ML20045B717

Heavy Water Reactor Facility (Hwrf) Small Scale Containment Cooling Test Preliminary Series 2 Test Results HWRF-RPT-92-001,Rev 0

ML20045B717
Person / Time
Site:	05200003
Issue date:	06/14/1993
From:	WESTINGHOUSE ELECTRIC COMPANY, DIV OF CBS CORP.
To:
Shared Package
ML20045B693	List: ET-NRC-93-3903, Forwards Nonproprietary WCAP-13726,WCAP-13728,WCAP-13733 & WCAP-13743 & Proprietary WCAP-13725,WCAP-13727,WCAP-13732 & WCAP-13742 Re Heavy Water Reactor Facility Passive Containment Cooling Sys Tests.Proprietary Repts Withheld ML20045B704 ML20045B709 ML20045B714 ML20045B717 ML20045B720
References
HWRF-RPT-92-001, HWRF-RPT-92-1, WCAP-13733, WCAP-13733-R, WCAP-13733-R00, NUDOCS 9306180340
Download: ML20045B717 (36)

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t WESTINGHOUSE CLASS 3 WCAP-13733 WESTINGHOUSE PROPRIETARY CLASS 2 VERSION EXISTS AS WCAP-13732 Heavy Water Reactor Facility (HWRF)

Small Scale Containment Cooling Test Preliminary Series 2 Test Results HWRF-RPT-92-001, Rev. 0 0 (C) WESTINGHOUSE ELECTRIC CORPORATION 19_9_3 A heenta is reserved to the U.S. Govemment under contract DE.AC03-90SF18495.

l 0 WESTINGHOUSE PROPRIETARY CLASS 2 l

This document contains informabon proprietary to Westinghouse Electnc Corporabon it is submitted in confidence and is to be used soloty for the l

purpor e for which it is fumished and retumed upon request. This document and such informahon is not to be reproduced, transmitted. disclosed or l

used otherwtse m whole or en part without authonzation of Westinghouse Electne Corporation Energy Systems Business Unst, sub ect to the legends f

contained hereof.

l GOVERNMENT LIMITED RIGHTS:

(A) These data are submitted with hmited nghts under Govemment Contract No. DE AC03-90SF18495. These data may be reproduoed and used j

by the Govemment with the express limitation that they will not, without wntion permissaon of the Contractor, be used for purposes of manufacturer nor dsclosed outside the Govemment; except that the Govemment may deciose these data outside the Govemment for the following purposes,if any, provided that the Govemment makes such dsclosure subject to prohibiton against further use and disdosure:

i 1

(l)

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

(II)

The 'propnetary data' may be dsclosed to the Electne Power Research institute (EPRI), electric utihty representatrves and their drect I

consultants, excludng drect commercial competitors, and the DOE Natonal Laboratones under the prohibibons and restnctions above.

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

i

@ WESTINGHOUSE CLASS 3 (NON PROPRIETARY)

EPRI CONFIDENTIAIJOBLIGATION NOTICES:

NOTICE:

1E 20 3 04 05 O CATEGORY: AEB DC OD0E DF 0 0 DOE CONTRACT DELIVERABLES (DELIVERED DATA)

Subject to specified exceptsons, dtselosure of this data is restncted unti September 30,1995 or Design Certfscation under DOE contract DE-AC03-90SF18495, whichever is later.

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

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-@ 1992 Westinghouse Electric Corporation All Rights Reserved

WESTINGHOUSE CLASS 3 HWRF RPT-92@l-Revision 0 l

TABLE OF CONIEh"IS

-i Section Pane ABSTRALT 1

1.0 INTRODUCIlON 3

2.0 REFERENCES

4 3.0 TEST APPARATUS 4

3.1 Summary Description 4

3.2 Foundation and Tower 6

3.3 Pressure Vessel 8

3.4 Steam Supply 8

3.5 Vessel Steam Inlet for Containment Simulation

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9 3.6 Condensate Handling 9

3.7 ' External Cooling Annulus and Air Ducting 11-3.8 Axial Fan 12 3.9 Instrumentation and Measurements 12 3.9.1 Steam and Condensate Flow, Temperature and Pressure 12 3.9.2 Containment Vessel Wall Temperatures 13 3.9.3 Containment Annulus Air Flow and Temperature 13 3.9.4 Bame Wall Temperatures 15 3.9.5 Wind Speed and Direction 15 3.9.6 Data Acquisition and Recording 16 L

4.0 TEST CONDmONS 16 5.0 PRELIMINARY RESULTS 17 5.1 Preliminary Series 2 HWRF Small Scale Test Results 17 i

WESTINGHOUSE CLASS 3 HWRF RIT 92-001 Revision 0 HWRF Passive Containment Cooling System Series 2 Small Scale Containment Cooling Test Preliminary Test Results ABSTRACT The Heavy Water Reactor Facility (HWRF)is being designed to utilize a Passive Containment Cooling System (PCCS) to remove heat released to the containment following a postulated beyond design basis event. This system employs passive or natural draft air cooling to transfer heat from the steel containment vessel to the environment. Air enters an annular space between the steel containment vessel and the shield building through inlets in the shield building wall. 'Ihe air in this annulus rises as a result of tN natural draft developed as the air is heated by the containment surface. The heated air exits the micid building through an outlet (chimney) 1ocated above the containment shell. In this manner, hear is transferred from the outer containment surface to the environment by natural convection.

The purpose of the HWRF Small Scale Containment Cooling Test was to provide beat transfer data for use in developing analytical models and verifying assumptions. The HWRF Small Scale Passive Containment Cooling System tests investigated a range of operating conditions and air flow path ennulus widths.

'Ihe HWRF Small Scale PCCS tests were conducted at the Westinghouse Science and Technology Center, Integral Containment Cooling Test Facility. 'Ihis faality was originally designed and constructed for AP600 Passive Containment Cooling System tests and was reconfigured for the HWRF Small Scale Test program.

Tests were completed in three test configurations using three different cooling air flow path annulus widths. The tests were conducted over a range of vessel internal pressures spanning predicted HWRF containment pressures. Preliminary test results from the Series 1 (15 inch annulus width) and Series 3 (3 inch annulus width) tests were reported in document NPR-RIT-91-003 dated October 7,1991. This I

report reFesents the preliminary results from the Series 2 tests which were conducted with a 5 loch cooling air annulus width.

The Series 2 test phase included tests designed to investigate the effects of varying the annulus inlet loss coefficient or pressure drop. Preliminary tests resuhs show Eood agreement with pre-test predictions which formed a basis for the design of the annulus inlet flow orificing used to vary the annulus flow coefficient. The actual measured annulus loss coefficient varied between approximately 1.8 in the unrestricted nominal 5 inch annulus configuration and approximately 37.9 with the most restricting orifice installed; ge4est design calculations predicted values of 2.0 and 46.0 respectively.

The range ofloss coefficients evaluated for the Series 2 tests resulted in measured annulus air velocities of 7.6 feet per second for the nominal 5 inch annulus configuration and approximately 2.4 feet per second with a loss coefficient of 37.9.

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WESTINGHOUSE CLASS 3 r-HWRF-RIT$2-001 Revision 0 A final, comprehensive report that includes final test results hom the Series 1,2 and 3 tests is -

scheduled to be issued.

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WESTINGHOUSE CLASS 3 HWRF RPT.92 001 Revision 0

1.0 INTRODUCTION

In the Heavy Water Reactor Facility (HWPS) design, the function of the Passive Containment System (PCCS)is to provide a safety grade means for transferring core decay heat during a be design basis event, and additional heat resulting from a postulated severe accident from the containment to the environment. The HWRF utilizes passive cooling of the fue standing steel containment vessel. Heat is transferred to the inside surface of the steel containment vessel by condensation of steam and through the steel wall by conduction. Heat is then transferred from the outside containment surface by natural convection to air. Cooling air enters an annular space b the steel containment sheD and the shleid building through inlets in the shield building wall. The air is heated by the outside containment surface and rises as a result of the natunt draft developed. Tlw heated air exits the shield building through an outlet (chimney) located above the containment shell Such passive cooung approaches have been under development for advanced new commercia and are supported by extensive testing and design evaluation. IJcensing and safety issues related to this approach have also been under extensive evaluation. The detailed design and analysis of the HWRF PCCS will utiUze this existing design basis.

The heat removal capability of the HWRF PCCS is affected by the configuration of plant structures external environmental conditions and natural phenomena which occur inside the containment structure i self. The performance depends predominantly upon the cooling air buoyant driving force, the air t

te v path pressure losses, the effective containment shell heat tnasfer coefficient and the available PCC5 heat transfer area. Other factors which can influence PCCS performance include wind conditions, nearby bu11 dings and topography, inside containment circulation patterns and the effects of non. con &nsible gases inside the containment.

In order to accurately assess the impact of t!ese parameters on the HWRF PCCS heat removal capability, a total testing package was prepared which includes t!c following series of tests:

HWRF Small Scale Containment Cooling Test HWRF Large Scale Passive Containment Cooling System Test a

HWRF PCCS Wind Tunnel Test HWRF PCCS Air Plow Path Pressure Drop Test

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This report addresses the last of three series of HWRF Small Scale Containment Cooling Tests.

'ne purpose of the HWRF Small Scale Containment Cooling Tests was to demonstrate the simulated l

operation of the HWRF Containment Cooling System using natural circulation air cooling. A range o operating conditions and air flow path annulus widths were investigated to provide test data for use in l

validation and venfication of computer codes used to predict containment performance. Three series cf tests were performed each using a different annulus width to investigate the effect of annulus width on air cooling capability. The tests were performed over a range ofinternal test vessel pressures, l

bounding the calculated worst case containment pressure, to obtain heat transfer data at relevant 3

1

WESTINGHOUSE CLASS 3 HWRF RPT-92-001 Revision 0 conditions and charactedze air cooling velocities developed by natural convection. Series 1 tests were performed with a 15 loch wide annular cooUng air flow path around a simulated containment vessel; the test facility was configured with a 3 inch annulus width for the Series 3 tests and with a 5 inch annulus width for the Series 2 tests. "Ihis test report addresses the preliminary results obtained from the Series 2 tests.

2.0 REFERENCES

Heavy Water Reactor Facility Containment Analysis Report, RD Req. No. H564, H585, Revision 1 -

Report "AO," May,1990.

NPR Document No. NPR-S-91-001, "HWRF Small Scale Containment Cooling Test Specification "

Revision 0, May 1991.

NPR Document No. NPR RFT-91-0021, " Phase 1 AP600 Small Scale Passive Containment Cooling System " Dry" Test Results Applicable to the HWRF Project," Revision 0, September,1991.

NPR Document No. NPR RIT-91-003, " Heavy Water Reactor Facility (HWRF) Small Scale Containment Cooling Test Preliminary Series 1 and Series 3 Test Results," Revision 0, October,1991.

3.0 PCCS TEST APPARATUS 3.1 SUNDdARY DESCRIPTION l

~Ihe HWRF Small Scale Corninment Cooling Tests were performed using the Integral Containment l

Cooling Test Facility located at the Westinghouse Science and Technology Center in Churchill, Pa.

This facility which was originaDy constructed for testing operation of the Westinghouse commercial I

plant Passive Containment Cooling System (PCCS), was configured for HWRF natural convection testing by removing the lower air plenum ducting and disconnecting the air preheater and humidi0 cation systems, the axial fan, and the external water film supply system.

The Integral Containment Cooling Test Facility uses a pressure vessel 24 feet tall,3 feet in diameter to I

simulate the steel containment sheII. "Ihe vessel contains air or nitrogen at one atmosphere when cold and is supplied with steam at pressures up to 80 psig. A transparent acrylic cylinder installed around

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the vessel forms the air cooling annulus. Air flow up the annulus outside the vessel cools the vessel surface resulting in con:kasation of the steam inside the vessel.

l Figure 3.1-1 is a schematic 6iagram of the test apparatus. Saturated steam from a boiler is throttJed to a variable but controlled pressure and supplied to the bottom of the vessel which for these tests initially contained one atmos; tere of air. The steam is distributed inside the vessel by the steam distributor arrangement shown in the Sgure. The steam distributor provides for slow radial flow, uniform along and around the central supply pipe which runs the full height of the test vessel. The 4

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WESTINGHOUSE CLASS 3 HWRF RPT-92-001 Revision 0 full length, uniform distributor was expected to produce the most limiting steam cond-nudon corxiitions by promoting uniform mixing of air and steam within the vessel.

To determine the total heat transfer from the test vessel, measurements are recorded for steam inlet pressure, temperature, and cona note flow and temperature from the vessel. Twenty four thermocouples located on the outer surface of the vessel's 0.375 inch thick steel wall indicate the temperature distribudon over the height and circumference of the vessel. The measured temperatures are weighted by the respective vessel wall areas sensed by the thermocouples and mmmed to obtain the average vessel outside surface temperature.

An axial fan, which was used to control the cooling air velocity in previous tests, is located in the chimney region above the test vessel. Although the fan was disconnected for HWRF natural draft testing, the fan itself was left in place and forms the upper chimney for the cooling air flow path. The fan adds nominal flow resistance.

The temperature of the cooling air is measured at ambient conditions and upon exiting the annulus in the chimney region. The cooling air velocity is measured by cornjucting a velocity traverse in the cooling air annulus using a hot wire anemometer. The heat transfer to the cooling air (i.e., its temperature rise multiplied by its specific heat and its measured flow rate) provides a semnd measurement of the total heat transfer.

A photograph of the test apparatus, Figure 3.1-2, shows many of the test components including the transparent cylinder and test vessel. The tower, which supports a!I but the pressure vessel, provides three floors for workers to assemble components, install instrumentation and conduct measurements.

3.2 FOUNDATION AND TOWTR i

The foundation for the pressure vessel and tower is a 121/2 foot square pad of reinforced concrete located next to Building 301 at the Westinghouse Science & Technology Center. The tower was constructed uslag 6 inch square structural tubing for posts and 6 X 4 loch angles for platform supports.

l The tower has three 111/2 foot square work platforms with a 6 foot - 2 inch square center opening to accommodate the test vessel and annulus baffle. The three work platforms are located at elevations approximately 10 feet,18 feet, and 26 feet above the foundation.

The pressure vessel is supported by four 6 inch steel angle legs attached to a 5 foot diameter steel ring l

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 100 miles per hour.

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WESTINGHOUSE CLASS 3 HWRF-RPT-92-001 Revision 0 3.3 PRESSURE VESSEL The pressure vessel is a 36 inch outside diameter vessel with elliptical heads and a 0.375 inch thick steel wall. Overalllength 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. The manway opening is covered by a 150 pound class,20 inch bund flange. A 4 Indi diameter hole through the center of the 20 inch blind flange is covered by a 150 pound class,4 Indi 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 laternal steam distributor. A threaded 1 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 bead on the vessel centerline. The top vessel opening is also covered by a blind flange. The top vessel blind flange serves as a feedthrough for vapor trap pigtails that connect with reference pressure lines and nitrogen charging lines inside the vessel. The top vessel opening was also utilized for installation and centering of the internal steam distributor.

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

the vessel support legs provide 60 inches of clearance between the bottom flange and the foundation to accommodate 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 zinc primer to prevent corrosion. Prior to application of the zine primer, the vessel was prepared by shot peening the surfaces with G 40 size steel shot.

l 3A STEAM SUPPLY Saturated steam is supplied by a 10,000 pounds per hour gas fired boiler which is maintained at 100 psig during testing. Full firing is maintained at the boiler to avoid cycling and pressure swings that could result in unsteady operation of controls in the test apparatus. Excess steam is vented to ambient through a pressure limiting relief valve and flow silencer above the boiler. Laboratory demineralized water is used for boiler water makeup; no cohe is returned to the boiler.

The steam is 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 are installed over 40 feet

{

cf 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) are maintained for all tests. At the test

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tower, steam is delivered from the main 4 inch supply manifold to the test vessel inlet through a 2

(

inch insulated pipe.

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r WESTINGHOUSE CLASS 3 IfWRF-RPT-92-001 Revision 0

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A wey strainer and a 1 inch pressure reducing valve that senses downstream pressure for control are installed in the 2 inch vessel steam supply line. Interchangeable valve springs provide manually adjustable pressure control in ranges of 3-30 psig and 20-100 psig (during operation, the valve provided precise and steady pressure control). De steam supply pipe size remains at 2 laches downstream of the 1 inch pressure reducing and control valve to minimize dynamic pressure effects in the internal steam distributor. The 2 inch steam supply pipe is connected to the 2 inch nipple welded into the 4 inch blind flange at the bottom of the pressure vessel.

3.5 STEAM INLET TO TIIE VESSEL FOR CONTAINMENT SIMULATION De 4 inch blind flange in the pressure vessel provides for installation of different types of steam distributors. He " uniform" steam distributor is used for all HWRF Small Scale Containment Cooling Tests.

De " uniform" distributor consists of six 4 foot long sections of pipe which are connected by couplings. De " uniform" distributor extends from the steam inlet nipple up into the neck of the weld-neck flange at the top of the vessel. De weld-neck flange retains the distributor while allowing it to slide up and down inside the neck to allow for differential thermal expansion. De distributor sections were fabricated from 48 inch lengths of threaded Schedule 40 stainless steel pipe containing fourteen 0.125 inch diameter metering holes. De metering holes were drilled in pairs,180 degrees apart, spaced six inches between pairs, with alternate pairs 90 degrees from the others. In order to prevent jetting of steam into the vessel, each inner distributor section is surrounded by a 31/2 inch outside diameter,0.065 inch thick wall, stainless steel shield tube. Each shield tube contains sixty-four 0.75 inch diameter holes. The 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 are assembled over the inner distributor sections, the 0.75 diameter shield tube holes are centered between the distributor metering holes. Disks welded on each end of each shield tube loosely center it over the inner distributor section. De shield tubes slide over the inner distributor sections and rest on the pipe couplings which join the assembled distributor sections. De inner distributor section and shield tube for one section of the uniform distributor are shown in Figure 3.5-1.

3.6 CONDENSATE HANDLING Condensate that is formed on the inside wall of the pressure vessel flows down and collects in the l

neck of 20 inch flange at the bottom of the vessel. De condensate is removed through a 1 inch pipe l

connected to a liquid drain trap (vapor trap or steam trap) and cooled below 9CTF by a condensate l

cooling heat exchanger. De cooled condensate is collected in a weigh tank consisting of a 55 gallon I

drum which rests on an electronic scale. %e mass of condensate collected in the weigh tank is measured by the electronic scale and this reading is continuously communicated to the Data Acquisition System (DAS) over an RS232 interface, A level probe installed in the weigh tank is connected to a solenoid valve installed in the weigh tank drain line and provides for automatic l

daining when the weigh tank is reaches the selected set point.

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HWRF.RPT-92 001 Revision 0 3.7 EXTERNAL COOLING ANNULUS AND AIR DUCTING' The HWRF Small Scale Test Matrix specifies three series of tests which use three differl annulus widths. "Ihe cooling air annulus is formed by a transparent acrylic cylinder installed aroun the pressure vessel. Series 1 tests were performed with a 15 inch annulus using the same a cylinder used for previous AP600 PCCS tests. A new acrylic cylinder which formed a 3 inch annu was fabricated for the Series 3 tests and an additional acrylic cylinder which formed a 5 inch annu was installed for the Series 2 tests.

"Ihe 15 inch air cooling annulus was fabricated from 1/4 inch thick acrylic sheets hot formed to a 3 inch inside radius. Aluminum angles were used to reinforce the edges of the acrylic pan also served as flanges which were used to join adjacent panels. The panels were stiffened aluminum bars. The components were assembled, using screws to fasten the acrylic to the alum 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 around the pressure vessel wall, the acrylic cylinder formed a 15 inch wide annular space thus providing a 15 inch wide annular air cooling flow path. The bonom of the acrylic cylinder was located at an elevation 35-3/4 lades above the bottom of the vessel even with the top of the inl duct.

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

In previous AP600 tests, the 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 ha 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 o approximately 31 inches high and covered by galvanized steel sheet. The air inlet duct was join a trapezoidal shaped galvanized sheet metal transition duct which was fastened to the air heatin For the HWRF tests, the transition duct which joined the inlet duct and heating coil was disconnected and the sheet metal covering around the 31 loch high inlet duct was removed. These modifications provided a 31 inch high opening around the circumference of tie annulus and allowed ambient air to enter the annulus directly.

The 3 inch air cooling annulus was fabricated using 3/32 inch thick acrylic sheets supported aluminum ribs anached to the original 15 inch annulus baffle. *Ihe gap between the 15 inch annulus baffle and the 3 inch annulus baffle was scaled at the top and bottom using a washer type rin from styrofoam sheet to prevent air from short circuiting the cooling air flow path between the 3 inch baffle and the vessel wall.

11

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WESTINGHOUSE CLASS 3 HWRF RPT 92-001 Revision 0 The 5 inch air cooling annulus was installed and supported by the 15 loch baffle in this same fashion as the 3 loch annulus. In the 5 loch annulus configuration, provisions for lastallation of an orifice were provided to permit varying the annulus loss coefficient by restricting the air flow at the annulus inlet. The inlet flow oriSce consisted of an anmdar disc cut from 3/4" thick plywood to fit into the 5 loch wide annulus gap at the inlet. Twenty-four equally spaced 3.5 inch diameta holes were cut into the plywood disc to provide for air flow. With the orifice installed in the annulus inlet, the inlet loss coefficient was varied by plugginE a predetermined number of holes to reduce the inlet flow area and achieve the desired pressure drop. Tests were conducted in the 5 inch annulus configuration with and without the flow orifice installed (4.47 sq. ft. flow area without orifice installed; with orifice inmbd.

1.60 sq. ft. flow area with 24 holes open and 1.07 sq. ft. flow area with 16 holes open).

3.8 AXIAL FAN The axial fan which provided controlled velocity air flow in the cooling air annulus for previous tests was disconnected for the HWRF tests. "Ihe fan, however, was physically left in place as the 48-1/2 inch diameter,36 inch high fan housing formed pan of the cooling air outlet or chimney. Although the fan was not operated during the HWRF tests, it did represent a form loss in the cooling air flow path.

3.9 INSTRUMENTATION AND MEASUREMENTS 3.9.1 Steam 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 by collecting the condensate in a weigh tank. 'Ihe mass of condensate collected in the weigh tank was measured using an electronic scale. 'lhe scale reading was communicated to the Data Acquisition System (DAS) over RS232 interface and recorded, along with the coinciding time, at the same sampling rze selected for recording temperature measurements.

The steam inlet temperature was measured using a 1/16 loch 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.

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

The enthalpies of the steam entering the vessel arx! the condensate leaving the vessel were determinM using the steam inlet temperature, vessel pressure and condensate drain temperature. Condensate mass flowrate was calculated by dividing the mass of condensate collected over a given time interval by corresponding time duration. The heat loput to the vessel or the total heat transfer from the vessel was determined by multiplying the difference of the steam and condensate enthalples by the conderwate mass flowrate.

12

r WESTINGHOUSE CLASS 3 HWRF-RPT 92-001 Revision 0 3.9.2 Containment Vessel Wall Temperatures Twenty four 0.032 inch diameter stainless steel sheathed copper constantan thermocouples attached to the outer vessel wall provided a measure of vessel surface temperature. Each thermocouple junction end was lastalled in a 1/32 inch deep,1/32 loch wide groove approximately 3/4 of an loch long and peened into place. "Ih: grooves were fiUed with solder and finished to provide a smooth outer surface.

The thermomuples were installed at locations representative of aH the vessel heat transfer areas.1he temperarme measurement locations are shown schematicaDy in Figure 3.9-1. 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. "Ihree 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' apart in each area. The lower three sets were located in the middle of threc 72 loch high areas on the lower vessel side wall also with three thermocouples spaced 127 apart 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 thre sets of thermocouples on the vertical side wall was 0.065; and the lower three sets of thermocouples ca 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.

The temperatures measured by each of the three thermocouples in a set were averaged and multip 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 mmmed o obtain the area weighted average vessel surface t

temperature.

3,9.3 Containment Annulus Air How and Temperature An ALNOR Thermo Anemometer was used to measure the air velocity in tle cooling air annulus.

The air velocity was obtained by performing air velocity traverses while the test was operating at steady state conditions. The traverses were conducted at six circumferential positions at each of three elevations; each traverse consisted of eight velocity measurements across the annulus width. As a l

result of the instrument operating characteristics, the measured velocity readings were referenced to standard conditions. To obtain the actual velocities, the resulting velocity measurements were corrected as follows:

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Va = Vi x CF Wtere:

Va = actual air velocity (ft/sec)

Vi = velocity indicated by Thermo Anemometer (ft/ min)

CF = correction factor = ds/da = 0.075*(459.7+T1yl.325'Pa ds = air density (lbfcu ft) at standard calibration conditions da = actual air density at local temperature and barometric pressure 13 i

WESTINGHOUSE CLASS 3 nwRFyr 92-001 Revision 0 1

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Locations for Vessel WallTemperature Measurements, Baffle Wall Temperature Measurements. Containment Annulus AirTemperature Measurements,and Inlet Steam and Condensate Temperature Thermocouples.

14

a WESTINGHOUSE CLASS 3 HWRF-RPT-92-001 Revision 0 T1 = local air temperature ('F) at velocity measurement location Pa = ambient pressure (in.Hg)

The local annulus air temperature measurements were obtained by performing air temp at three circumferential positions at each of three elevations corresponding with the velo measurement elevations. Each air temperature traverse consisted of nine temperature measureme across the annulus width.

The average air temperature entering the annulus was measured using three thermoc 127 apart, located in the annulus inlet region. The average air temperature leaving the annu 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 127 apart. Th annulus air temperature was calculated by averaging the ambient air temperature, annulus inl outlet temperatures and annulus air temperature traverse measurements on an elevatioi The cooling air mass flowrate was calculated as a sum of the products of the local annulus air 1

velocity, the corresponding local air density (based upon the air temperature traverse data) a flow area fraction assigned to each velocity measurement.

The heat flux to the cooling air was obtained by multiplying the difference between the amb temperature and average annulus outlet temperature by the annulus air mass flowrate and evaluated at the average annulus air temperature. The difference between the heat fl air and the condensate heat flux is reported as an apparent ambient heat loss.

3.9.4 Annulus Wall Temperaturrs The outer surface temperature of the 5 inch annulus wall was measured using four 0.032 in stainless steel sheathed copp:ra:onstantan thermocouples attached to the outer surfa cylinder. The wall thermocouples were located at four elevations adjacent to four vessel wall temperature locations as shown in Figure 3.9-1. Four additional thermocouples were attached to t outside surface of the outer (15 inch annulus) acrylic cylinder at locations adjacent to the thermocouples installed on tie inner (5 inch annulus) cylinder.

The inner (5 inch) and outer (15 inch) annulus wall temperature measurements were used to the temperature differences across the annulus walls and evaluate heat losses due to convec radiation from the annulus walls to ambient air.

3.9.5 Wind Speed and Direction A weather vane /anernometer was mounted on the roof of the building adjacent to the test tow approximately 12 feet above ground level. The wind speed and direction indicated by the ane were continuously monitored and recorded by the data acquisition system; this data was used to evaluate the influence of local wind effects on the steady state test data.

15

e WESTINGHOUSE CLASS 3 HWRF-RPT 92-001 Revision 0 i

3.9.6 Data Acquisition and Recording The test measurements, such as air velocity and atmospheric pressure, 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 and collected condensate weight, however, were processex! by a data acquisition system. 'Ihermocouples were connected to the system by 20 AWG, copper and constantan special limit (contmiled purity) duplex extension wires with solid polyvinyl insulation. All thermocouple outputs were recorded using an electronic data logger unit.

Thermocouple extensions were connected to isothermal terminal blocks that plugged into sets oflow 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, along with the condensate weigh tank output, to a computer for display and storage on a floppy disk.

4.0 TEST CONDITIONS 5

The test conditions which were examined in the Series 2 HWRF Small Scale Containment Cooling Tests are listed in the test matrix provided as Table 4.1 along with the Series 1 and Series 3 tests which were previously completed. All test cases were performed using the " uniform" steam distributor and with inlet air at ambient temperature and humidity.

As specified in the test matrix, the Series I and Series 3 tests were performed at five constant test pressures selected to provide data bounding the calculated worst case containment pressure of 75 psia (60 psig) (Reference 2.1 Appendix A) and provide heat transfer data over the entire anticipated containment pressure range.

Results of the Series I and Series 3 tests indicated that the 15 inch annulus tests (Series 1) provided heat transfer data in the free convection regime and the 3 inch annulus tests (Series 3) provided information in the forced convection regime. Based upon the results of these tests, concern was expressed as to whether the Series 2 tests, with a 5 inch annulus width, would provide sufficient information in the free convection regime. As a result, the Series 2 test matrix was modified to allow for variation of the annulus inlet loss coefficient. Three loss coefficients, one of which representing the nominal 5 inch annulus configuration, were selected based upon pre-test predictions to assure testing in the free convection regime and provide more prototypic annulus pressure drop conditions.

in order to provide continuity with the completed Series 1 and Series 3 tests, the Series 2 tests were conducted at 60 psig and 15 psig vessel pressures.

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c WESTINGHOUSE CLASS 3 HWRF-RI'r 92-001 Revision 0 5.0 RESULTS Preliminary Series 2 (5 loch annulus width) test results from the HWRF Small Scale Containment Cooling Test (SST) are provided in Tables 5.1 1 through 5.1-16. As the test data as weU as the associated calculations and results are geliminary; use is recommended for review and information only. *ihe test data is gesendy undergoing further evaluation; results of this evaluation and a & tailed description of the final results will be Fovided in the HWRF Small Scale Test summary report.

5.1 PRELIMINARY SERIES 2 HWRF SMALL SCALE TEST RESULTS The preliminary Series 2 HWRF Small Scale Test (HWRF SST) results are reported in Tables 5.1-1 through 5.1 16. Table 5.1 1 Fovides an overall test sununary for all Series 2 tests and Table 5.1-2 provides a summary of vessel surface teg wdures for each of the Series 2 tests. The annulus air g

temperature traverse measurements for each of the Series 2 tests are provided in Tables 5.1-3 through 5.1-9; nanulus air velocity data is Fovided in Tables 5.1-10 through 5.1 16.

These results represent tests conducted, with a 5 inch annulus configuration, by varying the annulus loss coefficient to pennit demonstration of the transition between the turbulent free convection and forced convection heat transfer regimes. *Ihe Series 2 tests were conducted at 60 psig and 15 psig vessel pessures to provide continuity with the completed Series I and Series 3 tests.

In general, the Series 2 test results show good agreement with pe-test predictions and characteristics, such as vessel wall temperature Fofiles, observed in the Series 1 and Series 3 tests were repeated in the Series 2 tests. As expected, the Series 2 tests performed with the nominal (unrestricted) 5 inch annulus configuration confirmed pre-test predictions and provided heat transfer data in the forced convection regime. Also, the actual measured annulus loss coefficient, appoximately 1.8, cornpared weD with the predicted value,2.0, for the nominal 5 inch annulus configuradon.

Tests performed with orificing installed in the annulus inlet to increase the loss coefficient resulted in reduced velocities and provided heat transfer data in the turbulent free convection regime. Again, the measured annulus loss coefficient, appoximately 37.9, showed good agreement with the gedicted value of 46.

'Ihe Series 2 test data is pesently undergoing further evaluation; results of this evaluation and a detailed desaiption of the final results will be Fovided in the HWRF Small Scale Test sumrnary report.

17

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WESTINGHOUSE CLASS 3 gwgp.wr-92-ool Revision 0.

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WESTINGHOUSE CLASS 3 m. m.92 m t Revision 0 I

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WESTINGHOUSE CLASS 3 HWRF FT 92@l Revision 0 Table 5.14 HWRF SerieF2 (S inch Annulus) Run 61 (60 psig No In!st Restriction)

ANNULUS air TEMPERATURE TRAVERSE DATA DISTANCE FROM AIR TEMPERATURE - F VESSELWALL 0

120 240 (INCHES)

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(BACK) AVERAGE

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ANNULUS air TEMPERATURE TRAVERSE DATA DISTANCE FROM AIR TEMPERATURE - F VESSEL WALL 0

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Table 5.16 HWRF 5eries-2 (5 inch Annulus) Run 64 (60 psig,24 x 3.5" Dia. Hole inlet Restrictor)

ANNULUS dlR TEMPERATURE TRAVERSE DATA DISTANCE FROM AIR TEMPERATURE - F i

VESSEL WALL 0

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. Revision 0 Table 5.17 HWRF Series 2 ($ Inch Annulus) Run 65 (15 psig,16 x 3.5" Dia. Hole Intet Restricto ANNULUS AIR TEMPERATURE TRAVERSE DATA DISTANCE FROM AIR TEMPERATURE F VESSEL WALL 0

120 240 (INCHES)

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(SIDE)

(BACK) AVERAGE 3

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z-WESTINGHOUSE CLASS 3 gwar.arr-92mi Revision 0 Table 5.14 HWRF Series 2 (5 inch Annulus) Run 67 (60 psig,24 x 3.5" Dia. Hole inlet Restrictor)

ANNULUS AlR TEMPERATURE TRAVERSE DATA DISTANCE FROM AIR TEMPERATURE-F VESSEL WALL 0

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WESTINGHOUSE CLASS 3 HWRF-RPT 92-001 Revision 0 Table 5.19 HWRF Series 2 (5 tnch Annulus) Run 69 (60 psig,16 x 3.5" Dia. HoleInlet Res ANNULUS AIR TEMPERATURE TRAVERSE DATA DISTANCE FROM AIR TEMPERATURE - F VESSEL WALL 0

120

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(FRONT)

(SIDE)

(BACK) AVERAGE

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Table 5.1-10 HWRF Series 2 (5 inch Annulus) Run 60 (15 psig, Noinlet Restriction) Annulus Air Velocity Data CORRECTED ANNULUS AIR VELOOfTY (FT/SEC)

DiST. FROM VESSELWAU.

CIRCUMFERENTIAL LOCATION - DEGREES (INCHES) 0 60 120 180 240 300 AVERAGE l

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WESTINGHOUSE CLASS 3 WU RPT Mi Revision 0 Table 5.111 HWRF Series-2(S inch Annulus) Run 61 (60 psig, Noinlet Restriction) Annulus Air Velocity Data CORRECTED ANNULUS AIR VELOCITY (FT/SEC)

[MST. FBOM VESSELWALL CIRCUMFERENTIAL LOCATON -DEGREES (INCHES) 0 60 120 180 240 300 AVERAGE m

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WESTINGHOUSE CLASS 3 WRF.M-92@l Revision 0 Table 5.112 HWRF Series.2 (Sind Annulus) Run 62 (60 psig, No inlet Restriction) Annulus Air Veloc.ity Data CORRECTED ANNLA_US AIR VELOCfiY (FT/SEC)

D6ST. FROM VESSELWALL CIRCUMFERENTML LOCATION-DEGREES (INCHES) 0 60 120 180 240 300 AVERAGE a., b

=

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WESTINGHOUSE CLASS 3 HWRF-RIrr 92-001 Revision 0 Table 5.113 HWRF Series 2 (S ind Annulus) Run 64 (60 psig,24 x 3.5" Dia. Hole inlet Restrictor)

Annulus AirVelodty Data CORRECTED ANNULUS AIRVELOCTTY(FT/SEC)

VESSELWALL CIRCUMFERENTIAL LOCATION - DEGREES (HCHES) 0 60 120 180 240 300 AVERAGE I

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31

WESTINGHOUSE CLASS 3 mvRF RFr 92-oot Revision 0 Table 5.114 HWRF Series 2 (5 f rxh Annulus) Run 65 (15 psig,16 x 3.5" Dia. Hole inlet Restrictor)

Annulus Air Velocity Data VESSR WALL CRCUWEREMW.LOCADON DEGREES ONCHES) 0 60 120 180 240 300 AVERAGE O3 b 32

WESTINGHOUSE CLASS 3 HWRF RPT-92@l Revision 0 Table 5.115 HWRF 5eries 2 (5 inch Annulus) Run 67(60 psig,24 x 3.5" Dia. Hole Inlet Restricto Annulus Air Velocity Data DIST. FROM VESSELWALL CIRCUMFERENTW. LOCATION - DEGREES (WCHES)

O 60 120 180 240 300 AVERAGE-7 i

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WESTINGHOUSE CLASS 3 uwar arr-93-ool Revision 0 Table 5.116 HWRF Series 2 (5 Inch Annulus) Run 69 (60 psig.16 a 3.5" Dia. Hole Intet Restri Annulus Air Velodty Data OtST. FROM CORRECTED ANNULUS AIR VELOCl1Y(FT/SEC) f VESSEL Wall CIRCUMFERENTIAL LOCATION-DEGREES (INCHES) 0 60 120 180 240 300 AVERAGE i

x,b I

i 34 1

i

.-