ML20045B720

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Heavy Water Reactor Facility Project Phase 1 AP600 Small Scale Passive Containment Cooling Sys Test Dry Test Results Applicable to Hwrf Project NRP-RPT-91-0021
ML20045B720
Person / Time
Site: 05200003
Issue date: 09/30/1991
From:
WESTINGHOUSE ELECTRIC COMPANY, DIV OF CBS CORP.
To:
Shared Package
ML20045B693 List:
References
NRP-RPT-91-0021, NRP-RPT-91-21, WCAP-13743, WCAP-13743-R, WCAP-13743-R00, NUDOCS 9306180345
Download: ML20045B720 (29)
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WESTINGHOUSE CLASS 3 WCAP-13743 WESTINGHOUSE PROPRIETARY CLASS 2 VERSION EXISTS AS WCAP 13742 Heavy Water Peactor Facility Project, Phase 1, APC00 Small Scale Passive Containment Cooling System Test " Dry" Test Results Applicable to the HWRF Project NRP-RPT-91-0021 29 (C) WESTINGHOUSE ELECTRIC CORPORATION 19 93 A license is reserved to the U.S. Govemment under contract DE4CO3-90SF18495.

O WESTINGHOUSE PROPRIETARY CLASS 2 TNs document contains informaton propnetary to Westmghouse Electnc Corporabon: it is submitted in confidence and is to be used solely for the purpose for which at is fumished and retumed upon request. This document and such information is not to be reproduced, transmitted, disclosed or used otherwise in whole or in part without authonzabon of Wesbnghouse Electne Corporation, Energy Systems Business Unit. sutgeet to the legends contained hereof.

GOVERNMENT LIMITED RIGHTS:

(A) These data are submitted with hmited nghts under Govemment Contract No. DE-AC03-90SF18495. These data may be repredad and used by the Govemment with the express limitation that they will not, without wntten permission of the Contractor, be used for purposes of manufacturer nor dnclosed outside the Govemment except that the Govemrnent may dsciose these data outside the Govemment for the following purposes, if any, provided that the Govemment makes such dsclosure sutgect to prohibiton against further use and disdosure:

(1)

This 'propnetary data' may be disdosed for evaluabon purposes under the restnctions above.

(ll)

De 'propnetary data' may be dselosed to the Electne Power Research Institute (EPRI), electric utikty representanves and their drect consultants, excludng drect commercial compentors, and the DOE Nanonal Laboratones under the probitxbons and restnctions above.

(B) This notice shall be marked on any reproduccon of these data,in whole or in part.

@ WESTINGHOUSE CLASS 3 (NON PROPRIETARY)

EPRI CONFIDENTIAL / OBLIGATION NOTICES:

NOTICE:

12 20 3 04 Os O CATEGORY: A EB OC DDOE OF 0-O DOE CONTRACT DELIVERABLES (DELIVERED DATA) i Sublect to specahed exceptons, disclosure of this data is restncted until September 30,1995 or Design Certficataon under DOE contract DE-AC03-

)

90$F18495, whichever is later.

Westinghouse Electric Corporation Energy Systems Business Unit Nuclear And Advanced Technology Division P.O. Box 355 Pittsburgh, Pennsylvania 15230 i

@ 1992 Westinghouse Electric Corporation All Rights Reserved i

WESTINGHOUSE CLASS 3 NPR-RIT-91-0021 Revision 0 1

PHASE I AP600 SMALL SCALE 4

PASSIVE CONTAINMENT COOLING SYSTEM TEST

" DRY" TEST RESULTS APPLICABLE TO THE HWRF PROJECT I

September,1991 I

I

" APPLIED TECHNOLOGY" Any further distribution by any holder of this document or of the data therein to third parties representing foreign interests, foreign governments, foreign companies and foreign subsidiaries or foreign divisions of U.S. companies should be coordinated with the Director, Office of LWR Safety and Technology, U.S. Department of Energy."

WESTINGHOUSE CLASS 3 NPR-RPT-91-0021 Revision 0 l

I 1

i LIMITED RIGHTS LEGEND This technical data contains " proprietary data" furnished under Contract No. DE-AC03-86SF10638" with the U.S. Department of Energy which may be duplicated and used by the Government with the express limitations that the " proprietary data" may not be disclosed outside the Government or be used for pumoses of manufacture without prior permission of the Contractor, except that funher disclosures or use may be made solely for the evaluation purposes under the restriction that the.

" proprietary data" be retained in confidence and not further disclosed.

l

I WESTINGHOUSE CLASS 3 NPR-RPT-91-0021 Revision 0 This document contains information proprietary to Westinghouse Electric Corporation; it is submitted in confidence and is to be used solely for the purpose for which it is furnished and retarned upon request. His document and such information is not to be reproduced, transmitted, disclosed or used othenvise in whole or in part without authorization of Westinghouse Electric Corporation, Energy Systems.

WESTINGHOUSE CLASS 3 NPR-RPT-91-0021 Revision 0 i

TABLE OF CONTENTS l

Section Eagt ABSTRACT 1

l l

1.0 INTRODUCTION

2 2.0 PCCS TEST APPARATUS 2

l 2.1 Summary Description 2

2.2 Foundation and Tower 4

2.3 Pressure Vessel 6

2.4 Steam Supply 6

2.5 Steam Inlets to the Vessel for Containment Simulation 7

2.6 Condensate Handling 9

2.7 External Cooling 9

2.8 Axial Fan 9

2.9 Instrumentation and Measurements 11 3.0 TEST CONDITIONS 14 4.0 RESULTS 14

{

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WESTINGHOUSE CLASS 3 NPR-RIrr-91-0021 Revision 0 TABLE OF CONTENTS List of Tables Table No.

Eage 3.1

" Dry" AP600 Passive Containment Cooling System Tests - Test Matrix 15 4.1 AP600 Passive Containment Cooling System Test Average Data and Results 16 Summary; Tests 1,2,3,4,22,23 4.2 AP600 Passive Containment Cooling System Test Data For Selected Set, 17 For Specific Test; Test 1 4.3 AP600 Passive Containment Cooling System Test Data For Selected Set, 18 For Specific Test; Test 2 4.4 AP600 Passive Containment Cooling System Test Data For Selected Set, 19 For Specific Test; Test 3 4.5 AP600 Passive Containment Cooling System Test Data For Selected Set, 20 For Specific Test; Test 4 4.6 AP600 Passive Containment Cooling System Test Data For Selected Set, 21 For Specific Test; Test 22 4.7 AP600 Passive Containment Cooling System Test Data For Selected Set, 22 For Specific Test; Test 23

WESTINGHOUSE CLASS 3

)

NPR-RPT-91-0021 Revision 0 TABLE OF CONTENTS l

List of Figures Firure No.

Eagt 2.1-1 Section View of AP600 Passive Containment Cooling Integral Test 3

2.1-2 Passive Containment Cooling System Test Apparatus 5

2.5-1 Uniform Steam Distributor 8

2.5-2 Side and Top View of Conical Steam Distributor 10 2.9-1 Temperature Measurement Locations 12 iii

WESTINGHOUSE CLASS 3 NPR-RPT-91-0021 Revision 0 Phase I AP600 Small Scale Passive Containment Cooling System Test

" Dry" Test Results Applicable to the HWRF-NPR Project ABSTRACT The AP600 reactor is being designed to utilize a

  • Passive" Containment Cooling System (PCCS) to remove heat released to the containment following any postulated event. This system employs natural draft air cooling and the evaporation of a water film from the outside of the steel containment shell.

The AP600 Small Scale Passive Containment Cooling System Test demonstrated water film behavior, mass transfer (evaporation), and convective heat transfer on the external surface of a steel tank initially filled with one atmosphere of air and heated on the inside with dry steam.

A range of design basis conditions for steam / air internal pressure, external cooling air velocity, air temperature, air relative humidity,and water film flow rates were investigated. Several tests were performed with no external water film flow; the results of these " dry

  • Phase I AP600 PCCS tests are applicable to the HWRF-NPR Project. Selected sets of data for each of the " dry" AP600 PCCS tests l

is reported in Section 4.0, Tables 4.1 thru 4.7.

Since the time of the reported tests, the AP600 Small Scale Test has been modified for HWRF Containment Cooling Tests. Prior to these modifications, the flow resistance of the inlet air heating coil present in the AP600 PCCS test configuration required utilization of an axial fan, located in the chimney region, to simulate natural draft conditions; this fan was in operation during performance of the reported " dry" AP600 PCCS tests (the axial fan is also present in the HWRF Small Scale Test configuration and contributes to the overall annulus exit form loss but is not operated).

1

WESTINGHOUSE CLASS 3 NPR-RPT-91-0021 Revision 0

1.0 INTRODUCTION

ne AP600 reactor is a pressurized water reactor being designed to utilize a passive containment cooling system (PCCS) as the safety grade means to remove heat released to the containment following any postulated event and transfer this heat to the environment. The PCCS utilizes a steel containment vessel for the heat transfer surface. The heat is transferred to the inside steel surface of the containment vessel by condensation of steam. Heat is conducted through the steel wall and finally heat is transferred to the environment from the outside surface of the containment by convection to air and evaporahn of a water film. For example, when the combined steam and air pressure inside 'he l

containment is 30 psig, the outside of the containment vessel is expected to be at 175'F. A natural air draft is created in a duct next to the outside of the containment (above the operating deck) by heating l

the air and adding water vapor. This draft is sufficient to result in an upward flow velocity of between 15 and 20 feet per second and turbulent forced convection heat and mass transfer (evaporation) occurs.

To demonstrate and obtain heat transfer data at prototypic conditions for both inside containment heat i

transfer by condensing steam and external heat transfer by conduction and water evaporation; a 24 foot tall,3 foot diameter, steel tank surrounded by a prototypically sized cooling air annulus was constructed. His tank, initially filled with one atmosphere of air was pressurized (heated) with steam over a range of expected design basis pressures and cooled externally with a range of prototypic air i

and external water flowrates. Overall heat transfer rates and local heat flux at 24 separate locations were measured.

The AP600 Passive Containment Cooling System Test included test cases with the external tank surface both wetted and dry. This report addresses the test cases performed with a dry external tank l

surface as applicable to the HWRF Containment Cooling System which does not utilize evaporation of an external water film for containment cooling.

2.0 PCCS TEST APPARATUS 2.1

SUMMARY

DESCRIPTION ne facility for testing operation of the AP600 Passive Containment Cooling System (PCCS) used a 24 foot tall,3 feet in diameter pressure vessel containing air or nitrogen at one atmosphere when cold and supplied with steam at pressures up to 80 psig. A transparant baffle wall installed around the vessel formed the air cooling annulus. In test cases with a dry external vessel surface, air flow up the annulus outside the vessel cooled the vessel surface directly resulting in condensation of the steam inside the vessel.

Figure 2.1-1 is a schematic diagram of the test apparatus. Saturated steam from a boiler was throttled to a variable but controlled pressure and led into the bottom of the vessel, which initially contained one atmosphere of air. Various arrangements of steam distributors were used to distribute steam inside the vessel. The steam distributor arrangement shown in the figure was used for slow radial flow, uniform along and around a central supply pipe which ran the full height of the test vessel.

2

WESTINGHOUSE CLASS 3 NPR-RPT-91-0021 Revision 0

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WESTINGHOUSE CLASS 3 NPR-RPT-91-0021 Revision 0 Another arrangement used a conical distributor at the end of a supply pipe that directed relatively low speed steam flow upward. The conical distributor was located at the bottom of the vessel for one set of tests in order to promote a substantial mixing of the steam with the air by the hot buoyant plume.

The full length, uniform distributor was expected to produce the most limiting steam condensation condition.

Steam inlet pressure and temperature and condensate temperature and flow from the vessel were measured to establish the total heat transfer from the test vessel. Twenty-four thermocouples located on the outer surface of the vessel's 0.375 inch thick steel wall indicated the temperature distribution over the height and circumference of the vessel. De measured temperatures were multiplied by the respective vessel wall areas sensed by the thermocouples and summed to obtain the average vessel surface temperature.

The test apparatus included provisions for varying annulus inlet air temperature and humidity to simulate cooling air conditions expected to occur next to the actual AP600 containment vessel. Air could be preheated to a set temperature by controlling steam pressure in a steam heating coil (heat exchanger). After heating, the air could be humidified, up to high levels, by a humidifier supplied with steam. Although the provisions for inlet air temperature and humidity control were in place during performance of the " dry" PCCS tests, all tests with no external water film flow were conducted at ambient temperature and humidity.

A varitble speed axial fan located in the chimney region above the test vessel enabled varying the air speed in the simulated containment annulus up to about 35 feet per second. The fan was needed in order to simulate natural draft conditions because of the resistance of the air heating coil, and because the smaller total duct height in the test facility produced a smaller buoyant head of air than the actual plant design.

The temperature of the cooling air was measured after passing through the air heating coil and upon exiting the annulus in the chimney region. The cooling air velocity was measured at the inlet to the air heating coil, ne heat transfer to the cooling air (i.e., its temperature rise multiplied by its specific heat and its measured flow rate) provided a second measurement of the total heat transfer.

A photograph of the test apparatus, Figure 2.1-2, shows many of the test components including the transparent baffle wall and test vessel. He tower which suppons all but the pressure vessel itself provides three floors for workers to erect the components, install instrumentation and operate instrument traverses.

2.2 FOUNDATION AND TOWER The foundation for the pressure vessel and tower is a twelve and one-half foot square pad of reinforced concrete located next to Building 301 at the Westinghouse Science & Technology Center.

The tower was constructed using six inch square structural tubing for posts and six by four inch angles for platform supports. He tower has three eleven and one-half foot square work platforms with a six foot two inch square center opening to accomodate the test vessel and annulus baffle. The 4

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WESTINGHOUSE CLASS 3 NPR-RPT-9l-0021 Revision 0 three work platforms are located at elevations approximately ten feet, eighteen feet, and twenty-six feet above the foundation.

He pressure vessel is supported by four six inch steel angle legs attached to a five foot diameter steel i

ring base. The ring and the tower's corner posts are anchored to the concrete foundation. The pressure vessel weighs approximately 5,000 pounds empty and the tower weight is approximately 8,600 pounds. With the air baffle in place, the assembly can withstand winds in excess of one hundred miles per hour.

2.3 PRESSURE VESSEL De pressure vessel is a 36 inch outside dianeter vessel with elliptical heads and a 0.375 inch thick steel wall. Overall length of the vessel, including the heads, is 286 inches.

At the bottom of the vessel, a standard 150 pound class,20 inch weld-neck flange is welded into the head on the vessel centerline. The 20 inch diameter opening formed by the weld-neck flange serves as a manway. He manway opening is covered by a 150 pound class,20 inch blind flange. A 4 inch diameter hole through the center of the 20 inch blind flange is covered by a 150 pound class,4 inch blind flange. A 2 inch pipe nipple is welded into the 4 inch blind flange to permit connection of the external steam supply pipe to the internal steam distributor. A threaded I inch pipe nipple is welded into the 20 inch blind flange to provide for the condensate drain.

At the top of the vessel, a standard 150 pound class,10 inch weld-neck flange is welded into the head on the vessel centerline. The top vessel opening is also covered by a blind flange. The top vessel blind flange serves r.s a feedthrough for vapor trap pigtails that connect with reference pressure lines and nitrogen charging lines inside the vessel.

The pressure vessel is rated for its intended use,100 psig, although the extra heavy walls would permit a higher rating. The heavier wall thickness was specified to better model wall heat transfer without making fabrication and erection unduly difficult.

He vessel support legs provide 60 inches of clearance between the bottom flange c.nd the foundation to accomodate installation of steam supply and condensate drain piping.

The inner and outer surfaces of the vessel were sprayed with a 0.006 to 0.008 inch thick coating of self-curing, inorganic zine primer to prevent corrosion. Prior to application of the zine primer, the vessel was prepared by sandblasting the surfaces with G-40 size steel shot.

2.4 STEAM SUPPLY Saturated steam was supplied by a 10,000 pounds per hour gas fired boiler which was maintained at 100 psig during testing. Fel! firing was maintained at the boiler to avoid cycling and pressure swings that would result in unsteady operation of controls in the test apparatus. Excess steam was vented to ambient through a pressure limiting relief valve and flow silencer above the boiler. Laboratory demineralized water was used for boiler water makeup; no condensate was returned to the boiler.

6

WESTINGHOUSE CLASS 3 1

NPR-RPT-91-0021 Revision 0 ne steam was supplied to the test tower through approximately 88 feet of 4 inch, Schedule 40 piping insulated with 1 1/2 inches of glass fiber insulation. Electrical trace heaters were installed over 40 feet of the steam supply piping to reduce piping heat losses and assure that superheated steam conditions (after throttling from 100 psig to the lower test pressure) were maintained for all tests. At the test tower, steam was delivered from the main 4 inch supply manifold to the test vessel inlet, the air humidifier and the air heating coil through individually valved 2 inch insulated pipes.

A wye strainer and a 1 inch pressure reducing valve that sensed downstream pressure for control were installed in the 2 inch vessel steam supply line. Interchangeable valve springs provided manually adjustable pressure control in ranges of 3-30 psig and 20-100 psig (during operation, the valve provided precise and steady pressure control). The steam supply pipe size was maintained at 2 inches downstream of the 1 inch pressure reducing and control valve to minimize dynamic pressure effects in the internal steam distributors. He 2 inch steam supply pipe connected to the 2 inch nipple welded into the 4 inch blind flange at the bottom of the pressure vessel.

2.5 STEAM INLETS TO TIIE VESSEL FOR CONTAINMENT SIMULATION Different types of steam distributors could be installed in the pressure vessel and connected to the vessel inlet nipple. For the " dry" tests, the

  • uniform
  • steam distributor and the " conical" steam distributor were used.

The " uniform

  • distributor consisted of six 4 foot long sections assembled with pipe couplings. The
  • uniform
  • distributor extended from the inlet nipple up into the neck of the weld-neck flange at the top of the vessel. The weld-neck flange retained the distributor while allowing it to slide up and down inside the neck to allow for differential thermal expansion. The distributor sections were fabricated from 48 inch lengths of threaded Schedule 40 stainless steel pipe containing fourteen 0.125 inch diameter metering holes. The metering holes were drilled in pairs,180 degrees apart, spaced six inches apart, with alternate pairs 90 degrees from the others. In order to prevent jetting of steam into the vessel, each inner distributor section was surrounded by a 3-1/2 inch outside diameter,0.065 inch thick wall, stainless steel shield tube. Each shield tube contained sixty-four 0.75 inch diameter holes.

He 0.75 diameter holes were drilled in sets of eight holes,45 degrees apart, with each set spaced at six inch intervals. The shield tubes were designed such that when they were assembled over the inner distributor sections, the 0.75 diameter shield tube holes were centered between the distributor metering holes. Disks welded on each end of each shield tube to loosely center it over the inner distributor section. He shield tubes slide over the inner distributor sections and rest on the pipe couplings which join the assembled distributor sections. He inner distributor section and shield tube for one section of the uniform distributor is shown in Figure 2.5-1.

He " conical" distributor directs steam upward from an outlet formed between a 48 inch long 2 inch, Schedule 40, stainless steel supply pipe and a 81/2 inch outside diameter cylinder made from 18 gauge stainless steel sheet. The supply pipe has forty 0.188 diameter metering holes spaced 45 degrees apart at five axial locations spaced five inches apart near the bottom of the pipe. A 28 inch long conical section welded to the supply pipe 2-1/2 inches from its lower end is welded to the 81/2 inch diameter cylindrical section which is 15 inches long. To assure a uniform velocity out of the distributor, two fine mesh copper screens are fixed 1 inch apart in the lower end of the cylinder 7

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WESTINGHOUSE CLASS 3 NPR-RPT-91-0021 -

Revision 0 annulus using a brass hub with six spokes. He brass hub assembly is attached to the cylinder by screws. He complete " conical

  • distributor is shown in Figure 2.5-2.

The conical steam distributor was installed inside the pressure vessel near the bottom; installed, its discharge is approximately 42 inches above the bottom of the vessel.

2.6 CONDENSATE HANDLING t

Condensate that flowed down the inside wall of the pressure vessel and collected in the neck of the 20 inch flange at the bottom was removed through a 1 inch pipe connected to a liquid drain trap (vapor trap or steam trap). He liquid delivered from the trap was cooled below 90'F, by a condensate cooling heat exchanger, before flowing through the condensate flowmeter.

2.7 EXTERNAL COOLING ANNULUS BAFFLE WALL AND AIR DUCTING 1

The air cooling annulus was fabricated from 1/4 inch thick acrylic sheets hot formed to a 33 in'ch inside radius. Aluminum angles were used to reinforce the edges of the acrylic panels; the angles also served as flanges which were used to join adjacent panels. The panels were stiffened using flat i

aluminum bars. The components were assembled, using stews to fasten the acrylic to the aluminum supports, to form a cylinder 259 inches (21 feet.7 inches) high and 66 inches inside diameter. The entire cylinder assembly was attached to the tower using aluminum angle supports. Once installed, the acrylic cylinder formed a baffle spaced 15 inches away from the pressure vessel wall thus providing a 15 inch wide air cooling annulus. The bottom of the baffle was located at an elevation 35-3/4 inches above the bottom of the vessel and at the top of the inlet air duct.

An air inlet to the cooling annulus was formed by a dished 1/8 inch thick steel pan at the bottom and a dished heavy gauge galvanized steel sheet at the top. The inlet duct had a circular shape with a 66 inch outer radius. The duct was located such that its centerline was offset 12 inches from the vessel centerline toward the inlet side of the duct. The sides of the inlet duct were approximately 31 inches high and covered by galvanized steel sheet. The air inlet duct was joined to a trapezoidal shaped galvanized sheet metal transition duct which was fastened i

to the air heating coil. Flow distribution in the annulus was improved by deflecting vanes installed in the inlet duct. The air inlet duct was designed to promote uniform, low air velocities around the lower vessel and accelerating flow up into the containment annulus.

At the top or outlet of the cooling air annulus, a 9.75 inch high conical section provided a transition between the 66 inch diameter annulus baffle and the 48 inch diameter axial fan housing.

2.8 AXIAL FAN Controlled velocity air flow in the cooling air annulus was provided by a 48 inch diameter, variable

'l speed axial fan inside a 48-1/2 inch diameter,36 inch high housing. The fan was capable of supplying up to 32,000 CFM of air which corresponds to 32 feet per second air velocity in the cooling annulus.

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WESTINGHOUSE CLASS 3 NPR-RPT-91-0021 Revision 0 2.9 INSTRUMENTATION AND MEASUREMENTS 2.9.1 Steam to Vessel and Condensate Flow, Temperature, and Pressure Steam flow rates to the vessel were not measured directly; however, steam that condensed on the inside vessel wall was measured as a condensate flow. A highly accurate water meter was utilized to register the total condensate passed during a given period of time. The nominal capacity of the water meter was 20 gallons per minute with an accuracy between 98% and 100.8% over the range of 0.25 GPM to 20 GPM. To prevent damage to the flowmeter, the condensate was cooled to 90'F or cooler, using city water in a counterflow heat exchanger, prior to entering the flowmeter.

The steam inlet temperature was measured using a 1/16 inch diameter stainless steel sheathed copper-constantan thermocouple located just upstream of the steam distributor inlet. Condensate temperature was measured as it drained from the vessel and again after the condensate cooler. The steam inlet and condensate drain temperatures were used to calculate total vessel heat transfer; the cooled condensate temperature was used to determine the condensate mass flowrate.

Steam pressure in the vessel was measured using a precision test gauge with an accuracy of 1/4% (or 0.4 psi).

The enthalpies of the steam entering the vessel and the condensate leaving the vessel were determined using the steam inlet temperature, vessel pressure and condensate drain temperature. The condensate mass flowrate was determined from the measured volumetric flowrate and the temperature of the condensate entering the flowmeter. The heat input to the vessel (or the heat removed by external air cooling) was determined by multiplying the difference of enthalpies by the condensate mass flowrate.

2.9.2 Containment Vessel Wall Temperatures Twenty-four 0.032 inch diameter stainless steel sheathed copper-constantan thermocouples attached to the outer vessel wall proviAd a measure of vessel surface temperature. Each thermocouple junction end was installed in a '

' deep,1/32 inch wide groove approximately 3/4 of an inch long and peened into place. The were filled with solder and finished to provide a smooth outer surface.

The thermocouples were installed at locations representative of all the vessel heat transfer areas. 'Ihe temperature measurement locations are shown schematically in Figure 2.9-1. Two sets of three thermocouples were located at each median radius of two equal areas on the vessel head with the thermocouples in each set located 120' apart around the circumference. Three sets of three thermocouples were located on the top vessel side wall; these thermocouples were located in the middle of three 18" high areas with three thermocouples spaced 120' apan in each area. The lower three sets were located in the middle of three 72 inch high areas on the lower vessel side wall also with three thermocouples spaced 120* apan in each area. The area fraction assigned to the two sets of three thermocouples on the top vessel head was 0.015; the area fraction assigned to the upper three sets of thermocouples on the vertical side wall was 0.065; and the lower three sets of thermocouples 11

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WESTINGHOUSE CLASS 3 NPR-RPT-9l-0021 Revision 0 on the vessel vertical side wall were assigned area fractions of 0.258 giving a total of 0.999 for the eight sets of three thermocouples.

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by the respective fractional area on the vessel in which the set was centered. The resulting values for each of the eight sets were then summed to obtain the area weighted average vessel surface i

temperature.

2.9.3 Containment Annulus Air Flow and Temperature A rotating vane anemometer was used to measure the inlet air velocity in the center of 12 equal areas at the inlet face of the air heating coil. He volumetric cooling air flowrate entering the heating coil was determined by multiplying the average measured inlet face velocity by the heating coil inlet face area (32 ft').

The average air temperature entering the annulus was measured using three thermocouples located in the middle of the inlet to the annulus at three locations 127 apart (since the inlet air was not heated for the " dry" PCCS tests, only slight differences between ambient temperature and air inlet temperature were observed). The average air temperature leaving the annulus was measured using three sets of three thermocouples centered in equal areas at the outlet of the air annulus before the fan with the three thermocouples in each set located 120' apart. The average annulus air temperature was calculated by averaging the annulus inlet and outlet temperatures.

1 The annulus air velocity was calculated by multiplying the average heating coil inlet face velocity by the ratio of ambient air density to average annulus air density and the coil inlet face to annulus flow 2

2 area ratio. The heating coil inlet face area was 32 ft and the annulus flow area was 16.69 ft i

resulting in a coil inlet face t'o annulus flow area ratio equal to 1.917. The annulus air mass flowrate was obtained by multiplying annulus air velocity by annulus air density and annulus flow area.

The heat flux to the cooling air was obtained by multiplying the difference between the annulus inlet and outlet temperatures by the annulus air mass flowrate and spcific heat which was based on the average annulus air temperature. Part of the heat flux to the cooling air is from convection of heat from the vessel and part is convection of heat radiated to the baffle wall from the vessel. The difference between the heat flux to the cooling air and the condensate heat flux is reported as an apparent ambient heat loss. Since the acrylic baffle was not instrumented for the " dry" AP600 PCCS tests, the actual ambient heat losses could not be calculated. However, the acrylic baffle was later instrumented for the HWRF Containment Cooling Test and preliminary test results show good agreement between the apparent heat loss and calculated ambient heat losses.

2.9.4 Data Acquisition and Recording Many of the test measurements, such as air velocity and integrated condensate flowrate, were obtained with installed or portable instruments and manually recorded in a data log together with the -

time at which the observations were made.' Thermocouple temperature measurements, however, were processed by a data acquisition system. Thermocouples were connected to the system by 20 AWG, 13 1

WESTINGHOUSE CLASS 3 NPR-RPT-91-0021 Revision 0 copper and constantan special limit (controlled purity) duplex extension wires with solid polyvinyl insulation. All thermocouple outputs were recorded using an electronic data logger unit.

Thermocouple extensions connected to isothermal terminal blocks that plugged into sets of low level input cards on the data logger or an extender chassis that connected with the data logger. The voltage signals were converted to digital temperatures as the data logger sequentially sampled the inputs. The sampling was done according to a pre-selected sequence programmed into the data logger. Since the data logger did not provide data storage capability, its digital output was transmitted to a computer for display and storage on a floppy disk.

3.0 TEST CONDITIONS The test conditions which were examined as applicable to the " dry" AP600 PCCS tests are shown in Table 3.1. All dry surface heat trr.nsfer test cases were performed with inlet air at ambient temperature and humidity. Test number 23 was conducted using the " conical" steam distributor installed near the bottom of the pressure vessel. The remaining " dry" tests were performed using the

" uniform" steam distributor.

4.0 RESULTS The results of each of the test cases listed in Table 3.1 are tabulated at the end of this section. Table 4.1 provides an overall summary of the average heat removed from the simulated containment with dry external surface conditions versus internal air / steam pressure. Tables 4.2 thru 4.7 provide the results for selected data sets from each specific test.

The average heat removal shown in the tables is based on the measured rate that steam was condensed inside the test vessel. The tabulated results also include the average heat removal based on the measured cooling air temperature rise.

The difference between the heat flux to the cooling air and the condensate heat flux is reported as an apparent ambient heat loss. Since the acrylic baffle was not instrumented for the " dry

  • AP600 PCCS tests, the actual ambient heat losses could not be calculated. However, the acrylic baffle was later instrumented for the HWRF Containment Cooling Test and preliminary test results show good agreement between the apparent heat loss and calculated ambient heat losses.

14

WESTINGHOUSE CLASS 3 NPR-RPT-91-0021 Revision 0 Table 3.1

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