ML20045B714
| ML20045B714 | |
| Person / Time | |
|---|---|
| Site: | 05200003 |
| Issue date: | 08/31/1992 |
| From: | WESTINGHOUSE ELECTRIC COMPANY, DIV OF CBS CORP. |
| To: | |
| Shared Package | |
| ML20045B693 | List: |
| References | |
| NPR-RPT-92-003, NPR-RPT-92-3, WCAP-13728, WCAP-13728-R01, WCAP-13728-R1, NUDOCS 9306180332 | |
| Download: ML20045B714 (34) | |
Text
. - - -
e 4
. -...A I
a 3$
l I
i f
)
.O f[
![g.h!
b g
lfNR *
'-:g L'
m e{
ive?
,,T
~~ 'g
~
m
[
repassen 2
,.z---=
- -m_
~~
~..l>._
y nu 3'-
B5 l
I ge.s :. :..
m--~ - ;_
l
--coy ggg__ --
- p u_~,. -
! l I
.a=-
=
9ggg r-hj i e
q'aw sign 01:u r== -f-9 1 y a us e 4
r
.h 7 [
... __E9[
N5imasi W
i g
~
4 Mh$$
)
z W r ga*>:ees: esseeees
$@s _R;A$$ll
..=z=-= _
gs W
l
^
- )
%SW@ WW MmM m ~ @o Tholans;p 4 % Jw
%g - %
y f
r
.Q 446:v E
p DA
't a m
P 4.m i[w j
,M,3
+. -
aq 73 j9 qmmm7 fr
^
,Pg; M,
,< yp > ylf q g p3gL{" 4 7
',, g.g gj
-f s
gjg 55-4j "A
t
,; q7 y
+
~' ", h ';'%l.["f"t h" D & ; % $ % ?,; W [. n f hn %_h, M
,, N r J ".% a.f
,Th& $~-N_l U
' " l:
ec a
e-<,
c.-
W' M@W,h ;W;i M, fema k
%" f : <. ml h gh
?
f.-
w,.
y _f,
f a,
Y p
.p.
. ms,
m
...m.
- s 1 W
b G.
A pa agg g i:e W;;! ?:f l af 6 i< w c
c
,a x,.x
, %,G
%, ' Q% ' ' L,.,
fQ r
s 7
gy jM+
, bb f
A h h
f h
j $w er M M ' $ %w @e $,[2 g 3 m M h h A " N u d M W h E d NaMP a%
e e.o u
W; 2 A s a
'e4 s
~
xg<
!;U
- Q
,a n
% i' f
v
?
- h. Mf;::
MV 1
,t :gQ hN. yp n f
[OOGyy
' [.1
. fQn\\ q/w ;[qg&aw,y%y:$'N 5" d@y Y
y.
- %~
" g.
- y y
+ ; 'yl, n yN t
gny gg
- Q }:
- k. p Lh
$r '
' '~
^u
- & w w%
m tm: A:/
WQ 7:t-L.
- y 1;yf}ig(' d,r f ',,i >, y)j 1S Gyx
+1.;:)' R l c:-
vl j
~ Np e V;Q,y:. + n
~,
a s
<s ihAS i i r
h g -@ $ $ [%[ %r ]
hi ik;hg[*
e<
a y' a s,
3x 5:i t N Olf yJ Ti s'
i f
.f Q,.
M E '.
e c.,
lb flf bh kk kh? f 'A < :
l y' K $g- [< %
si s
w s
31
, WWy " g, $,7 yj
", g.
kf% g %,..
J p
gy:ma q $
m aj %n gqh f _
3 y My.yk,aL mq ' % o..~ y g n g.3., w g:g n m n y 7.m y g ge p; g i p fg)y;,9 y
% a4 v ng m
q
?
d A
(
l' L
n gu S
, yw
..a r,
,, WM p-_
' MW.
m ';. lu.
.m a rg ' 4
+
+4 m
,%;m p' M;?p:y
!N@...
43.
o w '.
4
- e. '
< A; m
yw ? l 9
~
u
\\
y M
f U
ff i
p wwk'4 y%49%':jau m, ecgh,'u
' % v, ngym&
y
. gWg701h x;
'lJ g
)n
, y~ gNhy$... a@4 x y'"
i'-
9 7
e
@,w ' + v 9
hb hbNh' YYNd Y ?$ kN wbg e ;}wgO (y y$
+
qu m
e.
n q< fun aqNfg m #}f HEiE v
xr J
1
~
y:
p f
._o
!dy?SBg m
'm M
L A4 f; -
h!
(
~
y g
?'
- q
- e A. 9 y
c r
6-~
e p;.
r,
((
,g
-p laK
~ ~ '
F' i
7 4;
WI ;l u:
- .j
'I
- j
-.3
,3
- i n
I 1
e se
. tn 1{
0_mpad.
j g
^
i &
.m.
"i d
%%__ i-e W
M ket t
- RMo
-9306180332 930614 lh g;;ggrf PDR ADOCK 05200003 w-
.-w - %
4 fEREW hh
()
WESTINGHOUSE CLASS 3 WCAP-13728 WESTINGHOUSE PROPRIETARY CLASS 2 VERSION EXISTS AS WCAP-13727 Heavy Water Reactor Facility Project (HWRF)
Small Scale Containment Cooling System Test Final Report HWRF-RPT-92-003, Rev.1 0 (C) WESTINGHOUSE ELECTRIC CORPORATION 199,3 O teense is reserved to the U.S. Govemment under contract DE.ACO3-90SF18495.
O WESTINGHOUSE PROPRIETARY CLASS 2 This document contains information propnetary to Westinghouse Electne Corporaton; it is submitted in confidence and is to be used solely for the purpose for which it is fumished and retumed upon request. This document and such informahon is not to be reproduced, transmitted, disclosed or used otherwise in whole orin part ethout authorizaton of Westnghouse Electne Corporation Energy Systems Business Unit. subject to the legends conta:ned hereof.
GOVERNIV'ENT LIMITED RIGHTS:
(A) These data are submitted with hmited nghts under Govemment Contract No. DE-AC03-90SF18495. These data may be reproduced and used by the Govemment utn the express hmrtaten that they will not, without wntion permission 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, provded that the Govemment makes such declosure subject to prohibiton against further use and disdosure:
(1)
This 'propnetary data' may be disdosed for evaluabon purposes under the restnctions above.
(11)
The ' proprietary data' may be dsclosed to the Electric Power Research institute (EPRI), electnc utility representatrves and their drect consultants, excludng drect commercial compettors, and the DOE Nabonal Laboratones under the prohibibons and restrictens above.
(B) This notice shall be marked on any reproduction of these data, in whole or in part.
@ WESTINGHOUSE CLASS 3 (NON PROPRIETARY)
EPRI CONFIDENTIAUOBLIGATION NOTICES:
NOTICE:
13 20 3 04 O5 O CATEGORY: AEB DC ODOE OF 0 0 DOE CONTRACT DELIVERABLES (DELIVERED DATA)
Subject to spectf ed excephons, disclosure of this data is restncted unbl September 30,1995 or Design Cerbfcation 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 i
@ 1992 Westinghouse Electric Corporation All Rights Reserved
WESTINGHOUSE CLASS 3 NPR-RPT-92-003 Revision 1 HEAVY WATER REACTOR FACILITY (HWRF)
SMALL SCALE PASSIVE CONTAINMENT COOLING SYSTEM TEST FINAL REPORT August 1992
~
WESTINGHOUSE CLASS 3 t
NPR-RPT-92-003 Resision 1 3
\\
\\
l f
l LIMITED RIGHTS LEGEND J
This technical data contains " proprietary data" furnished under Contract No.
DE-AC02-90CH10439 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 purposes of manufacture without prior permission of the Contractor, except that further 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.
i I
- a x >
m
WESTINGHOUSE CLASS 3 NPR-RPT-92 003 Revisica 1 TABLE OF CONTENTS Section Eage ABSTRACT 1
1.0 INTRODUCTION
2
2.0 REFERENCES
3 3.0 PCCS TEST APPARATUS 5
3.1 Summary Description 5
3.2 Foundation and Tower 6
3.3 Pressure Vessel 6
3.4 Steam Supply 9
3.5 Vessel Steam Inlet to the Vessel for Containment Simulation 10 3.6 Condensate Handling 10 3.7 External Cooling Annulus and Air Ducting 10 3.8 Axial Fan 13 3.9 Instrumentation and Measurements 13 3.9.1 Steam and Condensate Flow, Temperature and Pressure 13 3.9.2 Containment Vessel Wall Temperatures 14 3.9.3 Containment Annulus Air Flow and Temperature 15 3.9.4 Annulus Wall Temperatures 17 3.9.5 Wind Speed and Direction 18 3.9.6 Data Acquisition and Recording 18 4.0 TEST CONDITIONS 18 5.0 RESULTS 20 5.1 FINAL HWRF SMALL SCALE TEST RESULTS 20 1
WESTINGHOUSE CLASS 3 NPR-RPT-92-003 Revision 1 TABLE OF CONTENTS List of Tables Table No.
Eage 4.1 HWRF Small Scale Containment Cooling Test-Text Matrix 16 5.1-1 HWRF SST Series 1 (15 inch annulus) Final Test Summary 18 5.1-2 HWRF SST Series 2 (5 inch annulus) Final Test Summary 19 5.1-3 HWRF SST Series 3 (3 inch annulus) Final Test Summary 20 5.1-4 HWRF SST Vessel Surface Temperature Summary 21 5.1-5 HWRF SST Measured Annulus Velocity Summary 22 i
J ii
WESTINGHOUSE CLASS 3 NPR-RPT-92-003 Resision 1 TABLE OF CONTENTS List of Figures Ficure No.
Page 3.1-1 Section View of HWRF Small Scale Containment 5
Cooling Test 3.1-2 Passive Containment Cooling System Test Apparatus 6
3.5-1 Uniform Steam Distributor 9
3.9-1 Temperature Measurement Locations 13 5.1-1 HWRF SST Series 1 Average Vessel Surface Temperature 23 versus Vessel Elevation 5.1-2 HWRF SST Series 2 Average Vessel Surface Tempersture 24 versus Vessel Elevation 5.1-3 HWRF SST Series 3 Average Vessel Surface Temperature 25 versus Vessel Elevation 4
l e
WESTINGHOUSE CLASS 3 NPR-RPT-92-003 Resision 1 Heavy Water Reactor Facility (HWRF)
Small Scale Passive Containment Cooling System Test Final Report L
i l
ABSTRACT l
l-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. The air in this annulus rises as a result of the natural draft developed as the air is heated by the containment surface. The heated air exits the shield building through an outlet (chimney) located above the containment shell. In this manner, heat 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 test 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 annulus widths.
The HWRF Small Scale PCCS tests were conducted at the Westinghouse Science and Technology Center, Integral Containment Cooling Test Facility. This facility 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 anticipated HWRF containment pressures. Preliminary test results from the Series 1 (15 inch vmulus width) and Series 3 (3 inch annulus width) tests were reported in document NPR-RPT-91-003, October,1991. Preliminary test results from the Series 2'(5 inch annulus-width) tests were reported in document NPR-RPT-92-001, January,1992. This report represents the final test results from each of the test series.
1
WESTINGHOUSE CLASS 3 NPR-RPT-92-003 Resision 1
1.0 INTRODUCTION
In the Heavy Water Reactor Facility (HWRF) design, the function of the Passive Containment Cooling System (PCCS) is to provide a safety grade means for transferring core decay heat during a beyond design basis event, and additional heat resulting from a postulated severe accident from the containment to the erwironment. The HWRF utilizes passive cooling of the free 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 between the steel containment shell and the shield building through inlets in the shield building wall. The air is heated by the outside containment surface and rises as a result of the natural draft developed. The heated air exits the shield building through an outlet (chimney) located above the containment shell.
Such passive cooling approaches have been under development for advanced new commercial plants and are supported by extensive testing and design evaluation. Licensing and safety issues have also been under extensive evaluation. The detailed design and analysis of the HWRF PCCS will utilize 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 itself. The performance depends predominantly upon the cooling air buoyant driving force, the air flow path pressure losses, the effective containment shell heat transfer coefficient and the available PCCS heat transfer area. Other factors which can influence PCCS performance include wind-conditions, nearby buildings and topography, inside containment circulation patterns and the effects of non-condensible gases inside the containment.
In order to accurately assess'the impact of these parameters on the HWRF PCCS heat removal capability,9 total testing package was prepared which includes the following series of tests:
HWRF Small Scale Containment Cooling Test HWRF 12rge Scale Passive Containment Cooling System Test HWRF PCCS Wind Tunnel Test -
HWRF PCCS Air Flow Path Pressure Drop Test This report addresses the HWRF Small Scale Containment Cooling Test.
2
WESTINGHOUSE CLASS 3 NPR-RPT-92-003 Revision 1 The purpose of the HWRF Small Scale Containment Cooling Test was to demonstrate the simulated operation of the HWRF Containment Cooling System using natural circulation air cooling. A range of operating conditions and air flow path annulus widths were investigated to provide test data for use in validation and verification of the GOTHIC containment analysis computer code. Three series of iests 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, bounding the calculated worst case containment pressure, to obtain heat transfer data at relevant conditions and characterize air cooling velocities developed by natural convection. Series 1 tests were performed with a 15 inch wide annular cooling air flow path around a simulated containment vessel. The annular air flow path width was reduced to 3 inches for the Series 3 tests which were performed at the same test conditions as the Series 1 tests. For the Series 2 tests, the annulus flow path configuration was modified to provide a 5 inch annulus width and the additional capability to permit varying the inlet loss coefficient. The Series 2 tests were conducted at test conditions designed to demonstrate the transition between the forced convection and free convection heat transfer regimes while maintaining continuity with the Series 1 and Series 3 test objectives.
This test report addresses the results obtained from each of the test series and provides a general summary of the overall HWRF Small Scale Containment Cooling Test program.
2.0 REFERENCES
2.1 Heavy Water Reactor Facility Containment Analysis Report, RD Req. No. H564, H585, Revision 1, Report "AO", May 1990.
2.2 NPR Document No. NPR-S-91001, "HWRF Small Scale Containment Cooling Test Specification", Revision 0, May 1991.
2.3 NPR Document No. NPR-RPT-91-0021, " Phase 1 AP600 Small Scale Passive Containment Cooling System " Dry" Test Results Applicable to the HWRF Project",
Revision 0, September 1991.
2.4 NPR Document No. NPR-RPT-91-003," Heavy Water Reactor Facility (HWRF) Small Scale Containment Cooling Test Preliminary Series 1 and Series 3 Test Results",
Revision 0, October 1991.
2.5 NPR Document No. NPR-RPT-92-001, " Heavy Water Reactor Facility (HWRF) Small Scale Containment Cooling Test Preliminary Series 2 Test Results", Revision 0, January 1992.
3
WESTINGHOUSE CLASS 3 NPR-RPT-92 003 Revision 1 2.6 NPR Transmittal 12tter HWRF-W-92-0164," Presentation Material, Agreements and Commitments from the February 25,1992 PCCS Status Review Meeting," March 2, 1992.
4 1
WESTINGHOUSE CLASS 3 F"R-RPT-92-003 Revision 1 3.0 PCCS TEST APPARATUS 3.1
SUMMARY
DESCRIPTION The HWRF Small Scale Containment Cooling Tests were performed using the Integral Containment Cooling Test Facility located at the Westinghouse Science and Technology Center in Churchill, Pa. This facility which was originally constructed for testing operation of the Westinghouse commercial 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 humidification systems, the axial fan, and the external water film supply system.
The Integral Containment Cooling Test Facility uses a 24 foot tall, 3 feet in diameter pressure vessel to simulate the steel containment shell. The vessel can contain 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 the vessel forms the air cooling annulus. Air flow up the annulus outside the vessel cools the vessel surface resulting in condensation of the steam inside the vessel.
Figure 3.1-1 provides a sketch of the test apparatus. Saturated steam from a boiler is throttled to a variable but controlled pressure and supplied to the bottom of the vessel which for these tests initially contained one atmosphere of air. The steam is distributed inside the vessel by the steam distributor arrangement shown in the figure. 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 full length, uniform distributor was expected to produce the most limiting steam condensation conditions.
To establish the total heat transfer from the test vessel, measurements are recorded for steam inlet pres:cre, temperature, and condensate flow and temperature from the vessel.
Twenty-four thermocouples located on the outer surface of the vessel's 0.375 inch thick steel wallindicate the temperature distribution aver the height and circumference of the vessel.
The measured temperatures are weighted by the respective vessel wall areas sensed by the thermocouples and summed 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 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 conducting a velocity traverse in the cooling air annulus using a hot wire anemometer. The heat transfer to the 5
WESTINGHOUSE CLASS 3 NPR-RPT-92-003 Resision 1 cooling air (i.e., its temperature rise multiplied by its specific heat and its measured flow rate) provides a second 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 all but the 1
pressure vessel, provides three floors for workers to assemble components, install instrumentation and conduct instrument traverses.
3.2 FOUNDATION AND TOWER l
The foundation for the pressure vessel and tower is a 121/2 foot square pad of reinforced:
i concrete located next to Building 301 at the Westinghouse Science & Technology Center.
The tower was constructed using 6 inch square structural tubing for posts and 6 X 4 inch l
angles for plationn :upports. 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 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
- i weight is approximately 8,600 pounds. With the air baffle in place, the assembly can withstand winds in excess of 100 miles per hour.
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. Overall length of the vessel, including the heads, is 286 inches. At the I
bottom of the vessel, a standard 150 pound class,20 inch weld neck flange is welded into the i
head on the vessel centerline. The 20 inch diameter opening formed by the weld neck l
flange serves as a manway. The 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 j
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:
4 steam distributor. A threaded 1 inch pipe nipple is welded into the 20 inch blind flange to.
provide for the condensate drain.
1 i
6
'f
WESTINGHOUSE CLASS 3 NPR RPT-92-003 Revision 1
)
i 1
.m, _
i
-- 4 Ft.Dia Asialf an(Not used) h I! i
- v, i \\
(
h 51/2 Ft.Dia.Plemoglass Annulus Wall i
I I
3 f t. Dia. x 24 Ft. High Pressure
- Vesselwrth 18-20 Psia N and a
H 20-80 Psia steam
-- 5 team Distributor Pipe Perforated Shield
=:n=r
==
Ia
- ,p y 34 Ft. High Tower with Platfor ms at ) Elevations mesme N
u==r
.a==mr H
i i
l Fr
\\
Air in Airin g
g L
Li ip Pg FE i t 1%
Steam inlet Condensate Outlet Figure 3.1 1. Section View of HWRF Small Scale Containment Cooling Test.
7 T
WESTINGHOUSE CLASS 3 NPR-RPT-92-003 Resision 1 t
T' l
4
..CMy 4
j, E(
s l
i l
4'~
. w (.4 i
M
'"5-%$.:
l i
\\
1 1
~
l r-- -
l
[. 8 ~
_=-.:
,.}f'
~
l r-J.
--~. -i.-~ ~ :.
t-s:.y -
i Figure 3.12. Passive Containmnet Cooling System Test Apparatus.
1 8
WESTINGHOUSE CLASS 3 NPR-RPT-92-003 Revision 1 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 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.
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.
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 sandblasting the surfaces with G-40 size steel shot.
3.4 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 condensate 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 11/2 inches of glass fiber insulation. Electrical trace heaters are 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) are maintained for all tests. At the test tower, steam is delivered from the main 4 inch supply manifold to the test vesselinlet through a 2 inch insulated pipe.
A wye 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). The steam supply pipe size is maintained at 2 inches 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.
9
WESTINGHOUSE CLASS 3 NPR-RPT-92-003 Resision 1 3.5 STEAM INLET TO TIIE VESSEL FOR CONTAINMENT SIMULATION The pressure vessel provides for installation of different types of steam distributors. The
" uniform" steam distributor is used for all HWRF Small Scale Containment Cooling Tests.
The " uniform" distributor consists of six 4 foot long sections which are connected by pipe couplings. The " uniform" distributor extends from the steam inlet nipple up into the neck of the weld-neck flange at the top of the vessel. The weld-neck flange retains 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 is surrounded by a 3-1/2 inch outside diameter,0.%5 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. The shield tubes slide over the inner distributor sections and rest on the pipe couplings which join the assembled distributor sections. The inner distributor section and shield tube for one section of the uniform distributor are shown in Figure 3.5-1.
3.6 CONDENSATE HANDLI'NG Condensate that is formed on the inside wall of the pressure vessel flows down and collects in the neck of the 20 inch flange at the bottom of the vessel. The condensate is removed through a 1 inch pipe connected to a liquid drain trap (vapor trap or steam trap) and cooled below 90 F by a condensate cooling heat exchanger. The cooled condensate is collected in a weigh tank consisting of a 55 gallon drum which rests on an electronic scale. The 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 draining when the weigh tank is filled.
3.7 EXTERNAL COOLING ANNULUS AND AIR DUCTING The HWRF Small Scale Test Matrix specifies three series of tests which use three different cooling air annulus widths. The cooling air annulus is formed by a transparent acrylic cylinder installed around the pressure vessel. Series 1 tests were performed with a 15 inch 10
WESTINGHOUSE CLASS 3 NPR-RPT-92-003 Revision 1 annulus using the same acrylic cylinder used for previous AP600 PCCS tests. A new acrylic cylinder which formed a 3 inch annulus was fabricated for the Series 3 tests and an additional new acrylic cylinder which formed a 5 inch annulus was installed for the Series 2 tests.
The 15 inch air cooling annulus was fabricated from 1/4 inch thick acrylic sheets hot formed to a 33 inch 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 aluminum bars. Tne components were assembled, using screws 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 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 bottom of the acrylic cylinder was located at an elevation 35-3/4 inches above the bottom of the vessel even with the top of the inlet air duct.
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 wall and the 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 heasy 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 to the air heating coil.
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 inch high inlet duct was removed.
These modifications provided a 31 inch high opening around the circumference of the 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 by aluminum ribs attached to the original 15 inch annulus baffle. The gap between the 15 inch annulus bafile and the 3 inch annulus baffle was sealed at the top and bottom using a washer type ring cut from styrofoam sheet to prevent air from short circuiting the cooling air flow path between the 3 inch baffle and the vessel wall.
11
WESTINGHOUSE CLASS 3 NPR RPT-92-003 Revision 1 The 5 inch air cooling annulus was installed and supported by the 15 inch baffle in this same fashion as the 3 inch annulus. In the 5 inch annulus configuration, provisions for installation of an orifice were provided to permit varying the annulus loss coefficient by restricting the air flow at the annulus inlet. The inlet flow orifice consisted of an annular disc cut from 3/4" thick plywood to fit into the 5 inch wide annulus gap at the inlet. Twenty-four equally spaced 3.5 inch diameter 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 plugging 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 installed, 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. The fan, however, was physically left in place as the 48-1/2 inch diameter,36 inch high fan housing formed part 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. The mass of condensate collected in the weigh tank was measured using an electronic scale. The scale reading was communicated to the Data Acquisition System (DAS) over RS232 interface and recorded, along with the coinciding time, at the same sampling rate selected for recording temperature measurements.
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.
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 and the condensate leaving the vessel were determined 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 the corresponding time duration. The heat input to i
13 j
i
WESTINGHOUSE CLASS 3 NPR-RPT-92-003 Revision 1 the vessel or the total heat transfer from the vessel was determined by multiplying the difference of the steam and condensate enthalpies by the condensate mass flowrate.
Pressure measurements along the air cooling path, were not obtained due to the extremely low pressure drops inherent in natural convective cooling experiments. The overall pressure drop can be inferred analytically by calculating the buoyancy force from the measured temperatures at the coding annulus inlet and outlet.
Pressure measurement along the air cooling path will be attempted for the 12rge Scale Confirmatory tests.
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 instal'ed in a 1/32 inch deep,1/32 inch wide groove approximately 3/4 of an inch long and peened into place. The grooves 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. The temperature measurement locations are shown schematically 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. 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 apart 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 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 three sets of thermocouples on the vertical side wall was 0.065; and the lower three sets of thermocouples 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.
The temperatures measured by each of the three thermocouples in a set were averaged and multiplied by the respective fractional area on the vesselin 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 temperature.
14
WESTINGHOUSE CLASS 3 NPR-RPT-92-003 Revision 1 3.9.3 Containment Annulus Air Flow and Temperature An ALNOR Thermo Anemometer was used to measure the-air velocity in the 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. Due to the nature of the imtrument operating characteristics and calibration procedures, velocity readings obtained using the ALNOR instrument are referenced to standard atmospheric conditions. To obtain the actual local annulus air velocities, the test velocity measurements were corrected as follows:
Va = Vi x CF Where:
Va = actual air velocity (ft/sec)
Vi = velocity indicated by Thermo Anemometer (ft/ min)
CF = correction factor = ds/da = 0.075 *(459.7+Tl)/1.325*Pa ds = air density (Ib/cu ft) at standard calibration conditions da = actual air density at local temperature and barometric pressure Tl = local air temperature ( F) at velocity measurement location Pa = ambient pressure (in.Hg)
The local annulus air temperature measurements were obtained by performing air temperature traverses at three circumferential positions at each of three elevations corresponding with the velocity measurement elevations. Each air temperature traverse consisted of nine temperature measurements across the annulus width.
The average air temperature entering the annulus was measured using three thermocouples, spaced 120 apart, located in the annulus inlet region. 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 ambient air temperature, annulus inlet and outlet temperatures and annulus air temperature traverse measurements on an elevation weighted basis.
The cooling air mass flowrate was calculated as a sum of the products of the local annulus air velocity, the corresponding local air density (based upon the air temperature traverse data) and the flow area fraction assigned to each velocity measurement. The purpose of this calculated air flow is to determine the flow regime (turbulent or laminar) and the heat transfer regime (forced or free convection) in which the test operates, i
15
WESTINGHOUSE CLASS 3 NPR-RPT-92 003 Revision 1
~D Outlet Air Temperature, %
3 Sets of 3 TCs 4gh Vessel Head Temperature
- D8 s
a g3 and Heat Flux.3 Pairs of
,1 TCs at 10 7/8 in. &
_,g 16 in. Radii i
di a
I Vessel Wall Temperature -
e and Heat Flux.3 Pairs of TCs 5 paced t20*at tach of 6 I
flevations
_g i
t i
me i
i l
l H1 g
4 Outer Eaffle Wall g
,1 l
g.
Temperature 4 O
[
Elevatiores i
gg l
5 6
6
-48 I
3 i
Pressure VesselWall -
-13 0
{
t I
-li 5 15 inch Air Annulus -
a a
i
_p [
Baffle Wa5
-n j
.f i
/
1
~,
inner AnnulusWall I
Temperature l
e
~8 Series 2 & 5eries 3 i
Only 4 tievations i
i
~'
e s
a inner Annulus Wall
-4 Series 2 & Series 3 i
Only i
-5 l
i
- ' a Inlet Air Temperature.
=
3 TCs Spaced 120' N
s
-3
(.:
c4 6ntet Air -=
~
Duct F
-l i
s Steam truet Temperatuce %
.)
L.J Condensate Dra. Temperature 1
in Figu re 3.9-1.
Locations for Vessel WallTemperature Measurements, Baffle Wall Temperature Measurements. Containment Annulus AirTemperature Measurements,and Inlet Steam and Condensate Temperature Thermocouples.
16
WESTINGHOUSE CLASS 3 NPR-RPT-92-003 Revision 1 The heat loss from the condensing steam inside the steel vessel wall consists of several components.
1.
Conduction through the vessel wall.
2.
Convection to the air in the cooling annulus from the surface of the vessel wall.
3.
Radiation from the vessel wall to the baffle across the cooling annulus.
The heat radiated across the annulus is split the following way:
1.
Convection from the baffle wall into the air in the annulus.
I 2.
Conduction through the acrylic baffle.
Finally, the heat that is conducted through the baffle wall is divided as follows:
Convection from the outer baffle wall to the environment.
Radiation from the outer baffle wall to the environment.
For a typical test,100 percent of the heat from the condensing steam is conducted through the steel vessel, wall,45 percent enters the cooling air via convection from the steel vessel wall, and 55 percent is radiated across the annulus to the baffle wall. The heat radiate across the annulus is divided into 15 percent of the total heat entering the cooling air via convection, with the remaining 40 percent conducted through the acrylic baffle wall. The heat transferred through the baffle wall is divided evenly; 20 percent natural convection to the environment,20 percent radiation to the environment.
3.9.4 Annulus Wall Temperatures The outer surface temperature of the 5 inch annulus wall was measured using four 0.032 inch diameter stainless steel sheathed copper-constantan thermocouples attached to the outer surface of the acrylic 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 the outside surface of the outer (15 inch annulus) acrylic cylinder at locations adjacent to the thermocouples installed on the inner (5 inch annulus) cylinder.
The inner (5 inch) and outer (15 inch) annulus wall temperature measurements were used to calculate the temperature differences across the annulus walls and evaluate heat losses due to convection and radiation from the annulus walls to ambient air.
17
WESTINGHOUSE CLASS 3 NPR-RPT-92-003 Revision 1 3.9.5 Wind Speed and Direction A weather vane / anemometer was mounted on the roof of the building adjacent to the test tower approximately 12 feet above ground level. The wind speed and direction indicated by the anemometer were continuously monitored and recorded by the data acquisition system; this data was used to evaluate the local wind effects on steady state test conditions.
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 processed by a data acquisition system.
Thermocouples were connected to the system by 20 AWG, 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 were 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, along with the condensate weigh tank output, to a computer for display and storage on a floppy disk.
4.0 TEST CONDITIONS The test conditions examined by the HWRF Small Scale Passive Containment Cooling Tests are listed in the test matrix provided as Table 4.1. 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 1 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.
18
WESTINGHOUSE CLASS 3 NPR-RPT-92-003 Revision 1 Tab!< 4.1 HWRF Small Scale Containment Cooling Test - Test Matrix
. O.,b i
19
WESTINGHOUSE CLASS 3 NPR-RPT-92-003 Revision 1 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.
5.0 RESULTS 5.1 FINAL InVRF SMALL SCALE TEST RESULTS Final test summaries for the Series 1, Series 2 and Series 3 HWRF Small Scale PCCS Tests are provided as Tables 5.1-1 through 5.1-3. Since the test analysis effort has advanced well beyond the initial development stage, the final test summaries have been condensed to include only measured test parameters; calculated results included in the preliminary summaries have been deleted.
An overall summary of the measured vessel outer surface temperatures for each of the HWRF SST tests is provided as Table 5.1-4; a summary of the measured annulus air velocities is provided in Table 5.1-5.
The final test results represent average nominal steady state conditions for each of the tests.
The results were obtained by averaging the test data collected during the time interval throughout which annulus air velocities were measured and recorded.
The HWRF SST data reduction techniques were revised, as the test program progressed through each of the test series, to reflect knowledge gained from previous tests. At the conclusion of the final test series, the data reduction process was repeated for each of the previous test series to provide verification of the preliminary results.
The data will be used to develop an air cooling heat transfer correlation to be included in the GOTHIC containment analysis code. A sophisticate analytical model of the Small Scale Test was developed using the TABACCO code [Ref 2.6]. This code allows the user to specify the vessel wall temperature profile, air inlet temperature, air cooling path hydraulic characteristics, and heat transfer correlation. The code then calculates the air heat pickup, baffle wall temperature profile, air pressure drop, and the air velocity in the annulus. Each of these parameters are compared to the measured values from the tests to assess the applicability of the heat transfer correlation.
Agreemen; between the measured temperatures and those calculated during pretest predictions using TABACCO was found to be very good, while the measured velocities were found to deviate somewhat. The velocity measurements are considered adequate to verify 20
WESTINGHOUSE CLASS 3 NPR-RPT 92-003 Revision 1 the flow and heat transfer regirne, but should not be used to verify the heat balances for the
- tests, i
The consistency of the HWRF SST data is also reflected by Figures 5.1-1 through 5.1-3 which represent the vessel axial outer surface temperature profiles for each of the Small Scale Test series. Temperature profiles which deviate from the norm, such as the plot for Series 2 Test Run 64 in Figure 5.1-2, can be attributed to some difference in the initial test conditions; in this specific instance, the non-condensible gasses were vented from the vessel as a result of a failed condensate drain line. Slight differences indicated by the plots for Series 2 Run 67 and Run 69 are attributed to the effects of the annulus inlet orificing installed to vary the annulus loss coefficient; Run 61 and Run 62 were performed in the nominal annulus configuration with no restriction while Runs 67 and 69 were conducted with the orifice installed in the annulus inlet. The plot for Test Run 56, shown in Figure 5.1-3, represents a similar case in which a valve was opened during test start up resulting in the venting of non-condensible gasses from the vessel. While no specific event is noted for Test S104, Figure 5.1-1, it appears that some amount of air was also vented from the vessel during this test as evidenced by the flattened temperature profile and elevated lower vessel wall temperatures.
P 21
t t'
kmGdzOIOCk or>
?bi@.
s I68-1 se i
re S
t se T
m ey t r s a ym Sgm nu iS l
ot os CeT 1 t
)
nh 1 et 5 mid enW i
lba at s T nu olu Cn en vA i
sh s
c a n Pi e5 la (1 c
S l
l a
m S
FR W
H
=
M
,rGdzO OCCm Or>
w n
I D
eh$8m
? j: = -
2 se ire S
tse T
mey t
r sya S m gm n u i S lct os Ce 2t Tn) 1 eh Jw t
5 md eniaW l
i bat s Tn u ol Cun e n v A issh ac P n 1
e 5 la(
c S
lla m
S FR W
H U
'[.
h b
mOdZOI em O >
m m
xmW@8m
%}s= -
3 se ire S
tse T
me tsyS yr ga im n
om l
ou CS 3t tns e
1 e m )T 5e ns Py lbal i u at u T nnon C A eh v
c is n
=
siaP (3 e
lac S
l la m
S F
R WH wA' a
1
WESTINGHOUSE CLASS 3 NPR-RPT-92-003 Revision 1 l
Table 5.14 HWRF Small Scale Passive Containment Cooling Test Vessel Surface Temperature Summary 3
9 h
P a
1 L
- I t
t b
a
~
n WESTINGHOUSE CLASS 3 NPR-RPT-92-003
'l
-Revision 1-I Table 5.15 HWRF Small Scale PCCS Test - Measured Annulus Velocity Summ3ry.
l
~
1 i
.[
e E
P t
l ct,b..
i I'f i
t
.h i
i i
h l
(
1 t
}
{
,{
n i
6 26 b
n WESTINGHOUSE CLASS 3 1
' NPR-RPT-92-003.-
Revision' 1 i
i I
s
.12
?
k.'
- i 3
2 E
E-4 8
.g
=
't 2'
8 i
N 10 l
O, O
.s.
2 m
.. - V O
- 4-g
.g o 'h a
e m.
.i
=.
E ll [].
m b-M W=
J
?
wi a
E i
i d - dW3130VdBDS B3100 73SSBA DAV l
27
l -:
- gg l
l AVG VESSEL OUTER SURFACE TEMP.- F l
4 j.
5.
7 3*
f~
is
=
4-z'
[1 ll w
3 E
3 2 m
-C C
i-2.
Zz T
-: m m 5
y
_a oc.
1 ft) -
)(
~~q%-.. ?
- m. T C C t
zz a
e' m
'. N -
c to
.-e.
X
)(
- r i
I i
=
C c.
.z
.'4 ~
E.
i 9
i Y
8
.3 5
9-
.(-
I uo! spas E00-76.LdE-EdN -
C SSVlO 3SOOHON1193M' c-r.
- ~..._,
6Z t
i 7
AVG VESSEL OUTER SURFACE TEMP - F m
=
l E.
?
':-f*
5 0
ll z
'h 3 3 3-C.C a.
Z Z g
X c
gh I 3 Y
C C zz
?
mm s,
W -'
2 2
) )(
2 R
x3 C C t
zz M8
- 5. -
- o.
9 1-F 4
i j
1-I uo! spay C00-Z6-idE EdN l
C SSVlO 3SOOHDN1193M
,