ML19276H111

Proposed Outline for Test of Cooling Coil Performance at Elevated Temps & Pressures.

ML19276H111
Person / Time
Site:	Three Mile Island
Issue date:	12/16/1968
From:	AMERICAN AIR FILTER CO.
To:
Shared Package
ML19276H110	List: ML19276H109 ML19276H111 ML19276H114 ML19276H115 ML19276H117 ML19276H119
References
RS-1044, NUDOCS 7910100509
Download: ML19276H111 (7)

Text

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PROPOSED OUTLINE FOR TEST OF COOLING COIL , ,

PERFORMANCE AT ELEVATED TEMPREATUPIS AND PRESSURES

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PROPOSED OU'ILINE FOR TEST OF COOLING COIL PERFOR".ANCE AT ELEVATED TD:PERATURES AND PRESSURES.

Prepared by CAG ENGINEERING DEPARL1ENT -

AMERICAN AIR FILTER CO., INC.

LOUISVILLE, KENTUCKY _

Prepared for METROPOLITAN EDISON C0::PANY READING, PENNSYLVANIA

'Jork Accomplished under:

PURCllASE ORDER 93342 SUBMITTED FOR CUSTOMER APPROVAL 16 Decembdr 196S 1415 167

PO 1 uhid u w RS 1044

1. Materials of Construe:, ion - identical, 5/8 inch 0.D.

Copper tubc, heavy wall - 0.049 inch, 0.007 inch copper fins spaced 6 per inch, copper headers with schedule 80 rteci connections (Test coil uses screwed connections, Full Coil uses ASA flanged connections), cicanabic fit-tings with high temperature 0-rings.

During tests, results will be considered valid if performance as given by water side data agrecs with perform..nce as given by gas mixture side data. Sufficient test data vill be generated to demonstrate reproducibility.

III. DESCRIPTION OF APPARATUS The apparatus used to test this coil has been previously used to test cooling coil performance and can generally be considered to consist of three systems which are the pressurc vessel, the test section, and allied instrumentation. A brief description of these systems is given below.

1. Pressure vessel and Mixture Circulation System. The steam-air mixture will be circulated through a closed loop system by means of a centrifugal blower. (See Figure 1.) On 1 caving the blower the mixture is completely contained in the duet system of the test section and is expelled from this duct af ter leaving the coil. This test section, discussed later, is completely sur-rounded by the 42 inch I.D. insulated shc11 capabic of with-standing the required pressure. The section containing the cooler is slightly larger to accommodate the coil manifold and accompanying piping. After leaving the cooler the mixture enters a transition section and is recirculated back to the fan inlet through the 12 inch I.D. duct provided for this purpose. A large blank-off plate is attached to the fan outlet to prevent the mix-ture's returning directly to the blower and not being returned through the recirculate duct.

In order to insure proper mixing, the steam and air are injected upstream of the blover. Compressed ai r is provided by the normal

" plant" air system and the steam is produced by a large (600 bhp) boiler. The mi:.ture flow is controlled by means of a damper on the Ian inict.

2. Containment Cooler Test Section and Water Sunply System. The test section wi;l consist of the cooler and all of its attached duct system of the sizes indicated in Figure 1. The cooler will be a 24 x 24 inch section idcutical in construction to the " full size" unit as shown on AAF Drawing No. MC Thermocouples will be placed in these ducts before and after the cooler to indicate the inlet and out1ct, wet and dry bulb tempera-ture. A rnoisture separator pad, of glass matte construction, vill be installed to remove any entrained water droplets present.

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P00R O H M *m Thermoccuples will also be placed in the water manifold as close to the coil as is practical to give an accurate indication of the et mer ' s performante and minimize any water temperat rc men-suremerit crror.

Because of heat balance inaccuracies encountered in previously run tests, a sheet metal housing will be installed over cach end of the coil having the return bends. This will be donc to prc-vent an unmeasurable heat gain by conduction to these parts due to their presence in the hot atmosphere.

Cooling water will be supplied to the coil from a large tank by means of a centrifugal pump. The supply will be arranged to pro-vide water flow through the coil counterflow to the mixture flow.

Valves will be provided to regulate the flow and on-line water flow measurement will be used to indicate quantity. The cooler inlet temperature uill be maintained through the addition of colc water to the supply. Any excess will overflow into the drain line.

The condensate will be collected in the sump where the temperature will be measured. The flow will be nicasured by a tapered tube flow meter as it is drained from the system. It will be returned to the boiler feed water system.

3. Containment Conler Instrumentation. The mixture flow will be mca-sured utilizing the sharp-edged orifice method. The resulting pressure drop will be indicated with a U-tube manometer. The sys-tem pressure will be measured by an " instrument" quality Bourden gage. The absolute pressure is then determined by addir.g this pres-sure to the barometric pressure measured in the same area by means of a mercury column barometer. The w.et and dry bulb temperatures will be measured by means of thermocouples. The wet bulb thermo-couple will be covered with a cotton wick aad supplied with water from time to time. All temperatures will be indicated and recorded utilizing a 24 point Esterline-Angus recorder.

A stop watch will be utilized to assure accurate time measurements when setting and monitoring the coolant flow rate. The coolant circulation measurement loop consists of a collection tank and suitable valving. The water can be diverted to a scales where weight rate of flow is determined without disturbing system opera-tion. The flow will be adjusted by means of' a ' control valve on the downstream side of the cooler.

IV. EXPERIMENTAL PROCEDURE The following procedure will be used to determine the heat transfer characteristics of the contvinment cooling c, oil.

1. The air circulation and water supply system will be started.

The steam and air rates will be adjusted, as necessary, to pro-duce the desired condition of temperature, pressure and humidity.

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2. The blowcr damper will be adjusted to give the proper mixturc flou

3. The cooling water flow rate and temperature will be adjustcd to give the required conditions.

4. Steps 1, 2 and 3 will be repeated as necessary until stabili:cd conditions are reached.

5. Data vill be recorded utilizing all instrumentation to determine the required temperature, pressure and humidity of the :ixture at the inlet and outlet. Tne temperature and flow rate of the cooling water w ill be verified. The condensate temperature and flow rate will be recorded.

6. The coil performance can then be determined knowing the cooling water flow rate and its temperature difference. The heat gained by the water system can then be verified by computing the heat lost by the mixture.

A successful test run shall be defined as operation at steady state conditions for a period of fifteen (15) minutes or more. Temperatures, pressures, pressure drops, and flow rates must have reached these steady state icvels and damped out excessive oscillations (The con-trol adjustments normally will allow small oscillations while not per-mitting larger variances). Steady state operation is evidence of the fact that condensate is not building up on the heat transfer surfaces.

Any degree of such build-up would rapidly change temperatures and pres-sure drops due to the very high condensation rates in this type service.

Innsmuch as there are many pieces of data to be observed, as well as a likelihood that any one test run will not be successful in achieving a heat balance (described hereafter), it is impossible to prepublish a rigid test schedule.

During a nominal period of stay of test witnesses (two or three dyas) there will be ample opportunity to evaluate the test procedure, ob-s,erve data being recorded, and gain a working knowledge of the test equipment. For witnesses to stay through the entire testing portion of the program, will require residency for a much longer period in the event of unplanned shutdowns and rework.

V. CALCULATION PROCEDURE Upon completion of a test run in which data appears to be sound (as previously defined), a trial heat balance will be made using the rater side (or coolant) data against the air side (or mixturc) data. If the heat transfer balance is made uithin reasonabic accuracy, the strip chart and all other recorded data sh:11 be appropriately r.arhed uith a test identification number for later reference. (Test data for runs which do not balance will not be so coded).

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/h51 RS 107.4 Density and mixture flow rate calculatio:u, for the trial hcat balcncc will be carried out in the usual manner, i.e. based on partial pres-sure laws. Eqt" tion (1) definds the density calculation.

PM +PM s s a a (1) p = 10.73(T + 459.7) where p = density, lbs/cu.ft.

P = partial pressure of air, psia I M = molecular weight of air (28.97) 'el ab P,= partial pressure of steam, psia M,= molecular weight of steam (18.)

T = temperature, F Equation (2) defines the volume flow rate calculations at conditions.

CFM = 1096.5 C A (

do i where CFM = volume flow rate, cubic feet per minute C

d

= rifice constants, dimensionless (determined through I calibration in place)

A = orifice flow area, square feet OPD = orifice pressure drop, inches water gage p = density, lbs/cu.ft.

The experimentally determined performance characteristics of the test coil,once established, will be compared with computer generated test coil performance characteristics. In this manner a direct relation-ship will be shown betscen computed results and those that have been measured experimentally. This comparison is made for each of the run conditions and is assumed to remain uniform regardless of coil size.

(Past test programs on similar coil configurations bear this out.)

In the case of the present test, the computer solution for the full sized (45 inct long) coils involves only accounting for the different length. Applying the ' comp'arison factor' to computer generated full scale coil data will demonstrate expected performance of the full sized coil bank in service.

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