of flow passage.

Fig. 3 — Close-up view of the channel showing the location of the spacers.

- 26

+ shunt

B.O. Rod

R

Adjacent Rod

Shell

R2 4-

Fig . 4 - Schematic diagram of the e l e c t r i c a l connection arrangement.

— 27 —

Fig. 5 — Close-up view of the exit section of the channel.

28

a = 1,5 mm

b = 2,9 mm

Fig. 6 - Relevant dimensions of the flow passage showing the positions of the exit water temperature probes.

29

Q O Û;

ó CD

Ζ

o

o Ζ t—

< UI X

Q O

UJ O < —> Q <

Ζ O

o

<

X

θ

?

1

η

o

o

< >

<>

o

0—L L o - o - 0J ·—0*—

Inlet, temp. 210 °C

Pressure 120 ata

Flow rate 5000 l/h

Total power 30 KW

Temperature probe positions

θ

,0„ΓΛ. . -ÍQ-Q — Ql 1— Q

Temperature probe positions

Vig. 7 - Transverse coolant temperaturs rise for several points of

the exit section during tests for control of the subchannels

geometrical symmetryι Asymmetrical heating.

30 -

Inlet temperature Pressure Flow rate

Total power

202 °C 110 ata 2875 l /h

627 KW

θ

Ui Q

O ca

o ζ

t— < LU Χ J^\J^S.

Ο-Ο-θ

Temperature probe positions

Fig. 8 - Transverse coolant temperature rise for several points of the exit section during terts for control of the subchannels geometrical symmetryt Symmetrica"', heating.

31

«00

300

200

100

S

δ χ

,­Δ # D

BURN OUT HEAT FLUX

IN EXPERIMENTS WITH

UNHEATEO SHELL.

NOMINAL MASS FLOW RATE

50 gr/cnrfsec

NOMINAL PRESSURE

132 a t ·

SYMBOL Φ./ Φ a»

Δ 0 □ 059

V 081

O 0,96

δ

(Δ

INLET TEMPERATURE °C

200 250 300 350

Fig. 9 - Burnout heat flux in experiments with unheated

shell. ρ

Nominal mass flow rate 50 gr/cm sec

Nominal pressure 132 ata

32

400

300

200

100

o

χ

_| b.

S ζ

^

BURN OUT HEAT FLUX

IN EXPERIMENTS WITH

UNHEATEO SHELL.

NOMINAL MASS FLOW RATE

156 gr/cntsec

NOMINAL PRESSURE

132 ata

SYMBOL Μι« Δ 0

α 059

V 081

O 0,96

¿D

INLE

Λ

0

Γ TEMPERAT URE e

C

200 250 300 350

Fig. 10 - Burnout heat flux in experiments with unheated

shell. «

Nominal mass flow rate 156 gr/cm sec

Nominal pressure 132 ata

- 33

500

400

300

200

100

0

iE

χ

!

I

Δ° ν

BURN OUT HEAT FLUX

IN EXPERIMENTS WITH

UNHEATEO SHELL.

NOMMAL MASS FLOW RATE

225 gr/crrfsec

NOMINAL PRESSURE

132 ata

SYMBOL ♦./φ» Δ 0 α oss V 081

O 096

D

α

( J

INU

Δ

O

:r TEMPERATI JRE »C

200 250 300 350

Pig. 11 - Burnout heat flux in experiments with unheated

shell. 2

Nominal mass flow rate 225 gr/cm sec

Nominal pressure 132 ata

­ 34

400

300

200

100

iE ­Ü.

»

X

_l b.

X

Δ

O

BURN OUT HEAT FLUX

IN EXPERIMENTS WITH

HEATED SHELL.

NOMINAL MASS FLOW RATE

156 gr/cm e«c

NOMINAL PRESSURE

132 ata

SYMBOL M.. i /Φι«

Δ 0 0

D 0,U3 0,413

V 0576 0,545

O Q876 0824

Δ

D _ £

ν π

t

α ο

ο*

Δ

D <9

INLET TEMPERATURE °C

200 250 300 350

Fig. 12 - Burnout heat flux in experiments with heated shell,

Nominal mass flow rate 156 gr/cm2sec

Nominal pressure 132 ata

­ 35 ­

400

300

200

100

"fe „o

X

3 b.

UI χ

e

BURN OUT HEAT FLUX

IN EXPERIMENTS WITH

HEATEO SHELL AND

AOJACENT ROD AL­

TERNATIVELY HEATED

OR UNHEATED.

NOMNAL MASS FLOW RATE

137 gr/crrvstc

NOMINAL PRESSURE

132 ata

SYMBOL ♦r/i. Φ, /i« O 0 083

O 088 0,83

o e

4 >

o

INLE1

°e o

' TEMPERATU 1

•

RE »C

200 250 300 350

Fig. 13 - Burnout heat flux in experiments with heated shell

and adjacent rod alternatively heated or unheated.

Nominal mass flow rate 137 gr/cm2sec

Nominal pressure 132 ata

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