ML20059H395
| ML20059H395 | |
| Person / Time | |
|---|---|
| Site: | South Texas  |
| Issue date: | 11/01/1993 |
| From: | Starks V HOUSTON LIGHTING & POWER CO. |
| To: | |
| Shared Package | |
| ML20059H343 | List: |
| References | |
| MC-6429, MC-6429-R, MC-6429-R00, NUDOCS 9311100072 | |
| Download: ML20059H395 (85) | |
Text
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STP361(1248) SOUTHTEXAS PROJECT CALC NO. ' MC $ 29 SHT J OF M $ REV. PREPARERIDATE REVIEWERIDATE ELECTRICGENERATINGSTATION HOUSTONLIGHTING& POWER O V//' #-i-13 $ nJi-o ; GENERAL COMPUTATION SHEET 1 SUBJECT UNIT Is ! h TABLE OF CONTENTS SECTION PAGE ! I OBJECTIVE 6 j II SCOPE 7 , j III RESULTS & CONCLUSIONS 7 l IV DISCUSSION 8 V REFERENCES 15 l i VI CALCULATION 18 f v A. Analyze 300 Ton chiller capacity at higher than norma chilled water outlet Temperature. 18 t
- Shop Test
. Maximum Shaft Horsepower ;
- Steady State 0 48 *F Chilled Water
+ Maximum Transient- t B. Analyze Conditions Related to Startup of an Idle Chiller. 25 C. Condenser Heat Transfer Model. 27 ,
t D. On-Set of ' Cold ECW" Conditions. 32 l t E. ECP Minimum Temperature Expectations 34 i F. Post LOCA Radiation Levels in CCW/ Chiller Rooms. 35 l G. Single Train HVAC Operation. 36 .; H. Restart of Operating Chiller 38 i I. ECW Flow Balance 41 l J. Minimum Load Considerations 42 7 K. Chiller Requirements during Modes 5, 6, & Defueled. 44 L. Capacity of Hot Gas Valve. 48
i HI PROJECT N- SW 4 OF M ELECTRICGENERATINGSTATION' REV. PREPARERIDATE REVIEWERIDATE HOUSION UGHTING & POWER o gg g_7; g g n lg - GENERAL COMPUTATION SHEET : SUBJECT UNIT is !
~i APPENDICES ,
- 1. 300 Ton Chiller Compressor Model Results 49
- 2. 300 Ton Chiller Compressor Model Formulas 50
- 3. 300 Ton Chiller Condenser Model Results ;
- a. 300 Ton w/ 48 *F Chilled Water 53
- b. Maximum Load w/ 48 *F Chilled Water 54
- c. Trial Max. during Start Up 55
- d. Maximum Load during Start Up e. Shop Test Results 57 -
- f. Max. load w/ 225 gpm 58
- g. Limited Load w/ 190 gpm 59-1
- 4. Chiller Condenser Model Formulas
- a. 300 Ton 60
- b. 150 Ton 64 .
- 5. R-11 Properties Spreadsheet ;
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- a. Typical Spreadsheet Results 68- ,
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- b. Spreadsheet Formulas 69 !
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- 6. 150 Ton Chiller Condenser Model Results ;
I , a. 150 tons at 110 *F ECW inlet. 74
- b. 159 tons at 53 *F ECW inlet. 75
- c. Maximum Load during Start Up 76
- d. Min. load & min. temp. 77 1
sTe ssw24e> CALO NO. Mc-6429 SHI s OF AC- i SOUTHTEXASPROJECT REV. PREPARERIDATE REVIEWERIDATE _ ELECTRICGENERATINGSTATION-l. HOUSTON LIGHTING & POWER o Yd //+13 th6 1iido GENERAL COMPUTATION SHEET SUBJECT UNIT Is
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- 7. Start Up of Operating Chiller
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- a. Air Handling Unit Initial Loads 78- -}
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- b. Train A Chill Water Data 79
- 8. 300 Ton Chiller Minimum Load Cases i
- a. 121 Tons & 240 gpm 81 .;
- b. 100 Tons & 240 gpm 82
- c. 100 Tons & 250 gpm 83 l t
- d. 100 Tons & 200 gpm 84 f ATTACHMENTS ;
A. Typical Centrifugal Compressor Curve 85-
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1 [ i E I l i I
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1 STP 361 (1248) CALC NO. MC-6429 SHI 6 og - 95 SOUTHTEXAS PROJECT REV. PREPARERIDATE REVIEWERIDATE ELECTRICGENERATINGSTATION HOUSTONLIGHTING & POWER o 4 ff_f 93 gp u ,1. q GENERAL COMPUTATION SHEET SUEUECT UNIT ls j i I I OBJECTIVE j i Analyze operation of the essential chillers during cold Essential !' Cooling Water (ECW) system conditions to determine if the chillers are capable of starting and operating unattended for the l required duration following a design basis accident. ! i Recently, three technical audits have'been performed on the _ Essential Chilled Water system. One audit was performed by the : NRC, one internal audit was performed by the QA department, and a- ' third party review was performed by CYGNA. Their findings are ! documented in References 3.B, 3.C, & 3.D. '} i Reference 3.B discusses observations on the design, maintenance, j and testing of the Essential Chilled Water System. It states j that the STPEGS had never analyzed or demonstrated the ability of i the system to function under design basis low heat load l conditions. If an accident occurred during cold weather and all ' chillers operate, the chiller would be under loaded causing , surging and failure,_resulting in loss of CH system cooling of safety-related equipment. , i Reference 3.C identified similar concerns prior to the NRC audit. It stated that an evaluation has not been performed to determine j i the effect on the Essential Chilled Water system for the j i simultaneous operation of all three chiller trains (six chillers) during winter heat loads in conjunction with low Essential l
. Cooling Water system temperatures. The chiller operation becomes t very sensitive when entering condenser water temperature is l bellow 55 *F. The chillers will start when the return chilled water temperature is 25 *F colder than the return chilled water temperature. However, the condenser water temperature must be !
maintained higher than the return chilled water temperature or -! the system will shutdown on low evaporator pressure or : temperature. : Reference 3.D identified similar concerns on essential chilled water rystem operation. In addition, Reference 3.D identified a {' concern regarding the suitability of manual actions in the chiller roons because of post LOCA radiation dose rates, as : currently reported in the design basis. j I i t e
STPb 1(1248) g g - SOUTHTEXAS PROJECT REV. PREPARERIDATE REVIEWERlDATE ELECTRICGENERATINGSTATION HOUSTONUGHTING & POWER b 1//k - //+6 % img GENERAL COMPUTATION SHEET SUBJECT UNF is . II SCOPE This calculation applies to both Units 1 & 2 in all modes of operation during " cold ECW" conditions. III RESULTS & CONCLUSIONS A. The 300 ton essential chillers can start and operate successfully, without operator intervention, following_a design basis accident, with.ECW flow rates manually set at 240 gpm. In modes 1 through 4 this conclusion is valid with ECW supply temperatures down to and including 42 *F. B. In modes 1 through 4 during cold ECW conditions the ECW flow through the 150 ton chiller must be stopped. This is required to prevent " free cooling" wh.n ECW. temperatures are very cold and " free heating" when ECF temperatures are above chilled water temperatures. C. Raising the chilled water outlet temperature to 48 'F without changing the maximum load limit setting would allow an increased rated output of the 300 ton chiller. This effect has not been utilized in this calculation, but may be utilized in the future if sufficient information can be cbtained from York to determine and justify a precise value. D. Starting an idle chiller involves heat transfer loads on the evaporator and condenser considerably in excess of the rated chiller load. The 300 ton essential chiller could operate at required loads with the load limiter set at about 80%, which would act to reduce the peak load when starting an idle chiller. This would allow operation at lower ECW flow rates and lower ECW temperatures. Similarly to the previous item, this has been not been utilized in this calculation due to insufficient information for full documentation. E. The radiation level in the CCW / Essenti?1 Chiller rooms,. including the stairwell used for access, will be less than 250 mr/hr eight hours after a design basis LOC 4. This is an independent conclusion. No need is foreseen to realign the chilled water or ECW system for several days following the design basis event.
STP 361(1248) CALC NO. un-na?o SHT R OF M SOUTHTEXAS PROJECT REV. PREPARERIDATE REVIEWERIDATE - ELECTRICGENERATINGSTATION HOUSTONLIGHTING & POWER o V//- 't + f3 $, ta g GENERAL COMPUTATION SHEET SUBJECT UNIT Is l l F. " Cold ECW" conditions are entered from a range of conditions l defined as follows: I
- Above ECW supply temperature of 69 *F only normal ECW i and Essential Chilled Water system operation is allowed.
- Below an ECW supply temperature of-60 *F, only " cold l ECW" operation is allowed.
. G. Emergency Cooling Pond (ECP) temperature excursions below 50
*F are expected to be infrequent, while excursions below 45 i
*F are expected to be rare. Excursions below 40 *F should j be very rare, and probably will not occur if at least one of !
the Units is generating power and equipment is operated to 4 maximize heat rejection to the ECP. H. During " Cold ECW" operation, trains of ECW and Essential Chilled Water must be operated together, minimizing the time a between starting the ECW pump and starting the Essential l i Chiller in the train. This applies only to " operable" trains. Single train HVAC operation is acceptable with : respect to chilled water train loading and chiller operation l J a with " Cold ECW", but there are unrelated issues which j require further review. 1 IV. DISCUSSION , i The essential chiller consists of 3 major components, the l j evaporator, the compressor, and the condenser. Chilled water ~ flows through the tubes of the evaporator, transferring heat .l 1 through finned tubes to the boiling refrigerant. The vapor is j moved from the evaporator to the condenser by the compressor. l The evaporator operates at a pressure slightly below saturation i pressure for the leaving chilled water temperature. The vapor ; condenses in the condenser,. releasing its heat of vaporization to , t the ;ondenser cooling water (ECW in this case). The condenser. .l operates at a pressure slightly above the saturation pressure.of the cooling water leaving the condenser (disregarding the effects j of superheat). t I d i
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l STP 361 (1248) CALC NO. Mc-6429 $gi 9 OF BT SOUTHTEXAS PROJECT REV. PREPARERlDATE REVIEWERIDATE ELECTRICGENERATING STATION HGUSTONLIGHTING & POWER o (f( a_ ,- 17 % u-t- % GENERAL COMPUTATION SHEET SUBJECT UNIT ls The condenser is located in the upper portion of the chiller while the evaporator is located in the lower portion. The pressure difference between condenser and evaporator provides the motive force to return the refrigerant to the evaporator. The refrigerant flow in these chillers is controlled by a float valve located in the condenser portion of the chiller. The flow through the compressor is controlled by prerotation vanes (PRV's) located at the compressor inlet. This in turn controls the evaporator pressure which in turn controls the leaving chilled water temperature. As leaving chilled water temperature goes down the PRV's are driven in the closed direction. At a preset minimum position selected to prevent
" surge", the PRV's stop closing and the hot gas valve (HGV) starts to open. This provides a relatively constant compressor flow above the flow which would cause surge. The surge condition occurs when the compressor does not have the capability to produce enough head to overcome the resistance imposed. When the compressor reaches this point, the gas in the discharge piping back-flows into the compressor momentarily. Surging can cause l the compressor to overheat or can cause damage to the thrust bearing due to the rotor shifting back and forth from active to ;
the inactive side. If the PRV position set by the temperature control attempts to load the compressor motor above the maximum allowable load, as measured by motor current, a current limiting controller overrides the temperature controller and drives the PRV in the closed direction. The current limiting controller maintains the motor current between 102% and 104% of the preset maximum. The control mode reverts to temperature control when current drops to 98% of maximum. (Reference 2.B) The minimum required pressure differential between condenser and evaporator can be assured by ensuring the entering condenser cooling water is at a temperature greater than the entering chilled water temperature. However, the STP ECW system design does not include provisions for controlling ECW temperature. There are some limited ways to influence entering chilled water temperature, but this parameter is primarily a function of load. There will be occasions when the chiller must be operated with entering ECW temperature cooler than entering chilled water temperature. Before starting the idle chilled water train, the chilled water 1 l
STP 351 (1248) CALC NO. Mc- u 29 SHT 10 OF %i SOUTHTEXAS PROJECT REV. PREPARER 1DATE REVIEWERIDATE ELECTRICGENERATINGSTATION HOUSTON UGHTING & POWER o ff{ y.g3 $n, a_ m ; GENERAL. COMPUTATION SHEET SUBJECT UNIT is will be at room ambient temperature, which in almost any installation can be higher than normal cooling water temperatures. The chiller supplier's standard operating recommendations permits starting the chiller with entering , cooling water temperature up to 25 *F lower than entering chilled water temperature. York's recommendation that entering cooling water be no lower than entering chilled water is a rule-of-thumb which ensures a higher condenser pressure than evaporator pressure without i knowing anything more about the process. However, the condenser pressure is actually determined by leaving cooling water temperature. When the vapor temperature falls below the cooling i water temperature at any point in the tube, heat transfer stops , and the cooling water temperature does not increase through the remainder of the passage. Proper pressure differential for chiller operation can be maintained by automatic control of cooling water, or by an engineered analysis of the range of conditions the chiller can see when cooling water entering temperature is less than entering chilled water. York also recommends the velocity of water in the condenser tubes be maintained above 3.33 fps. Below this velocity, silt in the cooling water will tend to settle in the condenser tubes, ' reducing the effective heat transfer area or increasing the fouling resistance. In addition, the higher temperature rise , through the condenser and higher inside tube wall temperature due f to the lower inside heat transfer coefficient will increase the rate of calcium carbonate scale deposition inside the tubes. For , these reasons operating with reduced cooling water flow will require more frequent monitoring of fouling and more frequent ' cleaning of the condenser tubes. The condenser tubes have been visually inspected for scale and silt buildup, but to date no ; cleaning has been necessary (Reference 3.E) 1 The tube side velocity at 240 gpm is about 1.3 fps, below the j York minimum velocity recommendation. The ECP receives makeup ! water from well water and thus there is very little silt in the water. The scalc forming tendency of the ECP water is monitored i and controlled as necessary. The time spent in the reduced flow l mode will be limited, because ECP temperatures are usually above 60 *F even in the winter. Chiller condenser fouling will be monitored by inspections and/or performance testing. The design fouling factor of 0.002 for the condenser tubes is an extremely l conservative value which provides considerable margin against any I l
STP 361 (12" CALC NO. MC-6429 $gy 11 OF 2< SOUTHTEXASPROJECT REV. PREPARERIDATE REVIEVERfDATE : ELECTRICGENERATING STAtl0N HOUSTON UGHT!NG & POVER g) 1/pL g_493 g g pg ' GENERAL COMPUTATION SHEET , SUBJECT UNIT is i scale or silt deposits. These factors address the causes of i York's velocity recommendation. Analysis of post-accident heat loads (Ref. 1.A) demonstrated that lower chilled water temperatures cause increased chilled water loads, and that existing air handling units are sufficiently oversized to permit a significant increase in chilled water temperature. Here-to-fore the Essential Chilled Water system was l designed to control leaving chilled water temperature at 42 "F. ' The single temperature is somewhat misleading because the chiller temperature control effectively acts as a proportional controller, with a 3 *F proportion band (Ref. 2.B). Ideally, the chiller leaving water temperature would be 39 *F at minimum load ; and 42 *F at rated load. This difference is called the '
" throttling range" and is internally adjustable from 0 to 10 *F in the chiller control panel. Reference 1.A recommends the throttling range be reset to provide 40 *F at minimum load and 48
'F at rated load. This is primarily intended to reduce peak post accident loads to within the capabilities of the 300 ton chiller.
It will also result in a more stable control of leaving chilled water temperature, higher chiller load capability, greater margin ' from compressor surge, and more comfortable room temperatures in the EAB when operating without throttling flow through the EAB i cooling coils. Almost without exception in the past, a chilled water train has been operated with only one of the chillers operating, usually the 150 ton chiller, with the other chiller idle but operable. l During " cold ECW" conditions in particular this lineup has several undesirable features. The idle chiller will have chilled water flow, at return temperature, as well as ECW flow. With ECW colder than chilled water, the refrigerant will condense in the ! condenser and vaporize in the evaporator. Liquid refrigerant i will accumulate in the condenser because the condenser is at a lower pressure than the evaporator. If the difference is small the refrigerant level can increase enough to allow static head to return some refrigerant to the evaporator. This cycle is called
" free cooling" because heat is transferred from chilled water to condenser cooling water without running the compressor. Some chiller installations are designed to utilize this process when conditions permit, however, the STP chillers are not among these.
At STP this has the adverse affects of reducing the load to the running chiller and reducing the refrigerant inventory in the evaporator section of the chiller. The chiller is designed to operate and remain in standby with the majority of the
STP 361 (1248) CALC NO. MC-6429 $gy 12 OF S( SOUTH TEXAS PROJECT REV. PREPARERlDATE REVIEWERIDATE ELECTRICGENERATINGSTATION HOUSTON UGHTING & POWER D $ u 93 g g_m GENERAL. COMPUTATION SHEET SUBJECT UNIT Is _ refrigerant in liquid form in the evaporator. A reduced inventory of liquid in the evaporator on startup increases the sensitivity of the evaporator to pressure and temperature transients and thus makes a trip on low evaporator pressure (150 ton) or low evaporator pressure (300 ton) more likely. Starting out with a significant number of condenser tubes covered would also make the chiller more likely to trip on high condenser pressure when starting. For these reasons, ECW flow must not be allowed to flow through the condenser of an idle but operable chiller for any longer than necessary to start up the entire train in a controlled manner. It may be possible to run only the chilled water pump in conjunction with a running ECW pump. The " free cooling" effect is probably adequate to remove the heat added by the chilled water pump, and keep chilled water temperatures within the bounds assumed in startup analysis of an idle chiller. Continued ECW and chilled water flow through the condenser and evaporator of an idle chiller when ECW is warmer than chilled water return temperature should not cause refrigerant to accumulate in the condenser, because vapor pressure in the evaporator section will be lower than the pressure necessary to cause condensation in the condenser section. In this case the process can reverse and transfer heat from ECW into the chilled water system. This process is probably responsible for a significant portion of the current warm weather heat load. To our knowledge, this does not degrade the starting reliability of i the chiller but would adversely affect the energy cost of operating the chillers. It is probably more economical to , operate system with only the 300 ton chillers operable, the 150 ton chillers isolated, and the operating 300 ton chiller (s) partially loaded, than to operate the 150 ton chillers fully ; loaded. A small increase in evaporator pressure, such as will result from changing the rated chilled water outlet temperature from 42 *F to i! 48 *F, causes a substantial increase in chiller capacity. This ! will be demonstrated analytically in a,later section of this calculation. The increased evaporator pressure results in a lower specific volume of vapor in the evaporator and compressor ; inlet. The volumetric flow rate for a given mass flow rate will i be significantly less. Since the compressor is basically rated j for volumetric flowrate, the compressor is capable of moving more ! mass of refrigerant at a given head. In addition, the increased
._- .- -_ = _- . _ _
STP 361 (1248) CALC NO. MC-6429 SHT 13 OF M ! SOUTH TE)MS PROJdCT i REV. PREPARERlDATE REVIEWERIDATE l ELECTRICGENERATINGSTATION HOUSTON LIGHilNG & POWER D g g-f-73 % g_g_ % l GENERAL COMPUTATION SHEET l SUBJECT UNITls i suction pressure reduces the pressure ratio across the compressor, which increases the volumetric flow rate with prerotation vanes fully open. The chiller will operate at a ! higher capacity with the PRV's being controlled at the maximum i current rating. It may be inferred that the 150 ton chillers are currently sometimes operated with loads approaching 200 tons, with increased chilled water leaving temperature. Perhaps 7' roughly 25% of this load is from free heating in the 300 ton chiller. In this case, the " load meter", which is really percent of maximum motor current, reads 100%. l t A related. effect occurs at lower than design condenser cooling ; water temperatures. The compressor pressure ratio is reduced, : which reduces the compressor horsepower. The load meter may read ' 60% while the chiller is actually operating at 150 tons capacity. This case increases the capacity of the chiller if motor l horsepower was the limiting factor at design conditions. l 3 j However, the volumetric flowrate and suction pressure to the ; compressor do not change in this case so the increased capacity is less than the previous example. ; It is believed the phenomena just described accounts for most of l ' the antidotal reports of low chilled water load at STP and that ! actual chilled water loads have n'ever been measured with accurate i - and calibrated test instrumentation. , i For reasons pointed out above, during " cold ECW" conditions, all I operable chillers served by an operating ECW train must be l operating, except for brief periods during orderly train startup or shutdown. Experience to date and consideration of minimum , load makes it unlikely that both 150 ton and 300 chillers can l operate together in a single train during normal operation. Of '! the two chillers, only the 300 ton chiller has sufficient i capacity to meet post-accident heat loads following a Safety ! Injection Signal. Therefore, for operating modes with Safety Injection operable, i.e. Modes 1 through 4, the 300 ton chiller ! must be the operable chiller in a train and ECW flow through the i 150 ton chiller must be secured. For Modes 5, 6, and "defueled" - mode, there is no accident scenario that automatically starts equipment that would cause a large increase in heat load above i the operating heat load. In this case either the 150 ton or 300 ton chiller is sufficient to meet operability requirements.for a-
- train. The same restriction on having only one chiller operable per train applies for " cold ECW" conditions during the Mode 5, 6,
- and "defueled" operation.
4 _ , ,..-,r. , _ _ . , , . .
I 5"""'" CALC NO. MC-6429 SHT 14 OF k SOUTHTEXAS PROJECT REV.- PREPARERIDATE REVIEWERIDATE ELECTRICGENERATINGSTAT10N HOUSTON UGHTING & POWER o d it-i-93 % h_ g q,3 GENERAL COMPUTATION SHEET SUBJECT UNIT ls , In keeping with the philosophy of Emergency Operating Procedures to consider combinations of events far more severe than " design basis accidents", it should be noted that during " cold ECW" conditions, a significant fraction of rated heat removal capabilities from a chilled water train may be available even if both essential chillers in the train fail to operate. ID extremis the prerotation vanes on an inactive chiller can be opened in manual, provided power is available to the panel, to maximize the " free cooling effect". If this is attempted, the motor driven lube oil should also be run in manual, in case the refrigerant flow causes the compressor to spin. Full ECW flow and chilled water flow rates should also be established. Establishing this lineup would probably reduce the chances of restarting the chiller if the original reason for failure can be repaired, so only should be done timely repair is not anticipated. I l
'l STP 361(1248) . CALC NO.
w e -r;a >o sgf a s . - op 9s ; SOUTHTEXAS PROJECT ; REV. PREPARERIDATE ' REVIEWERIDATE ELECTRICGENERATING STATION HOUSTON LIGHTING & POWER o d u. , _53 g u-g- % ! GENERAL COMPUTATION SHEET ; SUBJECT UNIT is ,' {
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i V. REFERENCES _
- 1. Calculations t A. MC-6412, Rev. O, Essential Chilled Water Heat Loads.
B. MC-6406, Rev. O, Essential Chiller Performance Test. i C. NC-9004, Rev. 8, Post LOCA Radiation Zones /EQ Radiation D. NC-9002, Rev. 2, EQ Airborne & Plateout. Source Terms and Dose Post LOCA l E. MC-6251, Rev. O, ECW Transient Analysis j l F. MC-5243, Rev.10, EAB Main Area Heat Load / Air Flows and ; Battery Room Hydrogen Dilution i EAB HVAV Pressure Drop i G. MC-5144, Rev. 6, i
- 2. Vendor Manuals / Vendor Documents ;
i A. 4310-00166-AYD, Performance Test Report for 300 ton l Chiller 7 i B. 4310-00180-DYD, Manual for 300 Ton Chiller- , C. 0400-00012-BNU, Emergency Cooling Pond Analysis D. 4102-00002-ABY, Technical Evaluation Report for i Hermetic Chillers j I
- 3. Correspondence ,
A. York letter ST-YD-YB-0044, dated August 30, 1984
- s B. Diagnostic Evaluation Team Report on South Texas !
Project Electric Generating Station, Issued June 10, l 1993 ; i C. Quality Assurance' Report of Essential Chilled Water' ; System Safety System Functional Assessment, March 26, j 1993 1 l I
- - - -,t
STP 361 (1248) CALC NO. MC-6429 SHf 16 OF %s SOUTHTEXAS PROJECT REV. PREPARERIDATE REVIEWERIDATE ELECTRICGENERATINGSTATION HOUSTON UGHTING & POWER o vgf,_ ,f _ f _93 eG G n-MS GENERAL. COMPUTATION SHEET SUBJECT UNilis D. Essential Cooling Water System, Essential Chilled Water System, & Ventilation Systems -- Third Party Review & Assessment -- CYGNA ENERGY SERVICES, September 21, 1993 E. Test Report - Inservice Eddy Current Examination of Condenser and Evaporator Tubing Installed in York Chillers 21B and 22B -- K & L Engineering, March 10 & 11, 1993
- 4. Handbooks / Reference Books ,
A. Encineering Data Book, Gas Processors Supplier's Association, Ninth Edition, 1972 B. Chemical Engineer's Handbook, Perry, Et. Al., 5" Edition C. Crane Technical Paper No. 410, 1976 Edition D. Gas Conditioning and Processing, Volume 2, Dr. John Campbell, Fifth Edition E. ASHRAE HANDBOOK. 1985 FUND 7MENTALS, Inch-pound Edition F. ASHRAE HANDBOOK. 1984 SYSTEMS, Inch-pound Edition H. Applied Heat Transfer, by V. Ganapathy, 1982
- 5. Design Drawings A. Essential Chilled Water System Flow Diagrams - Train A 3V119V22519, Rev. 1.
B. Essential Chilled Water System Flow Diagrams - Train B 3V119V22520, Rev. 1. C. Essential Chilled Water System Flow Diagrams - Train C 3V119V22521, Rev. 1.
" " " * ' CALC NO. Mc-6429 SHT 17 OF Pi SOUTHTEXAS PROJECT REV. PREPARERlDATE REVIEWERlDATE ELECTRICGENERATING STATION
. HOUSTON UGHTING & POWER C dd #-/-13 % n-b e GENERAL. COMPUTATION SHEET SUBJECT UNIT Is D. Essential Chilled Water system piping isometrics 3M369PCH211 SHT. 33 REV. 5 3M369PCH211 SHT. 58 REV. 4 3M362PCH211 SHT. A22 REV. 2 3M362PCH211 SHT. A26 REV. 2 3M362PCH211 SHT. A27 REV. 6 SM369PCH211 SHT. A09 REV. 8 3F369PCH511 SHT. A05 REV. 3 3F369PCH511 SHT. A01 REV. 6 3F369PCH511 SHT. A06 REV. 5 3M369PCH211 SHT. 31 REV. 5 3M369PCH211 SHT. 62 REV. 6 3M362PCH211 SHT. 34 REV. 2 l, 3M361PCH211 SHT. All REV. 2 j
- 6. Design Basis Documents ,
A. Diesel Generator System, SQ159MB1023, Rev. 1 B. EAB HVAC System, 5V119VB1022, Rev. 1 ,
- 7. Plant Procedures A. OPOP02-EW-0001, Rev. 1 l i
e t l l l l
.t STP 36 t (1248) CALC NO. Mc-sa29 SHT 18 OF %6 I SOUTHTEXAS PROJECT REV. PREPARERlDATE REVIEWER 1DATE ELECTRICGENERATINGSTATION !
HOUSTONLIGHilNG & POWER o g #/- r-53 g h-Hs '! GENERAL COMPUTATION SHEET . SUBJECT UNITis VI. CALCULATION I A. ANALYZE CHILLER CAPACITY AT HIGHER THAN NORMAL CHILLED WATER -l OUTLET TEMPERATURE [ Chiller performance at conditions of shop test. (Ref. 2.A) .l l Test Data: (Refrigerant properteries are obtained from Ref. 4.E, , using the interpolation spreadsheet described later.) , 5 Evaporator. Pressure = -14.7 "Hg i The data says the units are "HgA, which is contrary to the (-) j sign. To test this: ! 14.7 "HgA
- 0.491154 psi /Hg = 7.22 psia j i
Tsat 0 7.22 psia = 41.05 *F l
-Ambient pressure = 14.55 psia ,
If 14.7 is "HgV, Pressure = 14.55.- 7.22 = 7.33 psia { r Tsat 0 7.33 psia = 41.71 *F, this is higher than the chilled ! water outlet temperature, which is not possible in steady state conditions. Therefore the 14.7 "HgA appears to be the correct i unit. l Evap. Temperature = 40.4 *F Ambient pressure = 14.55 psia Chilled water out temperature = 41.49 *F
-i Compressor suction temperature = 41.72 *F I Compressor discharge temperature = 183.84 *F PRV position = 90% open KW input to motor = 332.5 KW Evaporator load = 301.9 tons I
l l j
^
q i STP 361(1248) ggg g - g_g 7 q gg yg gg j SOUTHTDMSPROJECT REV PREPARERIDATE - REVIEWERfDATE j ELECTRICGENERATINGSTATION HOUSTON UGHTING & POWER o g i;_ r_S3 g gg_g_ q GENERAL COMPUTATION SHEET ; SUBJECT UNITls , i By energy balance on evaporator t Qevap = w * [h yg -hg] l l h ma = h, O Tsat in evaporator ;! I hg= h,-c *p 6T u h, 0 Tsat in cond. Tsat 0 7.22 psia = 41.05 *F ; f cond. press. = 19.5 psig + 14.55 = 34,05 psia ; t 0 34.05 psia, Tsat = 121.5 *F 6T , = 121.5 - 118.9 = 2.60 *F , f hy 9 121.5 *F = 33.070 btu /lbm .I Cp = 0.217 btu /lbm (Ref. 4.E, page 17.3) hg = 33.070-0.217*2.60 = 32.506 btu /lbm-h, 0 41. 05 *F = 96.995 btu /lbm
.i Qevap = 301.9 tons
- 12000 btu /hr. ton = 3.623 E+6 btu /hr w = 3.623 E+6 =
56180 lb/hr = 936.3 lb/ min- l [96.995-32.506] f 6P = 2.8 E-7
- K*w 2 *v {Ref. 4. C, page'3-4] !
[ID]' j Find compressor inlet conditions: Pressure drop from evap to compressor inlet. -l Assume K = 5 [ Actual fittings account for a K factor of'1.1, l however, the prerotation vane effect is not known. l Basically the results validate the assumption.] l t 6P = 2.8 E-7
- 5* [561801 2
- 5.3115 = 0.76 psi .i 13.25' '
Inlet & discharge pipe sizes & layout are from Ref. 2.B j a I l i
STP 361 (1248) CALC NO. Mr-nn9a SHI 9n OF W SOUTHTEXASPROJECT REV. PREPARERIDATE REVIEWERIDATE ELECTRlCGENERATINGSTATION HOUSTON LIGHTING & POWER o ifd. /M-93 @$ M- 4 3. GENERAL COMPUTATION SHEET SUBJECT UNIT ls P3 = 7.22 -0.76 = 6.46 psia v 3 = 5.3115 * [7.22/6.46] = 5.936 cf/lb Find compressor. discharge conditions: Pcond = 34.05 psia Vsat @ 34.05 psia = 1.2514 cf/lb Tsat 9 34.05 psia = 121.5 *F + 460 = 581.5 "R The compressor discharge temperature can be predicted for adiabatic compression. We will use a trial 6P to find compressor discharge pressure, calculate the adiabatic temperature rise and actual (considering compressor efficiency) temperature rise, find specific volume from the actual temperature & trial pressure, find an accurate 6P with the specific volume, and iterate the process. The 6P is a small fraction of the total pressure, so one iteration provides sufficient accuracy. T = Compressor Inlet Temperature, *F 3 T 2s = Adibatic Compressor Discharge Temperature, *F T2 = Actual Compressor Discharge Temperature, *F r = pressure ratio = discharge pressure + inlet pressure P = Compressor Inlet Pressure, psia 3 P2= Compressor Discharge Pressure, psia r', etc. indicates a trial condition. use 6P'=0.2 P' 2
- 34.05 + 0.2 = 34.25 r'=P' 2 /P 3
=
34.25 / 6.46 = 5.303 T2s #~T 1 = [T +460]
- X' 3
[Ref. 4.B page 6-16] where X' = r, Hbu/u-1 = 5. 303H1.n-u/1.1u-l = 0 '798 k for R-11 = 1.11 [Ref. 4.D page 98] 4
1 l STP 331 (1248) CALC NO. Mc--6 4 2 9 SHT 21 OF 36 SOUTHTEXAS PROJECT REV. PREPARERIDATE REVIEWERIDATE ELECTRICGENERATING STATION HOUSTON LIGHilNG & POWER o Vgg. u ,. f3 g 3. g.% GENERAL COMPUTATION SHEET SUBJECT UNITls T 2s '-T 3 = 501.05
- 0.1798 = 90.09 T'p -T =
[T 2s '
- T 3 ]/ compressor ef f.
3 Assume adiabatic compressor efficiency = 0.70 per Ref. 4.A,pg 5-1 T' 2
-T 3
= [T2s' - T ]/ compressor ef f. = 90.09 / .70 = 128.7 3
T' 2
= 501.05 + 128.7 = 629.7 *R ~ 170 *F V' 2
= 1.2514 * [629.7/581.5] = 1.3551 cfflb Assume K2 = 1.5 [The exit accounts for K = 1.0 and there's a baffle which would cause some additional loss.]
6P = 2.8x 10-7
- 1.5
- f561801 2
- 1.3551 = 0.18 psi 10.02' P2 = 34.05 + 0.18 = 34.23 psia r=P /2 P = 34.23 / 6.46 = 5.30 3
Tp,-T3 = [T +460] *X 3 X=ruk-1uk3-1 = 5. 300M'"U'"l-1 = 0.1797 T 2s-T 3
= 501.05
- 0.1797 = 90.04 T 2 -T 3
=
[T 2s - T 3 ]/ compressor ef f. T 2 -T 3
=
[T2s - T ]/ compressor eff. = 90.04 / .70 = 128.6 3 T2 = 501.05 + 128.6 = 629.7 *R = 170 "F V 2 = 1.2514 * [629.7/581.5] = 1.3551 cfflb 6P = 2.8x 10~7
- 3.5
- T561801 2
- 1.3551 = 0.18 psi 10.02' ,
The calculated compressor discharge temperature compares to 183.8 ]
*F from test report. The difference is most likely due to the j effect of the prerotation vanes. Although the vanes are almost j fully open (90%), they would act to reduce the compressor ;
efficiency. i 1
1 STP 361 (1248) gg g i'ib b$53 . 22 g l SOUTHTEXAS PROJECT REV. PREPARER /DATE REVIEWERIDATE ELECTRICGENERATINGSTATION 4 n4U hhW HOUSTON UGHTING & POWER o GENERAL COMPUTATION SHEET SUBJECT UNITls , Q3 = 936.3 lb/ min
- 5.936 cf/lb = 5558 cfm adiabatic horsepower ,
hp, = 0. 004 3 6
- Q,
- P 3
[k/(k-1) *X [Ref. 4.B, page 6-16]
.I hp, = 0. 004 3 6
- 5558
- 6.46 * [ 1.11/ (1.11-1) ]
- 0.1797 = 283.9 hp compressor hp = 283.9 / .70 = 405.5 hp ;
Per shop test report (Ref. 2.A), KW input to motor = 332.5 KW j Motor efficiency = 0.946 near full load [Ref. 2.B] shp = 332.5 KW
- 0.946 / 0.746 KW/hp = 421.6 hp The difference between 405.5 & 421.6 would be losses in the gear- :
train, shaft seal, and compressor bearings. I i 421.6 - 405.5 = 16.1 hp = 4 % , which is a reasonable figure. j The conclusion from this is that reasonable approximations of- -j motor horsepower can be made with the limited data available from l York. Per Ref. 2.B, the current limiter is set 9 104% of a full load current of 60 amps. The maximum horsepower allowed by the current limiter is: Motor KW = [3]*
- volts
- amps
- power factor / 1000 volts = 4160 amps = 60 power factor = 0.845 [ trial]
KW = 1.732
- 4160
- 60 * .845 / 1000 = 365.3 kw shp = KW
- 0.946 / 0.746 = 365.3
- 0.946 / 0.746 = 463.2 hp Power factor @ 463.2 hp = 0.849 j KW = 367.0 kw Rated shp = 465.4 hp Maximum shp = 1.04
- 465.4 = 484 hp
) ,
STP 361 (1248) CALC NO. Mc-6429 SHI 23' OF M I SOUTHTEXAS PROJECT REV. PREPARERIDATE REVIEWERIDATE ELECTRICGENERATINGSTATION HOUSTONLIGHilNG & POWER o W/( II-t- U @6 h-i-9 G ! GENERAL COMPUTATION SHEET -
,i UNIT is '
SUNECT I) i Estimate the capacity of 300 ton chiller with 48 *F chilled water outlet temperature. l The preceding algorithm is used in a Quattro Pro spreadsheet to l facilitate looking at different conditions. The results are ! displayed in Appendix 1. Appendix 2 shows the compressor model '" formulas used in the calculation. i. ; Assuming an evaporator temperature 0.5 *F below chilled water i! outlet temperature. !! i.i i i t Refrigerant 11 thermodynamic properties from Ref. 4.E are also ' included in the spreadsheet, using a Lagrange Interpolation ! method from Ref. 4.B to provide more accurate interpolation. The f results match with values from Ref. 4.E. At 300 tons & 48 'F chilled water outlet, with the same condenser
" pressure, the shp horsepower is 372 hp; considerably less than ,1(
the 422 hp from the test. Shaft horsepower is repeated in the ! i spreadsheet just below load, to facilitate obtaining the load at ! which the shaft horsepower limit is reached. The 3 case finds .[ the load which requires maximum allowable horsepower from the i compressor. This load is 379 tons. j i' Estimate the maximum capacity of the 300 ton chiller with 75 *F enterina chilled water, such as may occur when startina an idle chiller. By trial and error, we find the evaporator pressure that gives l - maximum shp and provides a matching energy balance on the i evaporator chilled water. For a chilled water flow through the : 300 ton chiller of 640 gpm, the balance is reached with 58 *F l chilled water outlet temperature, or 57.5 *F evaporator temperature. The result is a-load of.452 tons. A Quattro Pro j spreadsheet has also been developed to solve the heat transfer ; problem in the 300 ton chiller condenser. . This spreadsheet is j covered in a following section. .This spreadsheet was used to , predict the required condensing temperature, with 240 gpm ECW ; flow at 69 *F inlet temperature, with the condenser heat load l' shown for the Maximum Load cases. The condensing temperature for the 452 ton load would be higher than the 121.5 used in case 4. The higher temperature and pressure in the condenser would reduce the load at which the 484 shp limit would be reached. By trial and error, it is found that the maximum load is about 431 tons, with a condensing temperature between 125 *F and 126 *F. t __ _ . . _ . - ._ _ - - __ ~
sw an"* CALC NO. Mr-^49a SHT 9a OF VC SOUTHTEXAS PROJECT REV. PREPARERIDATE REVIEWER 1DATE ELECTRICGENERATINGSTATION i HOUSTON UGHilNG & POWER o Vf[ n.c-f3 % n_ po GENERAL COMPUTATION SHEET SUBJECT UNiils York did not provide the compressor performance curve for the chiller compressors. However, curves for centrifugal compressors shown in various references are very similar. We believe the compressor curve for the 300 ton chiller would be similar to the
" Typical" from Ref. 4. D, included as Attachment A.
The adiabatic head can be found from data avai]able from previous work as follows: hp = head (ft)
- mass flow (Ib/ min) comp. eff.
- 33000 ft-lb/hp. min or head = (shp - gear loss)
- comp. eff.
- 33000 / mass flow, ppm The head and volumetric flow corresponding to the shop test is taken as 100% head and 100% flow. Case 2 indicates a significant '
amount of throttling of the prerotation vanes would be required to achieve the operating point, while case 3 is very close to the curve, so little PRV throttling would be required. This implies the actual motor horsepower would be higher than calculated in case 2, and that case 3 represents an achievable head and flow. Case 4, which is a trial maximum transient load case, and case 5, a closer estimate of maximum transient load are considerably below the curve, indicating PRV throttling would be required. There would be considerably more throttling than the K factor assumed for the suction line. This would increase the horsepower, or decrease the load at the limiting horsepower. Hence the load for the " maximum" is conservatively high. In addition, in cases 3 through 5, the compressor is operating ; with a greater margin from the possible surge flow, than in the original shop test. i l
S " '0240 CALC NO. Mc-6429 SHT 2s OF M SOUTHTEXASPROJECT REV. PREPARERIDATE REVIEWERIDATE ELECTRICGENERATING STATION i HOUSTONUGHTING & POWER C V/M u-/ f3 Ot:> h- M '3 GENERAL. COMPUTATION SHEET SUBJECT UNIT ls B. ANALYZE CONDITIONS RELATED TO STARTUP OF AN IDLE CHILLER The following sequence of events occurs during the diesel loading sequence of the standby diesel generators after a LOCA with Loss of Offsite Power. Times are noted in seconds after diesel generator breaker closure. Only events important to the 300 ton chiller are shown. (Diesel loading sequence from Ref. 6.A) Time Event 0 D.G. breaker closes 25 ECW Pump starts 35 Essential Chilled Water Pump starts
- EAB fans start Control Room fans start Chiller motor driven lube oil pump starts ECW Pump Discharge Valve opens 70 Chiller Compressor starts 75-90 Water initially within ECW Sump room enters condenser 100-115 Water initially within 30" header enters condenser 145 Prerotation Vanes are fully open (if demand & controls allow), chiller is fully loaded.
160-250 Water initially in ECP enters Mechanical Auxiliary Building (MAB). 225-300 Water initially in ECP enters condenser 275-350 Water initially in ECP exits condenser Thus it takes approximately 6 minutes to reach a roughly steady state condition which is only conditional on ECP temperature. The chiller will reach its maximum load before water from the ECP enters the condenser. The CCW/ Essential Chiller room in which the chiller and the first i portion of ECW piping is located will typically be between 65 & 75 *F when the train is idle. This temperature is not critical because water from the 30" underground supply line begins to
i STP361 (12* CALC NO. Mc-6429 SRT 26 OF M " I SOURIDGSPROJECT REV. PREPARERIDATE REVIEWERlDATE ELECTRICGENERATING STATION l HousioNUGHilNG & POWER o / tfji y+c ht gm ; GENERAL COMPUTATION SHEET l SUBJECT UNIT Is i
-l e
I enter the chiller condenser before the machine is fully loaded. Per Reference 4.F, Table 3, page 13.9, the average earth j temperature in Houston, O to 10 feet below the surface is 73 *F ! in the autumn and 62 *F in winter. The majority of the ( underground piping is about 13 feet below the surface [28 ft. ! grade elevation - 15 ft. pipe centerline = 13 ft.]. l The few recent occurrences of " cold ECW" conditions have been i relatively early in the winter. Taking the average of 62 & 73, l and adding 1.5 *F to account for slightly higher average , temperatures in this area versus Houston, gives a design basis underground temperature of 69 *F. If the ECP has been operating at lower temperatures, as would be the case during " cold ECW" operation, the ground immediately around an operating pipe would , be cooled below 69 *F. This would also affect the temperature in i an idle train, both by steady state heat transfer and the i transient effects from the previous operation of the train. _All l; things considered, 69 *F appears to be a conservatively high j. J temperature for the water in the underground pipe. ; The chiller will start successfully provided no safety trip setpoint is reached which trips the compressor. The device most likely to trip the compressor when starting with throttled ECW flow is the high condenser pressure trip. This trip is set at a , nominal 30 psig, with a tolerance of +0 & -4 psi. A maximum , condensing temperature of 130 *F, which corresponds to a saturation pressure of 24 psig, has been selected as the maximum condenser temperature allowable at maximum transient load and maximum underground temperature. A more limiting condenser temperature of 121.5 *F, based on the condenser temperature during the shop test, has been selected for i steady state-operation. The high condenser trip setpoint is based on overpressure protection of the condenser and is not necessarily selected to prevent surge in the compressor. As , shown in the previous section, the revised " throttling range" ! settings for the chiller will result in a greater margin against l' surge than existed during the shop test. While the steady state 1
STP 361(1248) CALC NO. Mc-6429 SHT 27 OF 86 SOUTHTEXASPROJECT REV. PREPARER 1DATE REVIEWERIDATE , ELECTRICGENERATINGSTATION i HOUSTONLIGHTING & POWER o d/k //-/-f3 b h 4-% GENERAL COMPUTATION SHEET UNITls ! SUBJECT criteria may be unnecessarily conservative, it is easily met and ; is not a limiting factor. : i When starting an idle train, there is no immediate concern over minimum operating ECW temperature, because the chilled water. system will always start out warmer than the chiller setpoint,oso l the chiller will be heavily loaded until the chilled water temperatures are pulled down into the normal range. C. CONDENSER HEAT TRANSFER MODEL 4 + A Quattro Pro spreadsheet was developed to calculate the total ! heat transfer in the 300 ton chiller condenser, with a given ECW ! flow rate, condenser saturation temperature, and inlet ECW j temperature. Either the " clean" heat transfer coefficient, which j is conservative for consideration of minimum load, or the J
" service" (or fouled) coefficient, which is conservative for .
consideration of maximum load, can be used. j The following data was taken from Ref. 1.B, for the 300. ton : chiller-I condenser surface area = 5546.4 ft2 , f 800 condenser tubes arranged in 4 passes j i tube ID = 0.612 in f l tube flow area = 0.294 in2 .l t Uclean = [.002029 + 3.14/h,]d ! Uservice = [.008610 + 3.14/hj ]d f i where hi = Tube side heat transfer coefficient ; tube length = 13.78 ft. In the range of water flow rates & temperatures considered, the -} tube side Reynolds Number [Re] usually fell within the ! transitional flow regime, that is, neither fully turbulent or laminar. The inside film coefficient increases significantly'as the water temperature increases through-the heat exchanger. Thus ; each pass of the condenser is treated separately, in sequence. ; 4 The known bulk properties of water entering each pass is used to l
i ST P 361(1248) CALC NO. Mc-6429 SHT 28 0F RT SOUTHIEXASPROJECT REV' PREPARERIDATE REVIEWERIDATE ELECTRICGENERATING STATION ( HOUSTON LIGHTING & POWER o gfL u- /-{3 % w_T- %
- GENERAL COMPUTATION SHEET SUBJECT UNIT ls calculate the heat transfer coefficient. The actual heat transfer coefficient would be higher, because the bulk average temperature in the tube is higher than the inlet temperature.
This is conservative in maximum load cases. In minimum load cases it is not conservative, but in these cases the temperature rise through each pass is small so the nonconservative error is small. Starting from the top of the spreadsheet: Qtotal = total heat transfer in BTU /Hr = the sum of heat transfer in each pass. Tout = ECW outlet temperature, *F= inlet temperature to fourth pass plus delta T across pass.
"YES" or "NO" is inserted in block E3, based on the case. "YES" is used for the low load / low temperature end of the range, while "NO" is used for the maximum load / maximum temperature end of the range.
Tin = ECW inlet temperature to condenser in column B. Column C ; value equals column B plus the delta T across the pass, and so on. Tsat = condenser shell side temperature. The column B value is , input and other columns are repeated. gpm = ECW flow rate in gpm. Input in B and repeated. Ap = area of each pass. = 5546.4/4 = 1386.6 ft2 spvol = specific volume of water at pass inlet temperature. This is 0.01602 ft 3 /lb if inlet temperature is below 60 *F, or a value 4 o f i) . 015 8 58 + 2 . 7x 10 T is calculated based on inlet temperature. This was obtained by linear regression using data between 60 & 120 *F. i visc = viscosity, lbm/ft.hr = 4 p = a e a = 6.89112 B= 1. 5190541 x 10-2 l l
i sa n24sl CALC NO. Mc-u?a SHT ?o OF 56 lA SOUTHTEXASPROJECT REV. PREPARERIDATE REVIEWERIDATE ; 1 ELECTRICGENERATINGSTATION HOUSTON LIGHTING & POWER o 1/gl_. n-i 93 % n_g_ u j GENERAL COMPUTATION SHEET l UNITis ; SUBJECT i l The constants werc determined by linear regression using ; data from 32 *F to 120 *F G = mass velocity, lb/hr.ft2 = mass flow, lb/hr + flow area, ft2 ; mass flow rate = gpm
- 1 ft 3
- 1 -lbm
- 60 min !
7.4805 gal spvol ft 3 hr ; 2 2 j area = 200 tubes *0.294 in / tube *1/144 ft /in2= 0.4083 ft 2 D = tube inside diameter = 0.612/12 = 0.0510 ft. l Re = Reynolds No. = G*D /g dol = D + L = 0.0510/13.78 = 0.003701 5 The equation j j = "j" factor from Ref. 4.H, Appendix B, page 433. i used depends on the flow regime, as shown by the Reynolds Number. [ i For Re < 2100 [ laminar flow] i l 0 "7 j = 1.86/[Re *(L/D)D*33} l I For Re > 10' [ fully turbulent flow] ! 0 ; j =
.027/Re*2 f
For 21005RE510000 [ transitional] ! l j = 0.116 I Re 0"I-12 51 I 1+ (D/L) 0.m73 l Re . (j is dimensionless) ! i Cp = specific heat capacity of water, BTU /lbm.*F l
= 1.0116-0.00017*T by linear regression !
k = thermal conductivity, BTU /hr.ft.*F y 5
= 0.3140+0.0004995*T by linear regression f I
Pr = Prandtl Number = 4*Cp/k i
, i i
. _ ._. . ~. . . __ _ -_
STP 361(1248) CALC NO. Mr- e o SHT ,n .OF 86- l i SOUTH TEXAS PROJECT PREPARERlDATE REVIEWERlDATE REV. l ELECTRICGENERAllNGSTATION HOUSTON UGHilNG & POWER o V.fL is.-SJ h n g3 l GENERAL COMPUTATION SHEET l SUBJECT UNIT ls ; i MUw = p, = viscosity of water at wall temperature.
= a
- e'"I Twall ~ Tsat when inside film coefficient is a significant factor.
MUratio = p, / p h = j
- Cp
- G
- Pr-0.N , (pjp)0m :
Uc = clean overall heat transfer coefficient
=
1/ [0.002029 + 3.14/h] ! U = service overall heat transfer coefficient ;
=
1/ [0.008610 + 3.14/h] : Cmin = Cp* mass flow rate, for ECW, BTU /hr.*F ! i
= Cp*gpm*60*[1/7.4805]*[1/spvol] :
l NTUp = NTU for one pass = U
- Ap / Cmin l i
If D3 is "yes", Uc is used, otherwise U is used. ! EFF. = cp = thermal effectiveness of pass
= 1 - e-wiup for condensing heat exchanger !
Op = heat transfer in the pass, BTU /hr e = Cmin
- cp * [Tsat-Tin] -l
?
I deltaT = 6T = Qp/Cmin = ECW temperature change through. pass. l i The inlet temperature for the next pass is then calculated, and ! so on. ! The' condenser heat load is found for each case as follows: } Qtotal = load, tons
- 12000 BTU /hr. ton + SHP
- 2545 BTU /hr.hp
- For the 300 ton load @ 48 chilled water outlet case, 6 Qtotal, BTU /hr = 300
- 12000 + 372.4
- 2545 = 4.55 x 10
sTe m one) CALC NO. e -rsooo SHT u 09 M SOUTHTEXAS PROJECT REV. PREPARERIDATE REVIEWERlDATE ELECTRICGENERATINGSTAIl0N HOUSTON UGHTING & POWER o Vd ri-i-93 b iM-% GENERAL COMPUTATION SHEET SUBJECT UNIT Is With 240 gpm flow, an inlet temperature of 81.3 *F is required to match this heat load. For the maximum load at 48 *F chilled water outlet, ' Qtotal, BTU /hr = 379.1
- 12000 + 483.9
- 2545 = 5.78 x 10 6 For the maximum trial load, 6
Qtotal, BTU /hr = 452.4
- 12000 + 484
- 2545 = 6.66 x 10 Tsat is greater than 121.5, so actual max. load is lower.
For maximum transient load, 6 Qtotal, BTU /hr = 431.3
- 12000 + 484.1
- 2545 = 6.41 x 10 Tsat = 125.8 ~ 125 assumed in conpressor load For the shop test results, 6
Qtotal, BTU /hr = 301.9
- 12000 + 421.5
- 2545 = 4.70 x 10 The " clean" coefficient is used in this case, because the chiller was new. The condenser flow of 1099 gpm and inlet temperature of 111.67 are from the corrected test results.
Tbc condenser pressure required to give this heat load matches the test results reasonably well. The above model was modified for the 150 ton chiller condenser, as follows: The following data was obtained from Ref. 1.B for the 150 ton chiller. Number of tubes = 347 arranged in 4 passes D = 0.53 in / 12 = 0.0442 ft. ; i 1 dol = 0.0442 / 13.78 = 0.003205 1/Uc = 1/[860.08*0.82] +0.00025/0.82 +0.0005606 +0.00025*4.61
+ 4.61 / h l
l I 1
-3
- ST P 361 (12* . CALC NO. Mc-6829 SHT 32 OF 44 SOUTHTEXAS PROJECT REVIEWERfDATE REV. PREPARERlDATE ,
ELECTRICGENERATINGSTATION
.O HOUSTON UGHTING & POWER 0 (L i9-S.3 -@p . n-\-As GENERAL COMPUTATION SHEET ,
, SUBJECT UNIT is j l Uc = [0.003436 + 4.61/h]~1 i Uservice = [0.01150 + 4.61/h]'1 flow area = [347 / 4]*[ 0.221 in / 144 in /ft ] = 0.1331' f t2 2 2 2 ! Ap = 3061 / 4 = 765.3 ft2 l r Several cases from the Ref. 2.D were run for comparison. -f Case 1 from Ref. 2.D: , Qtotal, BTU /hr = 150
- 12000 + 197
- 3413 = 2.47 x 10 6 .;
i ECW inlet temperature = 110 *F Case 6A from Ref. 2.D: r 6 Qtotal, BTU /hr = 500
- 600 * [61.02 - 53.33] = 2.31 x 10 fi ECW inlet temperature = 53.33 *F :
Results show Tsat = 68.3 *F . From R-11 Properties spreadsheet, Psat'= 12.9771 psia I
= 12.9771 psia + 0.491154 psi /"Hg = 26.42 "HgA j!
29.92 - 26.42 = 3.50 "HgV, which compares favorably to 3.22 ~
"HgV from Ref. 2.D, case 6A. j D ON-SET OF " COLD ECW" CONDITIONS .
" Cold ECW" conditions can be defined as the point at which ECW !
supply temperature is equal to, or less than, chill water return ; temperature, at chiller rated load or the' maximum expected j chiller load coincident with the conditions.- This temperature can be affected by the chilled water flow through the 300 ton chiller and the chill water temperature control settings. j
-- l With 48 *F chilled water out of the 300 ton chiller, continued ;
! flow through an inoperable 150 ton chiller, and 300 tons of load, l the return water temperature varied between different trains from- j 59.3 *F to 60.3 *F. [Per page 93 of Ref. 1.A] The maximum 1 ! 2 1
-- , . _ _ , .- .m
1
-l STP 361 (12 8Q CALC NO. Mc-s o o SHT 33 OF M !
REV. PREPARERfDATE REVIEWERIDATE RC ERA i STATION HOUSTONLIGHTING & POWER o Vfk //-/- s @S n-\- e j
- GENERAL COMPUTATION SHEET SUBJECT UNIT Is i
predicted load coincident with cold ECW conditions is less than l 300 tons [243 tons or 286 tons, depending on initial mode of l operation, from Ref. 1.A), so 60 *F appears to be a reasonable ! limit for initiation of " cold ECW", for a train with only the 300 ! chiller operable. The much higher loads expected for a brief j period after starting a 300 ton chiller in an idle train are ; l covered under the 25 *F delta temperature criteria, and are not ! considered under this criteria. i i 2 With both the 150 ton and 300 ton chillers operable in a train, the limit would be reached when the actual chilled water return ! temperature exceeded actual ECW supply temperature, or when this ! condition would be reached with a hypothetical accident, which ;
- ever is more limiting. ;
4 Take the following case: ; a ! 150 ton chiller is operating with 150 ton load. 300 ton chiller is operable but idle. , Chilled water flows are per the flow diagrams [Ref. 5.A-C] I flow rate, com l Train A Train B Train C ; I 150 ton 303 293 318 : 300 ton 607 587 636 l total 910 880 954 . 6T 3g = 150*12000/[500*gpm,150T] 6T tetat = 150*12000/[500*gpm, Total] 6T 150 11.9 12.3 11.3 }
- 6T totat 4.0 4.1 3.8 j
'i .
Return Temperature = 48 *F + 6T uo ; i
= 59.9 60.3 59.3 l l
l This will be the more limiting case. If both chillers were : started by an SI signal the total load would be less than 450 ! tons so the return water temperatures would be less than shown ! above. With both chillers operable in a train, and only the 150
- I l
STP 361 (1248) CALC NO. w-ca>o SHT na OF M SOUTH TEXAS PROJECT REV. PREPARERIDATE REVIEWERlDATE ELECTRICGENERATING STAT 10N HOUSTON LIGHTING & POWER o pyL p_ f43 66 n-W . ; GENERAL. COMPUTATION SHEET l SUBJECT UNIT is ton chillers operating, the On-set of " Cold ECW" is also about 60
*F. In this case it is possible for the actual load to be higher than 150 tons, which means the return chilled water temperature would equal ECW supply temperature at a higher temperature.
i E. ECP MINIMUM TEMPERATURE EXPECTATIONS : The minimum ECP temperature experienced to date is 38 *F, on or [ about Dec. 26, 1989. This occurred during a record or near record cold front. Both Units had been in refueling or forced outage shutdown for and extended period, although one of the Units was attempting to start up as the cold front hit. There was very little heat load to the ECP. Reference 2.C contains an analysis of minimum ECP temperatures calculated using temperature records for a 15 year period from 1966 to 1980, for cases ranging from zero heat load to 2 Units operating with " minimum" heat loads & two ECW trains operating per Unit. The results are summarized below: Minimum Temperature - 15 year record (Ref. 2.C, page 5-7) CASE MINIMUM TEMPERATURE Zero heat load 41.9 *F 1 Unit w/ 1 train 46.1 *F 1 Unit w/ 2 trains 46.7 *F 2 Units w/ 1 train / unit 51.0 *F 2 Units w/ 2 trains / unit 51.7 *F R'eference 2.C also analyzed the minimum ECP temperatures using temperature records for a record or near record cold front which occurred on or about Dec. 26, 1983. By the authors personal experience the 1983 & 1989 cold fronts were comparable. In both cases the temperature dropped briefly to the vicinity of 8 *F, with relatively high winds and clear sky. Sustained temperatures below 20 *F with a daily high less than 32 *F was experienced on at least one day. The calculated temperatures for various cases for the 1983 cold front were as follows:
STP361 (1248) CALC NO. r-M n SHT 35 OF % ~ : S0WHID@S PROJECT REV. PREPARERIDATE - REVIEWERIDATE ELECTRICGENERATlNGSTATION HOUSTON LIGHTING & POWER 0 WL fy- g (jbyz, h-\-43 , GENERAL COMPUTATION SHEET l SUBJECT UNITis ; i Minimum Temperature - 12/26/83 (Ref. 2.C Page 5-7) Ji CASE MINIMUM TEMPERATURE _ i Zero heat load 32 *F ( 1 Unit w/ 1 train 34.5 *F $ I 1 Unit w/ 2 trains 35.2 *F 2 Units w/ 1 train / unit 39.7 *F : 2 Units w/ 2 trains / unit 40.6 *F } Review of the input to the referenced analysis shows the ECW heat input to the ECP used in the analysis was 56.7 x 10 6 BTU /hr per , unit (Ref. 2.C page 4-10). This was intended to be a minimum value. In reality the load used (except the zero load case) is ! much higher than heat loads currently experienced and even . considerably higher than expected loads with a full spent fuel pit heat load. Many of the larger potential heat loads on the l CCW system are from equipment which is seldom if ever used, for example, the radwaste evaporator, boric acid evaporator, Boron
- Thermal Regeneration System, and maximum letdown. j Much of the above equipment could be operated, even if for no -I other purpose than to heat CCW. Additional heat input could be obtained by running 2 CCW pumps and using CCW to cool _the RCFC's. ;
Depending on the actual spent fuel heat load, the total heat l rejection could approach the value used in the cold weather : analysis. Therefore, with at least one unit operating, and with maximum effort to add load to the ECP, it appears probable that - the ECW supply temperature will not drop below 40 *F. , F. POST LOCA RADIATION LEVELS IN CCW/ CHILLER ROOMS Concern has been raised regarding the calculated dose rate in the l CCW/ Chiller room for manual adjustment of ECW flow after a LOCA. Reference 1.C shows a dose rate at time zero of 7.18 r/hr. The methods used to obtain this figure were highly conservative se even the instantaneous dose rate at t=0 wou7 d be considerably lower than 7.18 r/hr. However, assuming thi dose rate is 7.18 r/hr at t=0, the dose rate in the area would be within reasonable limits before adjustment was required post-LOCA. For example, 8 hrs after the LOCA, the outside decay factor (from Ref. 1.D, the. v
l STP 361(12 88) CALC NO. Mc-e42o SHT- 3 s OF $6 l SOUTHTEXAS PROJECT REV. PREPARERIDATE REVIEWERIDATE
~
ELECTRICGENERATING STATION HOUSTON UGHTING & POWER o d~ us 93 M
~
n-\-t3 i GENERAL COMPUTATION SHEET SUBJECT UNIT ls input source for Ref. 1.C) is 0.035, giving a dose rate at 8 hours of 7.18
- 0.035 = 0.250 r/hr.
Evening assuming an hour stay time to adjust valves in 2 or 3 trains, which seems more than adequate time, the dose is only 250 mr, or about 250 mrem. 6 The initial ECP volume = 14.98 x 10 ft3 (Ref. 2.C) 4 trains of ECW @ 20,000 gpm each = 10700 cfm 14,980,000/10700/60 min /hr = 23.3 hrs. It takes roughly 24 hours to make the complete circuit of the ECP, so the effects of the LOCA heat loads will not be seen during the first 8 hours. With the flow set at 240 gpm, the FCP outlet temperature could rise to 81 *F before the capability of the 300 ton chiller to , remove 300 tons of heat would be impaired (Appendix 3.a). Thus a LOCA is unlikely to require resetting the chiller flow, other than as the result of the change of seasons. G. SINGLE TRAIN HVAC OPERATION Ref. 1.A currently prohibits single train operation during " warm weather" because the calculated transient heat loads were greater than 300 tons, based on single train initial temperatures. On the same basis, the trans.ient heat loads coincident with " cold ECW" operation are less than 300 tons. Thuc single train EAB, Control Room, and chilled water is acceptable based on post accident chiller loads. There are other considerations, which may be acceptable by inspection but which may not have been documented. Ref. 1.E calculates Hydrogen concentrations from the battery rooms in the EAB, with design air flows, ranging from 0.0004% to i 0.16%. This compares to a maximum allowable of 2%. Operating a single train of supply, return, and. e).naust fans cannot reduce the flow more than 50%. The actual flow in single train is more likely 55 to 60% of actual two train flows. Thus the maximum { bettery room hydrogen concentration in single would be less than ) 0.32%, which remains less than one sixth the limit. Therefore, limits on hydrogen concentration will not be exceeded during i single train operation. i 1 i
i STP 361(1248) CALC NO. e-u ? o SHT w OF M i SOUTHTEXAS PROJECT ELECTRICGENERATING STATION REV. PREPARERlDATE REVIEWERlDATE l HOUSTON LIGHilNG & POWER O d n+E3 86 n-\- % l j GENERAL COMPUTATION SHEET SUBJECT UNIT ls The EAB supply fan, EAB return fan, EAB exhaust fan, and Control ; Room return fan, are all vaneaxial fans which have decreasing : i horsepower requirements as flow increases. The Control Room supply, fan is a centrifugal fan with an increasing horsepower ! curve as flow increases, but the motor is sized for the maximum i horsepower. Therefore, operating a single train of HVAC in the-EAB and Control Room does not run any risk of overloading fan . motors. l The supply ducts to battery rooms in the EAB contain reheat coils l to maintain battery room temperatures above 69 *F. The each ; reheat coil is interlocked with a flow switch, which de-energizes j the reheat coil if the flow drops below the setpoint. The single i train battery supply air flow must be high enough to activate the l flow switch for the reheater to be functional. The flow switch , for the reheater measures velocity pressure plus the differential : pressure across the supply air register or supply air grille. The calculation of EAB HVAC pressure drop, MC-5144, Rev. 6, ;
" assumed" a 0.1 " water column pressure drop across supply air '
registers and grilles, in the absence of vendor data. If the 0.1 inch assumption is correct, reducing the flow to the design , flow would reduce the pressure in the duct-to 0.025". The [ > velocity head term is much smaller than this figure. This is below the setpoint of the flow switch interlocked with the reheaters, but may be above the reset value. Thus initiating i single train flow from an idle HVAC system may not cause a high lj: enough flow to allow reheater operation, but reducing flow to single train from dual train may keep the flow above the reset j value and thus allow continued use of the reheaters. Many of the [ supply air registers contain integral dampers for flow balance i purposes, so the delta pressure depends on the damper position. ! Based on static pressures recorded in the final air balance, it I appears the operability of at least one of the safety related ! battery room reheaters is questionable in single train operation. . Conversely, with the reduced flow in single train the heater may
?
not be necessary. In addition, the battery room exhaust ducts contain low flow I switches which activate low flow alarms. These " low battery room infiltration" alarms are set about 10 to 15% below the normal two , train flow rate, so nearly all of these low flow alarms would be activated while operating with a single HVAC train in the EAB. The setpoints are higher than necessary to ensure adequate hydrogen removal from the battery rooms. A reduced setpoint for these alarms should be calculated if long term single train
y _ m _ - . . _ . STP361( 2* CALC NO. Mc-6eo SHT - u OF M - SOUTHTEXASPROJECT REV- PREPARERIDATE REVIEWERIDATE-ELECTRlCGENERATINGSTATION
-- s HOUSTON LIGHTING & POWER o d //+ f3 @h t-)-As l GENERAL COMPUTATION SHEET :1 SUBJECT UNIT ls l i
'l operation is desired.
Limited air balance testing was performed in Unit 2 in the !
" Single Train" mode during preoperational testing. No data was_ 1 recorded on battery room supply or exhaust. flows or on exhaust -
-l fan flow and/or pressures.
In summary, nothing related to cold weather operation of the ; chillers rules out single train EAB & Control Room HVAC. In j i several respects operation in single Train increases overall margin. In those respects where Single Train does not increase margin, initial transient load, for example, the single train value is far from being the limiting factor. However, there are , some issues unrelated to cold ECW operation which require ) 1 additional review. H. RESTART OF OPERATING CHILLER 'j The sequence of restarting a chiller if the chiller was running before Off-site power was lost is considerably different than the-sequence provided in VI.B on starting an idle _ chiller. -In this case the chilled water temperature starts at operating _ temperature and the ECW starts at ECP temperature. The start of the chiller compressor is delayed by the-necessity to close the prerotation vanes before restarting the compressor. _ In addition,- tripping the compressor initiates a post-lube sequence which must cycle through before the compressor starting sequence can be restarted. (Ref. 6.A for diesel loading sequence) Time Event 0 D.G. breaker closes 25 ECW Pump starts (discharge valve remains open) 35 Essential Chilled Water Pump starts EAB fans start Control Room fans start Chiller motor driven lube oil pump starts post lube period 170 Post lube complete 240 Lube oil pump starts pre-lube period
I STP 361(1248) CALC NO. Mc-6829 SHT 39 OF $6 SOUTHTEXASPROJECT REV. PREPARERIDATE ' REVIEWERIDATE - ELECTR CGENERATING STATION ef[ M HOUSTON UGHilNG & POWER o n- r-93 !)-1-% GENERAL COMPUTATION SHEET SUBJECT UNIT Is 270 Pre-lube complete, compressor motor starts l 340 Prerotation Vanes are fully open (if demand & controls ! allow), chiller is fully loaded. The chilled water system and the air handling units run for about i i 4 minutes before the compressor is started. For part of that-time the prerotation vanes are partially open while closing. For i most of that time the Hot Cas Valve is open. ; Assuming no heat removal through the non-operating chiller, I treating the water and metal in the system as well mixed, and- l assuming the air entering the cooling coils is constant at 82 *F, i the temperature of the chilled water train can be found as ! follows. t Q for each air handling unit = Cmin
- E *(Tair.in-Twtr.in)
Exception for small coils with minor loads, the highest coil inlet temperature is the EAB, train C, with SI from single train .. with failure of Train A S.I. (page 410 of Ref. 1.A). [ i Tair.in = 81.9 say 82 *F j Other rooms with a significant load have maximum temperatures of ; 78 *F (Control Room), & 75 *F (ESF Pump Room). The transient loads on the EAB and CR coils from page 408 of Ref. ! 1.A are 127.3 tons and 53.3 tons, respectively. Transient loads from other AHU's are obtained from the ; spreadsheet described in Appendix K3 of Ref. 1.A, with modifications as follows. The scenario being analyzed is an S.I. l with LOOP, so only the AHU's automatically started by S.I. are i assumed to start. The other AHU's could start on high temperature but the rooms start out cool and will take some time
,i to reach the setpoint. In addition, because this train was the i;' !
running train, in " single train" operation, the CCW supplemental ' cooler would be in operation and, with the low ECW temperature, would keep the CCW/ Chiller room slightly above ECW temperature. [ 75 *F room temperature is assumed for this spreadsheet. The j total, from the spreadsheet in Appendix 7.a, is 85.5 tons. . The tons load is 127.3 + 53.3 + 85.5 = 266 tons j I
STP 361(1245 CALC NO. - e-Aa9o- SHf an OF M SOUTHTEXASPROJECT REV. PREPARERlDATE REVIEWERlDATE ELECTRICGENERATINGSTATION g HOUSTON LIGHilNG & POWER o wJ( n- r-93 b h-\-% GENERAL COMPUTATION SHEET SUBJECT UNilis The initial chill water supply header temperature is 48 *F, from. Ref. 1.A. A single equivalent coil with air at 82
- F and cooling water at 48
- F would have an air handling unit constant of Cx = Q / (Tair.in-Twtr.in)
Cx = 266 tons *12000 btu /hr. ton = 93882 btu /hr.*F =1565-btu / min.*F (82 - 48) The mass of water and steel in the chilled water train is calculated for train A in Appendix 7.b. Train A has the smallest volume. Train A would also have a smaller transient load than. train C, but the actual transient load for Train A has not been calculated so train C loads will be used. Cp of steel = 0.11 btu /lbm.*F Cp of water = 1.0 pipe mass = 22894 lbs water mass = 14004 lbs-The 300 ton chiller has a refrigerant charge of about 2000 lbs and the 150 ton chiller has charge of about 1600 lbs. R-11 has a liquid Cp = 0.217 btu /lbm *F. The sum of mass times specific heat capacity
= 22894*0.11 + 14004*1.00 + 3600*.22 = 17300 btu /*F Q = M*Cp* sit _ and Q = Cx * (Tair - T) dt or 4
T = Tair - (Tair - To)
- e #**
F= Cx = 1565 = 0.09046 1/ min. M*Cp 17300 Tair = 82 "F To = 4 8 'F
,w- ------p -, , - . ,
i 1 5"'* m - CALC NO. Mc-sa29 SHI u - OF E5 REV. ' PREPARERf DATE REVIEWERlDATE . l RC NE T STATION HOUSTONLIGHTING& POWER d ~ W//_ n-/- 93 M h-i-U -! l g GENERAL COMPUTATION SHEET : SUBJECT UNiils
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l t = time in minutes = 4 "F .; T = 82 - ( 82-4 8 ) *e-0.09%6*4 = 58.3 ! This is the supply temperature. The heat load after 4 minutes is 6 Q = Cx*(Tair-T) = 93882 * (82 - 58.3) = 2.23 x 10 btu /hr '; 6T = Q/500*gpm = 2.23 x 106 / 500*900 = 4.94 *F !
^?
Coil outlet temperature = 58.3 + 4.9 = 63.2 *F The 25 *F temperature difference limit would be reached if Tecw < 63.2 - 25 = 38.2 *F .; 1 The limit set by York are met at temperatures about 38 *F. j ii I. ECW FLOW BALANCE $ I The design flows through the 150 ton and 300 ton chiller ; condensers are 600 and 1100 gpm,-respectively. Reducing these ! flows to 0 and 240 gpm will increase the flow to the remaining. ' components. No rebalancing will be required to maintain flow t rates above minimums. The actual increase will be on the order of 5% (estimate based on experience). The ECW operating procedure currently includes , maximum flow limits as well as minimum flows. The maximum limits -l are based on consistency with analysis of the transient that j occurs when the ECW pump is stopped. MC-6251 (Ref. 1.E) documents the initial flow assumptions used in the ECW transient. ; analysis. This calculation is not the latest or current transient analysis, but all later version refer to MC-6251 for l initial flow rates. It also provides a basis for allowing flow ! rates up to 10% higher as an upper limit. In general the. upper j limit on ECW flow rate in OPOP02-EW-0001, Rev. 1, (Ref. 7.A) could be increased accordingly. Without the increase, the ; reduced flows to the chillers could require minor adjustment of ; the ECW flow balance. With the revised limits it is unlikely that adjustment of any other ECW valves will be required when entering or exiting from " cold ECW" operation. l __ .-. __ ~_
STP3610248) CALC NO. Mc-6n x SHT A9 OF % SOUTHTEXASPROJECT PREPARERlDATE REVIEWERIDATE REV. ELECTRICGENERATINGSTATION 3 . HOUSTON LIGHilNG & POWER o fr{ 4_f.9y $ w_t- % GENERAL COMPUTATION SHEET SUBJECT UNIT is Item Flow Flow Max Flow'(1) cfs com gp_m
'CCW HX 35.237 15814 17400 CCW SUPPL. CLR 0.1762 79 8, 300 TON CHILLER 2.575 1156 1272 150 TON CHILLER 1.405 630 693 DG AIR COOLER 1.452 652 717 DG OIL COOLER 0.668 300 330 DG JW COOLER 1.410 633 696 Total DG Flow 1744 (1) Flow from Ref. 1.E plus 10%
J. MINIMUM LOAD CONSIDERATIONS The chiller condenser must operate at a higher _ pressure than the evaporator. A minimum pressure difference is required to obtain the necessary flow rate of R-11 back to the evaporator. A minimum pressure difference is also required to allow the necessary flow through the Hot Gas Valve. The vendor provided the minimum condenser pressure for 42 *F leaving chilled water at several load points (Reference 3.A). This will be corrected to the required chilled water temperature as follows: Assume evaporator pressure is saturated at leaving chilled water temperature. It actually is saturated at a slightly lower temperature, but the difference is small and effectively cancels out in the calculation. , Pevap @ 42 *F = 7.38 psia i load, tons cond. press. cond. press. Pcond-Pevap "HgV psia psid-300 5.2 12.14 4.76 150 9.2 10.17 2.79 75 11.1 9.24 1.86 The best fit curve of 6P versus load was obtained using the linear regression analysis feature of the TI 55III hand
i l STP 361 (1248) CALC NO. e-^soo SW e OF M H l SOUNTDMS PROJECT REVIEWERIDATE REV. PREPARERIDATE ;-l ELECTRICGENERATINGSTATION HOUSION LIGHTING & POWER o 41 4 er-/- 0 (Fy, n-H3 l J GENERAL COMPUTATION SHEET
^
\
UNIT is : SUBJECT calculator. The following equation summarizes the minimum 3 pressure difference versus load from the above data: l 6Pmin = 0.875 + 0.01292* load j Reference 1.A calculated conservative minimum loads for Loss of-Offsite Power, with all three trains starting and operating without operator action. The lowest load for normal dual train ) operation was 100 tons, while the lowest load for single train operation was 121 tons. Using compressor input obtained from j Ref. 3.A, the total condenser heat load is: Qtotal = tons *12000 + motor.eff*KWin*3413 btu /kw.hr i 6 0 100 tons Qtotal=100*12000 + 0.9*96.3*3413 = 1.50 x 10 btu /hr 0 121 tons Qtotal=121*12000 + 0.9*99.1*3413 = 1.76 x 106 btu /hr i With the temperature control set up to provide 40 *F at minimum ! load (30 tons) and 48 *F at rated load (300 tons), the outlet ! chilled water as a function of load is: l Tout = 40 + Load-30
- 8 300-30 -i At 121 tons (occurs in train B, other trains considerably higher) :
i Tout = 42.7 'F i Pevap = 7.50 psia 6P = 2.44 psid i Pcond 2 7.50 + 2.44 = 9.94 psia r Tsat O'9.94 = 55.5 *F j At 100 tons (occurs in train C, other trains at 106 tens) s Tout = 42.1 'F ! i Pevap = 7.40 psia j 6P = 2.17 psid i i t
STP 361(1248) : CALC NO. mex SHI n OF M- ' SOUTHTEXASPROJECT PREPARERlDATE REVIEWERIDATE REV. , ELECTRICGENERATINGSTATION HOUSTON LIGHTING & POWER o yg . /N F43 % ny-4 <3, GENERAL COMPUTATION SHEET ff SUBJECT UNIT Is j Pcond 2 7.40 + 2.17 = 9.57 psia j Tsat @ 9.57 = 53.7 *F : I Using the Condenser Model spreadsheet described in section C, the i conditions for 121 tons & 100 tons and 240 gpm are met with an l ECW inlet temperature of 40.2 & 40.7 *F, respectively. The ! results are shown in Appendices 8.a & 8.b. Allowing-for 10 gpm i flow error, the results for 100 tons and 250 gpm provide a . minimum temperature slightly above 41 *F. Using 42 *F as the ; minimum temperature at 240 gpm, indicated, provides for j temperature indication error. .i
.i Because the use of the " clean" heat transfer coefficient provides 'i additional conservatism, and because the minimum load was ;
obtained in a conservative manner, no addition error margins are j necessary. , While ECP temperatures below 42 *F are very infrequent, j temperatures below this range have occurred and may occur again. _. ; 3 3
-) -!
There are two remaining conservative factors which could provide i j for operation at lower temperatures: 1) the chiller can produce i i the required load with a lower motor current limit, so the ; initial transient upon starting an idle chiller can be reduced by : I lowering the current limiter setpoint; and 2) the peak load calculation did not account for the throttling effect of the l prerotation vanes to match the compressor curve to chiller demand. i The information currently available from York is not sufficient to formalize the capacity increase available with the higher chilled water load, so temperatures below 42 *F are not l completely covered in this calculation. In anticipation of ; obtaining the necessary data, Appendix 8.d analyzes 200 gpm (190 l gpm nominal with 10 gpm flow error) at 100 tons to determine the minimum ECW temperature acceptable under different conditions. K. CHILLER REQUIREMENTS DURING MODES 5, 6, AND DEFUELED MODES The essential chilled water is required to support operability of Class 1E electrical equipment in the EAB and habitability in the Control Room during cold shutdown, refueling, and defueled modes j l l i
STP 361 (12 88) CALC NO. e-u n o SHT a s OF M SOUTHTEXAS PROJECT REV. PREPARERIDATE REVIEWERIDATE ELECTRICGENERATING STAil0N i HOUSTON LIGHTING & POWER o Vf[ //-/- G @B u-\- e GENERAL COMPUTATION SHEET SUBJECT UNIT is i of operation. With the Safety Injection signal blocked below j Mode 4, there is no automatic signal to start the air handling units simultaneously. While a high radiation signal starts some ! s equipment in the FHB, it does not start equipment in rooms cooled l by the essential chilled water system. Loss of Offsite power ! starts some additional Class 1E equipment, but this is - accompanied by loss of the non-class lE equipment heat loads. , The few design basis accidents considered in Modes 5, 6, & ; Defueled mode do not cause significant additional load to the essential chilled water system. Therefore, without detailed accounting of heat loads, if the chilled water system can remove- ! heat loads existing during normal operation in these modes the system can meet post accident requirements. l Experience with the essential chilled water system has demonstrated the system can meet normal cooling loads with one j 150 ton chiller operable in two trains. This has been true even ; with the significant convective heating occurring through the idle 300 ton chiller much of the time. With ECW supply temperatures above 69 'F, a chilled water train ' is operable in modes 5, 6, or defueled mode with both chillers operable, or either the 150 ton or 300 ton chiller operable. If the 300 ton chiller is not operable, the ECW flow to that chiller j should be stopped to stop the additional load of convective , heating. This may also be done in case of an. inoperable 150 ton ! chiller, if desired to reduce electrical consumption. With ECW supply temperatures below 60 *F, an operable train must l have one and only one chiller operable. Either the 150 or the l[ 300 ton chiller is acceptable. The inoperable chiller must have ECW flow through the chiller stopped to prevent convective ll cooling or heating. j Between 60 'F and 69 'F, either arrangement is acceptable. ! 3 The initial load when starting a chiller which has been idle does }' not depend on the actual chilled water load. The chiller will be fully loaded, as determined by the current limiter, until chilled . water temperatures are reduced to the control band. Thus for a j idle but operable 300 ton chiller during " cold ECW" operation, l ! the ECW flow path must be through the bypass with the valve set i at the 240 gpm position. The required flow through the 150 ton , chiller ECW bypass valve, when it is the operable chiller, is I determined as follous: I
I STP 361(1248) CALC NO. e-429 SHI s r OF M SOUTHTEXASPROJECT- REV. PREPARERlDATE REVIEWERlDATE - ELECTRICGENERATINGSTAil0N
- - HOUSTONLIGHTING & POWER 0- vd u + 13 $1 g-H3 1
j GENERAL COMPUTATION SHEET 1 SUBJECT UNIT ls j j Assume the 150 ton chiller is capable of.the same percent , increase in capacity due to higher chilled water outlet- l temperature as the 300 ton. l l Max. Load = (431 tons /300 tons)*150 tons = 215 tons Max compressor input = 215 kw 6 Max. Condenser load = 215*12000 + 215*3413 = 3.32 x 10 btu /hr- f: Using the condenser spreadsheet model for the 150 ton chiller, l with 69 *F ECW supply temperature, 120 gpm gives a saturation l temperature in the condenser of 128.5 *F (Appendix 6.c), which is -j less than the transient limit of 130 *F previously described. i 1 The vendor provided the minimum condenser pressure for 42 *F > leaving chilled water at several load points (Reference 2.D). l This will be corrected to the required chilled water temperature. i as follows: Assume evaporator pressure is saturated at leaving chilled water j temperature. It actually is saturated at a'slightly lower i temperature, but the difference is small and. effectively cancels -; out in the calculation. l l Pevap 0 42 *F = 7.38 psia .j load, tons cond. press. cond. press. 'Pcond-Pevap l' "HgV psia psid 159 3.22 13.11 5.73 t 120 5.29 12.09 4.71 80 7.23 11.14 3.76 The best fit curve of 6P versus load was obtained using the l linear regression analysis feature of the.TI-55III hand t calculator. The following equation summarizes the minimum j pressure difference versus load from the above data: j
~!
6Pmin = 1.75 + 0.0249* load ,
'f At a minimum load of 100 tons, the minimum 6P is 4.243 psid. j o.
i l I
I swm ona CALC NO. Mc-6429 SHf 41 OF M i SOUTH TEXAS PROJECT REV. PREPARERlDATE REVIEWERIDATE ELECTRICGENERATING STATION HOUSTON UGHTING & POWER o V//_ t/-i43 M M c6 GENERAL. COMPUTATION SHEET SUBJECT UNIT Is The condenser loads can be calculated from the entering and leaving water temperatures and the 600 gpm flow rate. The results for 80 tons and 120 tons are as follows: Qcond at 80 tons = 500*600*(56.43-52.47) = 1188000 btu /hr Qcond at 120 tons = 500*600*(58.69-52.88) = 1743000 btu /hr Take the average for 100 tons Qcond at 100 tons = 1470000 btu /hr The chilled water outlet temperature at 100 tons would be Tout = 40 + 100-15) / (150-15) *8 = 4 5. 0 "F Pevap = 7.898 psia 9 45.0 *F Pcond = 7.898 + 4.243 = 12.141 psia Tsat = 65.0 *F 0 12.141 psia Using the 150 ton condenser 6 model spreadsheet with Tsat = 65.0 to find Q = 1.47 x 10 btu /hr, Tin (min.) = 39.9 *F In Modes 5, 6, & Defueled Mode, if a chiller is operable, but in standby (ready to start automatically on the diesel), the ECW bypass valve should be set at the predetermined position which gives 240 gpm or 120 gpm, for the 300 ton or 150 ton chiller respectively. If the ECP is below 42 *F, the operators should be prepared to reduce flow within 20 minutes of the auto start of I the chiller. The operating chiller may have loads less than 100 tons and may experience ECW temperatures less than 42 *F. In such cases the flow to an operating chiller should be adjusted until the condenser pressure is within an operating band of 2" of HgV to 7 psin (or 14 psia to 22 psia).
i STPM1(1248) . CALC NO. Mc_ee29 SHT w 0F 56
. SOUTH fEU.S PROJECT REV- PREPARERIDATE REVIEWERIDATE -- -<
ELECTRICGENERATINGSTATION
.. HOUSTON UGHTING & POWER o Vfj_ 0-t- f3 % \\-\-48 GENERAL COMPUTATION SHEET j i
SUBJECT ONIT ls ' b S L.- CAPACITY OF HOT GAS VALVE ! For an case of interest, the flow through the Hot Gas Valve will be choked. This means the flow rate is independent of the j evaporator pressure. Therefore the slight increases to -! t 'corator pressure due to higher chilled water outlet l
+. ratures will not reduce the capacity of the Hot Gas Valve. l Th< ondenser pressures have increased to keep the minimum J pressure differential, so any changes to Hot Gas Valve capacity I will be. positive. :
[ t
'b I
-5.
i 1 l t t 1 6 i 1
300 TON CHILLER COMPRESSOR MODEL APPENDIX 1 Calc. No. MC-6429 Page W of I ' shoptest 300T@48 F MAX @48F MAX, trial f.*}{-/-13 ' MAX g_q Te 41.05 47.5 47.5 57.5 57.5 Tc 121.5 121.5 121.5 121.5 125 Pe 7.22 8.3513 8.3513 10.3759 10.3759 Pc 34.05 34.05 34.05 34.05 36.009 K_1 5 5 5 5 5 K_2 1.5 1.5 1.5 1.5 1.5 Vge 5.3115 4.6424 4.6424 3.7952 3.7952 Vge 1.2514 1.2514 1.2514 1.2514 1.1871 dTsc 2.6 2.6 2.6 2.6 2.8 Cp 0.217 0.217 0.217 0.217 0.217 load 3 01.9 300 379.1 452.4 431.3 shp 421.5 372.4 483.9 484.0 434.1 hg_evap 96 995 97.793 97.793 99.153 99.153 hf_cond 33.07 33.07 33.07 33.07 33.832 Oevap 3.623E+06 3.600E+06 4.549E+06 5.429E + 06 5.176E+06 ' w pph 56177 55141 69680 81456 78555 w ppm 936.3 91 9.0 1161.3 1357.6 1309.2 dP_1 0.76 0.64 1.02 1.14 1.06 P* 6.46 7.71 7.33 9.23 9.31 v_1 5.9376 5.0284 5.2910 4.2654 4,2287 k 1.11 1.11 1.11 1.11 1.11 (k-1)/k 0.09310 0.09910 0.09910 0.09910 0.09910 , comp.eff 0.70 0.70 0.70 0.70 0.70 tryP_2' 34.25 34.25 34.25 34.25 36.209 r' 5.3030 4.4422 4.6742 3.7099 3.8884 X' O.1798 0.1592 0.1651 0.1387 0.1441 T_2' 169.7 163.0 167.2 160.1 164.0 v_2' 1.3552 1.3406 1.349G 1.3344 1.2662 d P_2' O18 0.17 0.27 0.37 0.33 P_2 34.2282 34.2198 34.3231 34.4189 36.3346 r 5.2996 4.4383 4.6842 3.7282 3.9019 X 0.1797 0.1591 0.1654 0.1393 0.1444 T_2 169.7 162.9 167.4 160.5 164.3 v_2 1.3551 1.3405 1.3501 1.3353 1.2668 dP_2 0.18 0.17 0.27 0.37 0.33 gearloss 16 16 16 16 16 O_1 5559 4621 6145 5791 5536 shp 421.5 372.4 483.9 4 84.0 484.1 head,ft 10005 8958 9308 7964 8258 head,% 100 90 93 80 83 vol.fiow% 100 B3 111 104 100
300 TON COMPRESSOR MODEL, FORMULAS APPENDIX 2 Cate. No. MC-6429 Page 50 of M
'd4 .O Vf[ it-f-LT B1: [W10] ^ shoptest h N-A3: 'Te B3: [W10] 41.05 A4: 'Tc B4: [W10] 121.5 A5:'Pe BS: [W10] 7.22 A6:'Pc B6: [W10] 34.05 A7: 'K_1 B7: [W10] 5 AB: 'K,,,2 B8: [W10] 1.5 A9: 'Vge B9: [W10] 5.3115 A10: 'Vge B10: [W10] 1.2514 A11: 'dTsc B11: [W10] 2.6 A12: 'Cp B12: [W10] 0.217 A13: ' load B13: [W10] 301.9 A14: 'shp B14: (F1) [W10] +B40 A15: 'hg_evap B15: [W10] 96.995 A16: 'hf_cond B16: [W10] 33.07 A17: 'Oevap B17: (S3) [W10] + B13*12000 A18: 'w pph B18: (FO) [W10] +B17/(B15-B16+B11*B12)
A19:'w ppm B19: (F1) [W10] +B18/60 A20: 'dP_1 B20: (F2) [W10] 2.8E-07*B7*(B18) ^ 2*B9/(13.25) ^ 4 A21:'P_1 B21: (F2) [W10] +B5-820 A22: 'v_1 0
1 300 TON COMPRESSOR MODEL, FORMULAS APPENDIX 2 Cate. No. MC-6429 Pege 6 I of M Ce42 fff n-s-93 B22: (F4) [W10] +B9*B5/B21 _) \-\d') A23: 'k B23: [W10] 1.11 l A24: '(K-1)/k I B24: (FS) [W10] (B23-1)/B23 .) A25: 'cornp.eff B25: (F2) [W10] 0.7 A26: 'tryP_2' B26: [W10] 0.2+B6
- A27: 'r' B27: (F4) [W10] +B26/B21 i A28: 'X' B28: (F4) [W10] + B27 ^ BS24-1 A29: 'T_2' [
B29: (F1) [W10] +B$3+(B$3+460)*B28/B$25 A30: 'v_2' B30: (F4) [W10] + B10*(B29+460)/(B4+460) ; A31: 'dP_2' , B31: (F2) [W10] 2.8E-07*B8*(B18) ^ 2*B30/(10.02) ^ 4 ; A32. 'P_2 > B32: (F4) [W10] +B6+B31 A33: *r ! B33: (F4) [W10] +B32/B21 l A34: 'X B34: (F4) [W10] +B33 ^ B$24-1 l A35: 'T_2 B35: (F1) [W10] +B$3+(B$3+460)*B34/B$25 A36. 'v_2 B36: (F4) [W10] +B10*(835+460)/(B4+460) A37: 'dP_2 , B37: (F2) [W10] 2.8E-07*B8*(B18) ^ 2*B36/(10.02) ^ 4 A38: 'gearloss B38: [W10] 16 A39: 'Q 1, , B39. (FO) [W10] + B19*B22 .. A40: 'shp B40: (F1) [W10] 0.00436*B39*B21*B34/824/B25+B38 [ A41: ' head,ft B41: (FO) [W10] (B40-838)*33000*B25/B19 A42: ' head,% ! h
300 TOf4 COMPRESSOR MODEL FORMULAS APPENDIX 2 Cale. No. MC-6429 Pagef2-of $ [ E'd.0- Cff Is-t-93 B42: [W10] + B41/B41 *100 lH-O A43: 'vol. flow % B43: [W10] + B39/B39*100 P b k a 6 h v f I f t i 1 l i 1
~l I
i 300 Tons at 48 F APPENDIX 3.a Calc. No. MC-6429 Page53of 6 I Ee J 2. ' ff[ tv-t-1) { Ototal 4.55E+06 b . Tout 119.5 BASED ON CLEAN COEFFICIENT 7 NO 3 Tin 81.3 100.6588 111.568- 117.0389-Tsat 121.5 121.5 121.5 121.5 t gpm 240 240 240 240 Ap 1386.6 1386.6 1386.6 1386.6 ; spvol 0.016078 0.01613 0.016159 0.016174 visc 2.004195 1.493575 1.265485 1.164567
- G 293247.1 292296.8 291764 291497.6 l D 0.051 0.051 0.051 0.051 .}
Re 7462,147 9980.842 11758.31 12765.58 ; Dol 0.003701 0.003701 0.003701 0.003701 j j 0.004089 0.004029 0.004143 0.004075 ! Cp 0.997779 0.994488 0.992633 0.991703 K 0.354609 0.364279 0.369728 0.372461 } Pr 5.639287 4.077486 3.397529 3.100741 j MUw 1.088263 1.088263 1.088263 1.088263 Muratio 0.542993 0.72863 0 859958 0.934479 f h 346.6622 439 0006 519.7944 548.7907 : Uc 90.19728 108.9134 123.918 129 0211 , U 56.60012 63.44127 68.25543 69.77553 Cmin 119466.9 118687 118249.7 118031 , NTUp 0.656933 0.741174 0.800366 0.819706 EFF. 0.481561 0.523446 0.550835 0.559439 Op 2312729 1294787 646930.6 294571.3 deltaT 19.35875 10.90926 5.470887 2.495711 ! I r I h i l
i i I MAX: MUM at 48 F APPENDIX 3.b Calc. No. MC-6429 Page5Vof $f Vd S- U,{ st-t- 13 Ototal 5.78E+06 Tout 118.7 h n \.4'.h BASED ON CLEAN COEFFICIENT? NO Tin 70.3 93.56012 107.7791 115.2535 Tsat 121.5 121.5 121.5 1215 gpm 240 240 240 240 Ap 1386.6 1386.6 1386.6 1386.6 spvol 0.016048 0.016111 0.016149 0.016139 ' visc 2.368694 1.663635 1.340456 1.196583 G 293789.8 292644.5 291948.8 291584.5 D 0.051 0.051 0.051 0.051 Re 6325.546 8971.244 11107.7 12427.73 Dol 0.003701 0.003701 0.003701 0.003701 j 0.004075 0.004061 0.00419 0.004097 Cp 0.999649 0.995695 0.993278 0.992007 . K 0.349115 0.360733 0.367836 0.371569 Pr 6.782474 4.591959 3.619674 3.19461 - MUw 1.088263 1.088263 1.088263 1.088263 Muratio 0.459436 0.654148 0.81186 0.909476 h 299.5742 403.6529 500.6053 539.1567 Uc 79.93257 101.958 120.4615 127.3413 U 52.37921 61.01668 67.19344 69.2813 C min 119912.3 118972.4 118401.4 118102.3 NTUp 0.605685 0.711138 0.786903 0.813409 EFF. 0.454299 0.508915 0.544748 0.556656 Op 2789174 1691670 884979.7 410656.5 deltaT 23.26012 14.21902 7.474404 3.477125 , i 4 4
1 l l
.I TRIAL MAXIMUM TRANSIENT LOAD APPENDIX 3.c Calc. No. MC-6429 Page$$of 85 !
0J. 0 $ it-t-13 ; Ototal 6.66E+06 g n-) Tout 124.9 BASED ON CLEAN COEFFICIENT? NO i I Tin 69 95.45378 112.072 120.8258 Tsat 128 128 128 128 gpm 240- 240 240 240. > Ap 1086.6 1386.6 1386.6 1386.6 f spvol 0.016044 0.01611 6 0.01 6161 0.016184- { visc 2.415935 1.616461 1.255834 1.099466 f G 293854.1 292551.7 291739.4 291313.4 l Re 6203 2 923 . 2 1184 6 135 Dol 0.003701 0.003701 0.003701 0.003701 [ J 0.004071 0.004054 0.004137 0.004029 Cp 0.99987 0.995373 0.992548 0.99106 l K 0.346466 0.361679 0.36998 0.374352 - -} Pr 6.932166 4.448642 3.369034 2.910723 I MUw 0.985944 0.985944 0.985944 0.985944 [ MUratio 0.4081 0.60994 0.785091 0.896748 i h 290.2068 407.2391 515.2292 561.9694- ; Uc 77.82785 102.6751 123.1015 131.294 l U 51.46715 61.27279 68.00697 70.43497 . Cmin 119965 118896.2 118229.5 117879.9 -! NTUp 0.594876 0.71458 0.797588 0.828514 -[ EFF. 0.44B369- 0.510603 0.549586 0.563302 f Op 3173529- 1975838 1034961 476381.9 ! deltaT 26 45378 16.61818 8.753826 4.041249 f i i i i I I l
F. l l MAX. TRANSIENT CONDENSER LOAD APPENDIX 3.d Calc. No. MC-6429 Page5bof I iki A- 1[ n-r-f3 Ototal 6.41 E+06 n-\-43 [ Tout 122.8 BASED ON CLEAN COEFFICIENT? NO j Tin 69 94.51591 110.4524 118.8581 Tsat 125.8 125.8 125.8 125.8 .[ gpm 240 240 240 240 Ap 1386.6 1386.6 1386.6 1386.6 -! spvol 0.016044 0.016113 0.016156 0.016179 ' visc 2.415935 1.639655 1.287113 1.132825 j G 293854.1 292597.7 291818.4 291409.1 D 0.051 0.051 0.051 0.051 Re 6203.213 9100.989 11562.89 13119.29 Dol 0.003701 0.003701 0.003701 0.003701 1 j 0.004071 0.004058 0.004157 0.004053 Cp 0.99987 0.995532 0.992823 0.991394 ; K 0.348466 0.361211 0.369171 0.37337 [ Pr 6.932166 4.519051 3.461473 3.007948 MUw 1.01945 1.01945 1.01945 1.01945 - MUratio 0.421969 0.621747 0.792044 0.899918 h 291.5678 404.5915 509.3906 553.6956 Uc 78.13498 102.1459 122.052 129.8704 U 51.60128 61.08395 67.68543 70.02318 Cmin 119965 118933.9 118294.3 117958.4 ; NTUp 0.596427 0.712152 0.793382 0.823122 EFF. 0.449224 0.509413 0.547688 0.560941 ; Op 3061016 1895391 994344.2 459329.7 dettaT 25.51591 15.93651 8.405679 3.893998 : i r
?
t I I l 1
l t c/ 1 SHOP TEST RESULTS APPENDIX 3.e Calc. No, MC-6429 PageMef ob j SG L Qf) ot-t-13 l 1 Ototal 4.69E+06 g-4'3 j Tout 120.4 + BASED ON CLEAN COEFFICIENT? YES t Tin 111.68 116.2138 118.5666 119.76 f Tsat 120.95 120.95 120.95 120.95 '! gpm 1099 1099 1099 1099 j Ap 1386.6 1386.6 1386.6 1386.6 { spvol 0.01616 0.016172 0.016178 0.016181 visc 1.263334 1.179256 1.137853 1.117411 G 1336011 1335000 1334476 1334210 ; D 0.051 0.051 0.051 0.051 l Re 53933.94 57735.S7 59812.89 60894.96 [ Dol 0.003701 0.003701 0.003701 0.003701 f j 0.003055 0.003014 0.002992 0.002982 ; Cp 0.992614 0.991844 0.991444 0.991241 j K 0269784 0.372049 'O.373224 0.37382 l Pr 3.391176 3.143774 3.022626 2.962985 { MUw 1.097393 1.097393 1.097393 1.097393 ! MUratio 0.868649 0.930581 0.964442 0.982086 f h 1759.752 1840.727 1884.188 1906.619 ! Uc 262.2371 267.7485 270.5994 272.0426 i U 96.20618 96.93822 97.30939 97.4954 Cmin 541464.5 540634.5 540204.3 539986.2
- NTUp 0.671545 0.686712 0.694576 0.698563 ;
EFF. 0.489082 0.496772 0.500714 0.502701 ! Op 2454885 1272014 644679.6 323026 ! dettaT 4.533787 2.352818 1.1934 0.598212 l i j l l 1 I i
l
)
i I MAX. TRANS. w/ 225 gpm ' APPENDIX 3.f Calc. No. MC-6429 Pago 66 of 3T -- i
& 4* Q-if[ tI-l-f.3 0:otal 6.41 E+06 . gg-AG . I Tout 126.4
~'
BASED ON CLEAN COEFFICIENT? NO Tin 69 96.46705 113.647 122.4693 Tsat 129.2 129.2 129.2 129.2 gpm 225 225 225 225. I Ap 1386.6 1386.6 1386.6 1386.6 spvol 0.016044 0.016118 0.016165 0.016189 j visc 2.4'.5935 1.591771 1.226144 1.072357 G 275488.2 274220.7 273433.8 -273031.4 f D 0.051 0.051 0.051 0.051 l Re 5815.512 8785.974 11373.16 12985.04 l Dol 0.003701 0.003701 0.003701 0.003701
- j 0.004052 0.004066 0.00417 0.004061 f Cp 0.99987 0.995201 0.99228 0.99078 f K 0.348466 0.362185 0.370767 0.375173 f Pr 6.932166 4.373814 3.281519 2.831944 MUw 0.968134 0.968134 0.968134 0.96813a MUratio 0.400729 0.608212 0.789577 0.90281 -
h 270.1098 387.0364 495.7441 541.0747 Uc 73.23913 98.60055 119.5756 127.677 , U 49,41956 59.79813 66.91688 69.38053 Cmin 112467.2 111426.9 110781.1 110450.9 5 NTUp 0.60929 0.74413 0.83757 0.871003 EFF. 0.456263 0.524852 0.567239 0.581468 -l Op 3089142 1914311 977340.1 432272.1 i deltaT 27.46705 17.17996 8.822262 3.913702 ! i k l I I i l r I
t TRANSIENT LOAD W/ LOAD LIMIT APPENDIX 3.g Calc. No. MC-6429 Page59 of T'S Sed S l}[ n-t-9.3 Ototal 5.10E+06 . g_ H 3 Tout 123.0 BASED ON CLEAN COEFFICIENT? - NO ; Tin - 69 95.68706 111.9674 119.7089 Tsat 125 125 125 125 , gpm 190 190 190 190 Ap 1386.6 1386.6 1386.6 1386.6 , spvol 0.016044 0.016116 0.01616 0.016181 - visc 2.415935 1.610743 1.25783 1.118278 I G 232634.5 231594.4 230964.4 230666.1 D 0.051 0.051 0.051 0.051 Re 4910.677 7332.836 9364.689 10519.72 i Dol 0.003701 0.003701 0.003701 0.003701 l j 0.003965 0.004089 0.00405 0.004236 Cp 0.99987 0.995333 0.992566 0.991249 [ 0.348466 0.361796 0.369928 0.373795 K I Pr 6.932166 4.431302 3.374926 2.965512 MUw 1.031915 1.031915 1.031915 1.031915 ! Muratio 0.427129 0.640645 0.820393 0.922771 ! h 225.1782 328.2707 401.3474 463.9894 U 62.60363 86.24945 101.4956 113.6829 U 44.33702 55.01979 60.85077 65.03052 l Cmin 94972.31 94118.69 93601.69 93356.83 NTUp 0647323 0.810577 0.901433 0.955878 EFF. 0.476555 0.555399 0.594013 0.619351 Op 2534531 1532287 724618.9 305932.7 deltaT 26.68706 16.28037 7.741516 3.277025 i l i i 1 i
/
APPENDIX 4.a Cale. No. MC4429 Page bO Dof gb 300 CondnSer Model Formulas Ru. O gj{ a+13 A1: 'Ototal g gg E1: (S2) @ SUM (B26..E26) , i A2: Tout E2; (F1) + E4 + E27 A3:
- BASED ON CLEAN COEFFICIENT 7 E3:'NO A4: Tin >
B4: 81.3 C4: + B4 + B27 D4: + C4 + C27 E4: + D4 + D27 A5: 7 sat B5: 121.5 C5: + B5 05: + B5 , E5: + B5 A6: 'gpm B6.240 C6: + B6 D6: + C6 E6: + D6 A7; 'Ap B7: 1386 6 C7: 1386 6 D7.1386 6 E7: 1386 6 A8;'spvol r B8: @lF(B4>60,0 01585B + 2 7E-06* B4.0.01602) C8:GIF(C4>60.0 015058+2 7E46*C4,0.01602) D8: @lF (D4 >60,0 015858+ 2.7E46*D4,0.01602) E8: @lF(E4 > 60,0.015856 + 2.7E46*E4.0.01602) A9: 'visc , B9: 0 0019142*@EXP( 0 015190541*B4)*3600 C9: 0 0019142*@EXP(4.015190541*C4)*3600 D9; O 0019142*@EXP(-0 015190541*D4)*3600 E9: 0.0019142*@EXP(-0 015190541 *E4)*3600 AI D: "G q l
h 300 Condenser IAodel Formulas APPENDIX 4.a Catc. No. MC4429 Page $ I of W Ru o tjf1,.,-a B10: 60*B6/7.4805/BB/0.4083 C10 60*C6/7.4805/C8/0.4083 DIO: 60*D6/7.4805/D8/0.4083 E10: 60*E6/7.4805/E8/0.4083 A11:'D B11: 0.051 C11: 0 051 D11:0 051 E11:0.051 A12: 'Re B12; 4 B10*B11/B9 C12: + C10*C11/C9 D12: + D10*D11/D9 E12: 4E10*E11/E9 A13 ' Dol B13: 0.051/13.78 C13: 0 051/13.78 D13: 0.051/13.78 E13: 0 051/13.78 A14: 'j B14: @lF(B12<2100,1.86/(B12 ^ 0 66667*(1/B13)
- 0.33).@lF(B12> 10000.0.027/B12 ^ 0 2.0,116*(312 ^ 0.66667-125)*(1 + B13 ^ 0.66667)/B12)) i C14: @lF(C12<2100,1.86/(C12 ^ 0.66667*(1/C13) ^ 0,33),@lF(C12>10000,0.027/C12 ^ 0.2.0.116*(C12 ^ 0.66667-125)*(1 + C13
- 0 66667)/C12))
D14: GIF(D12 < 2100,1.86/(D12 ^ 0 66667 * (1/D13) ^ 0.33),@lF (D12 > 10000,0.027/D12 ^ 0.2,0.116* (D12 ^ 0.66667-125)* (1 + D13 ^ 0.66667)/D12)) i E14: @lF(E12<2100,1.86/(E12 ^ 0.66667*(1/E13)
- 0 33) @iF(E12>10000.0.027/E12 ^ 0.2,0.116*(E12 ^ 0.66667125)*(14 E13 ^ 0.66667)/E12)) {
A15: 'Cp B15: 1.0116 0.00017*B4 C15: 1.0116-0 00017'C4 i D15: 1.0116-0.00017* D4 ; E15: 1.0116400017'E4 > A16: 'K ] B16: 0.314 + 0.0004995'B4 l C16: 0.314 + 0.0004995'C4 ~I D16: 0 314+ 0.0004995*D4 E16: 0 314 + 0.0004995*E4 i A17: 'Pr B17: 4 D9'B15!B16 6 C17; 4 C9'C15/C16 l i i l i r
i g/ i 300 Condensor Model Formulas APPENDIX 4 a Calc. No. MC-6429 Page Nof A
~5
$4 4. O
\!f M-t-f)
D17: + D9*D15/016 $\ E17: 4 E9'E15/E16 '{ A18: ' mow l B18: 0 0019142*@EXP(-0.015190541*B5)*3600 C18: 0.0019142*@EXP(4.015190541 *C5)*3600 i D18; 0.001914?*@EXP(4 015190541*D5)*3600 , E18: 0.0019142* @EXP(4.015190541
- Ed)*3600 -
r A19: 'Muratio [ B19: 4 B18/89 i C19: + C18/C9 D19: + D18/D9 E19: 4 E18/E9 A20; 'h i B20. + B14*B15*B10*(B17 ^ (4 66667)}* B19 ^ 0.14 C20: 4 C14*C15*C10*(C17 ^ (-0 666f 7))*C19 ^ 0.14 , D20: 4 D14 *D15*D10* (D17 ^ (4 66667))*D19 ^ 0.14 E20: + E14*E15*E10*(E17 * (0 66667))*E19 ^ 014 A21: 'Uc B21: 1/(0.002029 + 314/B20) C21: 1/(0.002029 + 3.14/C20) D21: 1/(0 002029+ 314/D20) E21: 1/(0.002029 4 3.14/E20) A22: 'U B22: 1/(0.00061 + 314/B20) , C22: 1/(0.00861 + 3.14/C20) i D22: 1/(0 008614 314 /020) E22: 1/(0 00861 + 3.14/E20) i A23: 'Cmin B23: + B6*60/7.4805/B0*B15 C23: 4 C6* 60,7.4805/C8'C15 D23:
- D6*60/7.4805/D8*D15 E23: + E6*60/7 4805/E8'E15 A24. *NTUp B24: GIF($E$3=*YES*,4 B21*B7/B23.+ B22*B7/B23) l C24: Gif(5E$3="YES*.* C21*C7/C23, + C22'C7/C23) l D24: @lF (SE$3 ="YES*.4 D21
- D7/D23.+ D22*D7/D23)
E24: GIF{$E$3 =*YES*.+ E21 *E7/E23,4 E22* E7/E23) F e__ __ .__. .__ __.__ _.
i 300 Condenser Model Formutas APPEND:X 4 a Calc. No. MC-6429 Page 43 of1 in.o dj G -p A25: 'EFF. 3 \b\q3 B25; 1@EXP(.B24) , C25: 1@EXP(-C24) D25: 1-@EXP(-D24) E25: 1.@EXP(~E24) A26: 'Op j D26: + B23*B25*(B5-B4) i C26. + C23'C25*(C5-C4) .! Dil't + D23*D25*(D5-D4) E26:4 E23*E25'(E5-E4) l A27: 'daltaT , B27: + B26/B23 C27: + C26/C23 D27: + D26,023 E27: + E26/E23 I i i 2 l l I l i p i t l i t
?
I
+
?
I
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i t 4
i I d t l i 150 Ton Condenser Model Formulas APPENDIX 4 b Calc. No. MC6429 PaDe W of Ra o qf a-,-o j A1: 'Ototal \\-\-V3 r E1: ($2) @ SUM (B26..E26) t A2: ' Tout E2: (F2) + E4 + E27 A3: ' BASED ON CLEAN COEFFICIENT 7 ! E3:'NO
'i A4 : ' Tin t
.I B4: 110 f
C4: + B4 + B27 ! D4: + C4 + C27 I E4: + D4 + D27 r AS: *Tsat I B5: 125.35 E i C5: + B5 D5: + B5 E5: + B5 , A6. *gpm 5
?
B6: 600 C6: + BG l
.I D6: + C6 E6: + D6 A7; 'Ap B7: 765 3 C7: 765.3 '!
D7: 765.3 - 6 E7: 765.3 A8: 'spvoi f , BB: @lF(B4 > 60.0 015858 + 2.?C 06*B4,0 01602) j CB: @lF(C4>60,0 015858+ 2.7E46*C4,0.01602) f DB: @lF(D4 >60,0.015858+ 2.7E-06*D4.0 01602) : 1 E8: @lF(Ed >60.0 015858 + 2.7E-06*E4.0.01602) . A9: 'visc j B9: 0.'J019142*@ EXP(-0.015190541
- B4)*3600 9
F t " ---x - .
'-*rv--
i I s
~
I i j i 150 Ton Condenser Model Formulas APPENDIX 4.b Calc. No. WC6429 Page h of fes o /// &,-r3 l C9: 0 0019142*@EXP(-0 015190541*C4)*3600 ll- \-(6 . l D9: 0.0019142*@EXP(4 015190541*D4)*3600 E9; 0.0019142*@EXP(4.015190541
- E4)*3600 f A10: *G I
B10: 60*B6/7.4805/B8/0.1331
's C10: 60*C6/7.4805/C8/0.1331 D10: 60*D6/7.4805/D8/0.1331 f E10: 60*E617.4805/E8/01331 i A11:*D i i
B11: 0 0442 l C11:0.0442 'f D11: 0 0442 E11: 0.0442 , A12: 'Re i D12: + B10*B11/B9 -[ C12: + C10*C11/C9 .I D12: + D10*D11/D9 ! E12: + E10*E11/E9 l c 8 A13: ' Dol I B13: 0.003205 ! C13: 0.003205 DI3: 0 003205 l E13. 0.003205 ; A14:'j - B14: @lF(B12<2100,1 66/(B12 ^ 0 66667*(1/813) ^ 0.33),@lF(B12> 10000,0 027/B12 ^ 0.2.0.116*(812 ^ 0 66667125)*(1 + B13 ^ 0 66667)/B12)) ! i C14: @lF(C12<2100,1.86/(C12 ^ 0 66667*(11C13)
- 0.33),@lF(C12> 10000,0 027/C12 ^ 0.2.0.116*(C12 ^ 0.66667-125)*(14 C13 ^ 0.66667)/C12)) j D14: @lF(D12< 2100,1.86!(D12 ^ U.65667*(1/D13) ^ 0.33),@lF(D12>10000,0 027/D12 ^ 0.2,0.116*(D12 ^ 0.66667-125)*(1 + D13 ^ 0.66667)/D12)) l i
i Eid: @lF(E12 < 2100,1. 86/iE12 ^ 0 66667* (1/E13) ^ 0.33),@lF(E12>10000,0 027/E12 ^ 0 2.0.116*(E12 ^ 0 66667-125)*(1 + E13
- O 66667)/E12)) -j A15: 'Cp {
B15: 1.01164 00017*B4 C15: 1.01164 00017*C4 D15: 1.01164 00017'D4 E15: 101164 00017*E4 J I t lI 1
}
i i k i I k v i 150 Ton Condenser Model Fortnulas APPENDIX 4.b Calc. No. MC6429 PagekofdI ,; AO & 11-* ~4} . A16: 'K {\d-fd i B16: 0.314 + 0.0004995'B4 C16: 0 314 + 0 0004995*C4 D16: 0.314 + 0 0004995*D4 E16. 0 3144 0.0004995'E4 t A17; 'Pr l
~
B17; + B9'B15/B16 C17: + C9*C15/C16 D17; + D9*D15/D16 E17: + E9'E15/E16 A18: 'MUw h
~
B18: 0,0019142*@EXP(-0 015190541 *BS)*3600 !
.t C18 0.0019142*@EXP(-0 015190541*C5)*3600 ;
'i 018: 0.0019142 * @ EXP(4.015190541 *D5)*3600 .
E18. 0 0019142'@EXP(4 015190541*E5)*3600 A19: 'Murate ! I B19: + B18T$9 i t C19. + C18/C9 l - D19: 4 D18/D9 -1 I E19: + E18'E9 I A20 'h j B20: + B14*B15'B10*(B17 ^ F0 66667))*B19 ^ 0.14 i C20: + C14'C15'C10*(C17 ^ (-0.66667))* C19
- 0.14 D20: + D14 *D15'D10*(D17 ^ (-0 66667))*D19 ^ 0.14 (
l E20:
- E14'E15*E10*(E17 ^ FO 66667))*E19 ^ 0.14 !
s A21: Uc -l B21: 1/(0.003436 + 4.611820) l C21:1/(0.003436+ 4 61/C20) D21: 1/(0 003436+ 4 61/D20) -l l E21:1!(0 003436+4 61/E20) A22: V '}* j B22; 1/(0 0115+ 4 61/B20) C22:1/(0 0115+4 61/C20) .l l I I
~r a
1 i
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'i 1
l 1 i f I 150 Ton Condenser Modet Formulas APPENDIX 4.b Calc. No. MC6429 PageMof NJ0 Of{ II-t-[I D22: 1/(0.0115+4 61/020) p.A$ .f E22: 1/(0 0115 + 4.61/E20) A23: 'Cmin B23: + B6*60/7.4c05/BB*B15 C23: + C6*60/7 4805.C8'C15 D23: + D6*G0/7.4805/DB*D15 E23: + EC*60/7.4805/E8'E15 I A24: 'NTUp j B24: @iF($ES3 =*YES* + B21*B7/B23,+ B22*B7/B23) I I C24: @lF(3 E13 =*YES*,+ C21*C7/C23,+ C22*C7/C23) ; D24: GIF($E S3 ="YE S*,+ D21
- D7/D23,+ D22*D7/D23)
E24: @lF(SES3="YES* + E21*E7/E23.+ E22*E7/E23)
- A25: *EFF. ;
i B25: 1 C EXP(.B24) : [ C25: 1-@EXP(C24) , 025.14EXP(C24) [
-i
, E25: 1 -@EXP( E24) -[ A26: 'Op [ B26: + B23*B25*(35-64) '! C26' + C23*C25*(C5-C4) I D26: + D23*D25*(D5-D4) ) r F.26: + E23*E25*(ES-E4) , A27; 'deltai -! B27:+ B26'B23 l f C27: + C26lC23 D27: + D26/D23 : E27: + E26123 f i 5 l l
'i e .
R-11 PROPERTIES, EXAMPLE SPREADSHEET APPENDIX 5.a Cate. No. MC-6429 Pa e (c6of[ E C V. A
\f[ tt+ f.3 T P Vg rho Hf Hg g pq l 68.3 l 12.9771 l 3.0827 l 92 863 l 21.517 l 100.361 l TEMP PRESSUR SP. VOL. DENSITY ENTHALPY VAPOR LIQUID LIQUtD VAPOR F PSIA CF/LBm LBm/CF BTU /LBm BTU /LBm 10 3.3592 10.803 97.44 9.3727 93.158 20 4.3529 8.4942 96.673 11.404 94.391 30 5.5715 6.7559 95.9 13,464 95.627 40 7.0497 5.4311 95.119 15.547 96.865 50 8.8251 4.4094 94.33 17.65 98.102 60 10.938 3.6129 93.533 19.768 99.339 70 13.429 2.9856 92.725 21.901 100.57 80 16.345 2.4867 91.907 24.045 101.8 90 19.732 2.0864 91.078 26.201 103.03 100 23.637 1.7625 90.237 28.368 104.24 110 28.113 1.4983 89.382 30 545 105.45 120 33.21 1.2811 88.513 32.734 106.65 130 38 983 1.1013 87.63 34.933 107.83 140 45 486 0.95152 86.73 37.145 109.01 150 52.777 0.82591 85.813 39.369 110.16 40 7.0497 5 4311 95.119 15.547 96.865 50 8.8251 4.4094 94.33 17.65 98.102 60 10.938 3.6129 93.533 19.768 99.339 70 13.429 2.9856 92.725 21.901 100.57 0.303387 0.23373 4 093494 0.669073 4.168634
-1.76199 -0.88037 -18.8336 -3.52394 -19.5867 4.814979 1.590422 41.17383 8.702002 43.72957 9 62073 2.138927 66.42953 15.69019 72.04981 l I i +
l l l
R 11 PROPERTIES, FORMULAS APPENDIX 5.b Calc. No. MC-6429 Page $7 of[ l Seb 2.- . G[ It-t~93 A1: ^T gg-O , B1: ^ P l C1: ^Vg D1: ^ rho E1: ^ Hf f F1: ^Hg - A2: 68.3
~
B2: (F4) @ SUM (B27..B30) C2: (F4) @ SUM (C27..C30) D2; (F3) @ SUM (D27..D30) E2: (F3) @ SUM (E27..E30) F2, (F3) @ SUM (F27..F30) A3: ^ TEMP B3: ' PRESSURE C3: 'SP. VOL. D3: ' DENSITY E3:
- ENTHALPY -
C4: ^ VAPOR D4: ^ LIQUID E4: ^ LIQUID + i F4: ^ VAPOR I A5: ^ F B5: ^ PSIA C5: ^ CF/LBm ! DS: ^LBm/CF l ES: ^ BTU /LBm F5: ^ 8TU/LBm A6: 10 i B6: 3.3592 - i, C6: 10.803 ! t DS: 97.44 ; .; . E6: 9.3727 I F6: 93,158 ! A7:20 ! 37: 4.3529 C7: B.4942 D7: 96.673 E7: 11.404 ! F7: 94.391 ! A8: 30 J _ _ . . _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ . _ _ . _ _ _ _ _ _ ,__ __ m ..__. .
R-11 PROPERTIES, FORMULAS APPENDIX 5.b _ Cale. No. MC4429 Page 70 of_3I QcJ,0._ fjp gy-9,3_ B8: 5.5715 go . C8: 6.7559 1 D8: 95.9 : E8: 13.464 F8: 95.027 'i A9: 40 ; B9: 7.0497 . C9: 5.4311 09:95.119 ! E9: 15.547 ; F9: 96.865 q A10: 50 ) 810: 8.8251 f C10: 4.4094 .l D10: 94.33 - E10: 17.65 F10: 98.102 A11: 60 ; B11: 10.938 C11: 3.6129 4 D11: 93.533 E11: 19.768 F11: 99.339 A12: 70 B12: 13.429 I C12: 2.9356 -l D12: 92.725 l E12: 21.901 l F12: 100.57 l A13: 80 ; B13: 16.345 l C13: 2.4867 . D13: 91.907 ! E13: 24.045 ; F13: 101.8 A14: 90 B14: 19.732 ! C14: 2.0864 . D14: 91.078 E14: 26.201 ! i
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.l R-11 PROPERTIES. FORMULAS APPENDIX 5.b Calc. No. MC-6429 Pa e 7 / of ('a' l kel..A { & il-i-9.3 i P
F14: 103.03 A15:100 g 13 \% - i B15: 23.637 ! C15: 1.7625 , D15: 90.237 f E15: 28.368 [ F15: 104.24 [ A16:110 ' B16: 26.113 C16: 1,4983 ! D16: 89.382 f E16: 30.545 F16: 105.45 { A17:120 ! B17: 33.21 l C17: 1.2811 .. i D17: 88.513 E17: 32.734 F17: 106.65 i A18: 130 t B18: 38.983 l C18: 1.1013 D18; 87.63 E18: 34.933 I F18: 107.83 A19:140 B19: 45.486 .j C19: 0.95152 f D19: 86.73 l E19. 37.145 F19: 109.01 f A20: 150 I B20: 52.777 ! C20; 0.82591 l D20: 85.813 I E20: 39.369 F20: 110.16 ; A22: @VLOOKUP($A$2-20,$A$6..$HS20,0) f B22: @VLOOKUP($A$2-20,$A$6..$H$20,1) l C22: @VLOOKUP($A$2 20,$A$6..$H$20,2)
, .- ~ ,_ - _ , 4
R-11 PROPERTIES, FORMULAS APPENDIX 5.b Calc. No. MC-6429 Page 72 of N ! Rel o Q n+93 j D22: @VLOOKUP($A$2-20,$A$6..$HS20,3) gA 4S . E22: @VLOOKUP($A$2-20,$A$6..$H$20,4) F22: @VLOOKUP($A52-20,$A$6..$H$20,5) ; A23: @VLOOKUP($A$2-10,$A$6..$H$20,0) f B23: @VLOOKUP($A$2-10,$A$6..$H$20,1) { C23: @VLOOKUP($A$2-10,$A$6..$HS20,2) i D23: @VLOOKUP($A$2-10,$A$6..$H$20,3) E23: @VLOOKUP($A$2-10,$A$6..$H$20,4) F23: @VLOOKUP($A$2-10,$A$6..$H$20,5) A24: @VLOOKUP($A$2,$A$6..$H$20,0) 824: @VLOOKUP($A$2,$A$6..$HS20,1) C24: @VLOOKUP($A$2,$AS6..$H$20,2) { D24: @VLOOKUP($A$2,$A$6..$HS20,3) E24: @VLOOKUP($A$2,$A$6..$H$20,4) F24: @VLOOKUP($A$2,$A56..$HS20,5) [ A25: @VLOOKUP($A$2+10,$A$6..$HS20,0) B25: @VLOOKUP($A$2+10,$A$6..$H$20,1) { C25: @VLOOKUP($A$2+10,$A$6..$H$20,2) D25: @VLOOKUP($A$2+10,$A$6..$H$20,3) 'I E25: @VLOOKUP($A$2+10,$A$6..$H$20,4) f F25: @VLOOKUP($A52+10,$A$6..$H$20,5) i B27: ($A$2-A23)*($A$2-$A$24)*($A$2-$A$25)*$BS22/(-6000) C27: ($A$2-$A$23)*($A$2-SA$24)*($A$2-$A$25)*C22/(-6000) $ D27: ($A$2 $A$23)*($A$2-$A$24)*($A$2-SA$25)*D22/(-6000) ; E27: ($A$2-$A$23)*($A$2-$A$24)*($A$2-$A$25)*E2.2/(-6000) [ F27: ($A$2-$A$23)*($A$2-$A$24)*($A$2-$A$25)*F22/(-6000) i B28: ($A$2-$A$22)*($A$2-$A$24)*($A$2-$A$25)*B23/(2000) C28: ($A$2-$A$22)*($A$2-$A$24)*($A$2-$A$25)*C23/(2000) D28: ($A$2-$A$22)*(SA$2-$A$24)*($A$2-$A$25)*D23/(2000) ! E28: ($A$2-SA$22)*($A$2-$A$24)*($A$2-$A$25)*E23/(2000) f F28: ($A$2-$A$22)*($A$2-$A$24)*($A$2-$A$25)*F23/(2000) l C23: ($A$2-$A$22)*($A$2-$A$23)*($A$2-$A$25)*B24/(-2000) f C29: ($A$2-$A$22)*($A$2-$A$23)*($A$2-$A$25)*C24/(-2000) f D29: ($A$2-$A$22)*($A$2-$A$23)*($A$2-$A$25)*D24/( 2000) -l E29: ($A$2-$A$22)*($A$2-$A$23)*($A$2-$A$25)*E24/(-2000) ; F29: ($A$2-$A$22)*($A$2-$A$23)*($A$2 $A$25)*F24/(-2000) [ B30: ($A$2-$A$22)*($A$2-$A$23)*($A$2-$A$24)*B25/(6000) C30: ($A$2-$A$22)*($A$2-SA$23)*($A$2-$A$24)*C25/(6000) D30: ($A$2-$A$22)*($A$2-$A$23)*($A$2-$A$24)*D25/(6000) E30: ($A$2-$A$22)*($A$2-$A$23)*($A$2-$A$24)*E25/(6000)
I R-11 PROPERTIES, FORMULAS APPENDtX 5.b Calc. No. MC-6429 Page73 of SI i Se/ A Y,dh it~(-93 F30; ($A$2-$A$22)*($A$2-$A$23)*($A$2-$A$24)*F25/(6000) ,g 4') .
-[
3 F 1 i b 8
+
r
+
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l i f i l 150 TON CHILLER, REF. 2.D. CASE 1 APPENDIX 6.a Calc. No. MC6429 Page 7'/of[ ea. o yg u., g i Ototal 2.47E+06 g g g 4') Tout 118.36 BASED ON CLEAN COEFFICIENT? NO : Tin 110 112.7267 114.9781 116.8339 . Tsat 125.35 125.35 125.35 125.35 . gpm 600 600 600 600 l Ap 765.3 765.3 765.3 765.3 , spvol 0.016155 0.016162 0.016168 0.016173 1 visc 1.295989 1.243405 1.2016 1.168198 ' G 2238138 2237118 2236277 2235585 D 0.0442 0.0442 0.0442 0.0442 Re 76332.2 79524.09 82259.87 84585.66 ; Dol 0.003205 0.003205 0.003205 0.003205 j 0.00285 0.002827 0.002808 0.002792 Cp 0.9929 0.992436 0.992054 0.991738 .i K 0.368945 0.370307 0.371432 0.372359 Pr 3.487749 3.332371 3.209344 3.111375 ' MUw 1.026443 1.026443 1.026443 1.026443 MUratio 0.792015 0.82551 0.85423 0.878655 f h 2665.254 2738.375 2800.238 2852.27 Uc 193.5859 195.3323 196.7617 197.9313 U 75.5877 75.8525 76.0671 76.24126 i , Cmin 295781.1 295508.3 295283.3 295098 f NTUp 0.195575 0.196441 0.197147 0.197722 EFF. 0.177638 0.17835 0.17893 0.179402 ' Op 806519.1 665295.4 547999.3 450850.6 , deltaT 2.726743 2.251359 1.855842 1.5278 V L I Y i l
)
. .~
e i 150 TON CHILLER, REF. 2.D. CASE 6A APPENDIX 6.b Calc.No MC6429 Page 75or K S'l' S Yff f/-I-9] Ototal Tout 2.31 E+ 06 61.02 g g.g i BASED ON CLEAN COEFFICIENT? NO Tin 53.33 55.78336 57.84421 59.57236 Tsat 68.3 68.3 68.3 68.3 gpm 600 600 600 600 { Ap 765.3 765.3 765.3 765.3 ,. spvol 0.01602 0.01602 0.01602 0.01602 visc 3.065228 2.953096 2.86208 2.787924 ! G 2256999 2256999 2256999 2256999 i D 0.0442 0.0442 0.0442 0.0442 Re 32545.48 33781.27 34855.53 35782.66 Dol 0.003205 0.003205 0.003205 0.003205 j j 0.00338 0.003355 0.003334 0.003316 f Cp 1.002534 1.002117 1 001766 1.001473 l i K 0.340638 0.341864 0.342893 0.343756 Pr 9.021285 8.656511 8.361602 8.122118 , MUw 2.441761 2.441761 2.441761 2.441761 Muratio 0.7966 0.826848 0.853142 0.875835 ! h 1709.31 1752.344 1789.318 1820.915 [ Uc 163.0525 164.8326 166.3229 167.E689 l U 70.43744 70.76759 71.04089 71.26723 l Cmin 301167.7 301042.4 300937.2 300848.9 ! NTUp 0.178989 0.179903 0.180661 0.18129 j 0.163885 0.164649 0.165282 0.165806 EFF. Op 738872.8 620403.1 520064.7 435357.9 ; de!!aT 2.45336 2.060849 1.72815 1.447098 l i a I h
?
f 1 i a
o . _ . . . , l i
~i 150 TON CHILLER, MAX. TRANSIENT APPENDIX 6.c Calc. No. MC6429 Page 75of,$I ReJ.O fggy.,.13 Ototal 3.32E+06 4 l Tout 124.71 BASED ON CLEAN COEFFICIENT? NO f
Tin 6C 95.29856 111.7571 120.4418 Tsat 128.5 128.5 128.5 128.5 gpm 120 120 120 120 Ap 765.3 765.3 765.3 765.3 spvol 0.016044 0.016115 0.01616 0.016183 . visc 2.415935 1.620277 1.261855 1.105898 G 450716.1 448730.2 447496.2 446847.8 0 0.0442 0.0442 0.0442 0.0442 Re 8245.939 12241.04 15674.8 17859.4 f Dol 0.003205 0.003205 0.003205 0.003205 J 0.00407 0.00411 0.003911 0.003811 ; Cp 0.99997 0.995399 0.992601 0.991125 l K 0.348466 0.361602 0.369823 0.374161 Pr 6.932166 4.460218 3.38681 2.929443 MUw 0.978484 0.978484 0.978484 0.978484 Muratio 0.405013 0.603899 0.775433 0.884787 h 444.5419 (G1.2646 743.4094 810.2969 Uc 72.43109 93.12026 103.765 109.5858 U 45.72426 53.18356 56.49348 58.17582 l Cmin 59982.51 59451.2 59121.06 58947.59 , NTUp 0.583383 0.684618 0.731287 0.75528 EFF. 0.441993 0.495717 0.518711 0.530121 , Op 1577454 978479.4 513450.3 251813.1 ' dettaT 26.29856 16.45853 8.684728 4.271813 i b i I a i [ i i
i 150 TON CHILLER,100 tons & 120 gpm APPENDIX 6.d Cale.No MC6429 Page77ofI N'A Yff Il-1-9.3 l Ototat 1.47E +06 g ; Tout 64.26 BASED ON CLEAN COEFFICIENT? YES l Tin 39.9 53.12924 60.03349 63.05219 Tsat 65.0 65.0 65.0 65.0 gpm 120 120 120 120 ! Ap 765.3 765.3 765.3 765.3 i spvol 0.01602 0.01602 0.01602 0.016028 visc 3.758918 3.074591 2.768463 2.64438 , G 451399.7 451399.7 451397.2 451167.7 + D 0.0442 0.0442 0.0442 0.0442 ! Re 5307.876 6489.276 7206.798 7541.128 Dol 0.003205 0.003205 0.003205 0.003205 j 0.004004 0.004071 0.00408 0.00408 l Cp 1.004817 1.002568 1.001394 1.000881 K 0.33393 0.340538 0.343987 0.345495 Pr 11.31082 9.051812 8.05939 7.660642 MUw 2.567284 2.567284 2.567284 2.567284 ,{ Muratio 0.682985 0.835 0.927332 0.970845 i h 341.6444 413.6477 454.0231 472.0811 i Uc 59.06828 68.58358 73.58532 75.75028 l U 40.0103 44.16035 46.18155 47.02503 ! Cmin 60370.72 60235.6 60164.74 60103.33 j < NTUp 0.748789 0.871362 0.936011 0.964534 EFF. 0.527061 0.581619 0.607811 0.618839 i Op 798658.5 415882.1 181619 72447.4 { dettaT 13.22924 6.904258 3.018695 1.205381 l i f I i t f f i I i
AHU TRANSIENT, Sl w/ LOOP APPENDIX 7.a CALC. NO. MC-6429 Page 78 OF ($ N' S- Of /p4-13 -} CHILL WATER TEMP. = l 48 l TRAIN A l TRAIN B l TRAIN C S DES. INIT. -AHU COEFFICIENT-- h i TEMP TEMP -AHU LOAD, TONS-l ELECT PENET ROOMS 104 75 5057 4441 6319 ; 11.38 9.99 14.22 CCW/ CHILL WTR RMS 115 75 2728 2565 2960 l 6.14 5.77 6.66 l [ ESF PUMP ROOMS 104 75 20682 20326 20754 46.53 45.73 46.70 l ESF VALVE ROOMS 104 75 516 516 516 - 1.16 1.16 1.16 ; SFP PUMP ROOMS 120 120 0 0 0.00 0.00 ; RAD WASTE CONT RM 78 78 0 0 0.00 0.00 RAD. MONITIOR RM 104 75 1729 1729 3.89 3.89 RX MAKEUP PUMP RM 104 104 0 0 t 0.00 0.00 , CVCS VALVE RM M033 104 104 260 260 1.21 1.21 BORIC ACID PUMP RM 104 104 0 0 0.00 0.00 CVCS VALVE RM M226 104 104 239 239 1.12 1.12 CVCS VALVE RM M044 104 104 254 1.19 SUB-TOTAL 70.32 64.99 74.93 e CHILLED WATER PUMP 10.60 10.60 10.60 l s TOTAL 80.92 75.59 85.53 ! I l l l i
l APPENDIX 7.b Calc. No. MG-6429 Page'7T of T ; Train A Flow Dia9 tam k* ;
\ff n-t-(J '
%f5 tH-op '
pipe flow vel, length time wt/ft total water wt 10 gpm fps ft. sec. Ib/ft Ibs Ibs f 900 5.77 6 1.0 28.55 171.3 130 ; 1 7.981 26 3.4 10.79 280.5 143 l 2 4.026 300 7.56 3 4.026 300 7.56 19 2.5 10.79 205.0 105 t 6.66 31 4.7 18.97 588.1 388 4 6.065 l 600 l 6.065 600 6.66 9 1.4 its.97 170.7 113 ; 5 6 7.981 900 5.77 22 3.8 28.55 628.1 477 7 6 065 694 7.71 33 4.3 18.97 626.0 413 8 0.957 10 4.46 86 19.3 2.17 186.6 27 9 4.46 86 19.3 2.17 186.6 27 i 0.957 l 10 l 10 6.065 684 7.60 126 16.6 18.97 2390.2' 1577 11 4.026 148 3.73 3 0.8 10.79 32.4 17 g 12 4.026 148 3.73 61 16.4 10.79 658.2 337 i 13 4.026 148 3.73 59 15.8 10.79 636.6 325 14 4.026 0 0.00 2 10.79 21.6 15 4.026 148 3.73 3 0.8 10.79 32.4 17 16 6.065 536 5.95 15 2.5 18.97 284.6 188 l l 17 6.065 536 5.95 8 1.3 18.97 151.8 100 L 18 300 ton 600 4.78 56 11.7 0.0 979 19 EAB COIL 536 6.37 43.3 6.8 0.0 507 l 20 CR CO!L 148 3.39 49.0 14.4 0.0 298 l 21 150 ton 300 5.80 56 9.7 0.0 403 ! l s 22 6.065 536 5.95 8 1.3 18.97 151.8 100 I 23 6.065 0 0.00 2 18.97 37.9 24 6.065 536 5.95 13 2.2 18.97 246.6 163 i 25 6 026 684 7.69 109 14.2 18.97 2067.7 1347 26 6.026 694 7.81 40 5.1 18.97 758.8 494 i 27 4.026 206 5.19 13 2.5 10.79 140.3 72 I 28 1.939 42 4.56 33 7.2 5.02 165.7 42 i 29 42 l 4.56 33 7.2 5.02 165.7 42 l l 1.939 l 30 4.026 1 04 4.13 69 16.7 10.79 744.5 3 81 j 31 4.026 84 2.12 74 35.0 10.79 798.5 408 I 32 0.742 3 2.23 109 49.0 1.47 160.2 20 ; 109 49.0 1.47 160.2 20 l, 1 33 0.742 l 3l 2.23 34 3.068 22 0.95 63 66.0 7.58 477.5 202 l . 35 1.939 0 0.00 39 5.02 [ 36 1.939 l 0l 0.00 50 5.02 37 1.5 22 3.99 216 54.1 3.63 784.1 165 ] 38 1.5 l 22 l 3.99 216 54.1 3.63 784.1 . 165 .j 77'
- 39 1.939 22 2.39 60 25.1 5.02 301.2 4 40 4.026 84 2.12 63 29.8 10.79 679.8 348 I 41 4.026 1 61 4,06 72 17.7 10.79 776.9 397 ;
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Train A Flow Diagram APPENDIX 7.b Cale. No. MC-6429 Page 70 of[ Cu o. vif a+v time towt/ft n-t-%total water wt pipe flow vel. length fps ft. sec. Ib/ft lbs Ibs ID gpm 2.69 20 7.4 7.58 1 51.6 64 42 3.068 62 2.69 19 7.1 7.58 144.0 61 43 3.068 l 62 l 3.34 104 31.1 7.58 788.3 333 44 3.068 77 16 2,90 123 42.3 3.63 446.5 94 45 1.5 2.90 122 42.0 3.63 442.9 93 46 1.5l 16 l 1.939 61 6.63 71 10.7 5.02 356.4 91 47 21 9.37 49 5.2 2.17 106.3 15 48 0.957 9.37 52 5.6 2.17 112.8 16 49 0.957 l 21 l 40 4.35 35 8.1 5.02 175.7 45 50 1.939 40 0.88 B4 95.1 0.0 529 51 ESF AHU 52 0.0 4.35 34 7.8 5.02 170.7 44 53 1.939 l 40 l 1.939 61 6.63 72 10.9 5.02 361.4 92 54 55 3 D68 77 3.34 106 31.7 7.58 803.5 340 4.026 4.06 44 10.8 10.79 474.8 243 56 161 57 4 026 164 4.13 100 24.2 10.79 1079.0 552 58 4.026 206 5.19 37 7.1 10.79 399.2 204 59 7.981 900 5.77 8 1.4 28.55 228.4 173 TOTAL 22894 14004 Note: The mass of copper tubing in the chiller evaporators, copper tubing in the air handling units, and water ; in all air handling units except the EAB. Control Room, and ESF nump room, have been negtected. Thus l the heat capacity calculated is conservative. i i Item numbers correspond to Ref. 5.A Nodes, except ; item 31 corresponds to Ref. 5.A node 41 A. , Flow rates have been adjusted from Ref. 5.A values to reflect decreased flow rate through ESF pump room cooler and stopping flow rate through the Radwaste Control Room. Flow rates to the other coolers were increased roughly 5*4. This is based on rough estimates of the effect of the other flow reductions. j l As noted in Ref.1.A, the actual flow to the remaining coolers is not known to a high degree of accuracy and is not entical to the coolers performance. 4 e M v y., , -. - -,-., m.-. . , -7 v-~ ,-- - ... n .-
i l
-i 121 tons & 240 gpm APPENDlX 8.a Calc. No. MC-6429 PagehofM ecs.1L gjg u.o .
Ototal Tout 1.77E + 06 54.8 g0W ! BASED ON CLEAN COEFFICIENT 7 'YES . Tin 40.2 47.83196 51.97155 53.95105 ! Tsat 55.5 55.5 55.5 55.5 gpm 240 240 240 240 , Ap 1386.6 1386.6 1386.6 1386.6 i spvol 0.01602 0.01602 0.01602 0.01602 visc 3.741827 3.332225 3.129139 3.036447 i G 294299.8 294299.8 294299.8 294299.8 D 0.051 0.051 0.051 0.051 Re 4011.22 4504.284 4796.62 4943.044 Dol 0.003701 0.003701 0.003701 0.003701 j 0.003774 0.003896 0.003948 0.003969 Cp 1.004766 1.003469 1.002765 1.002428 : K 0.33408 0.337892 0.33996 0.340949 Pr 11.25378 9.89601 9.229886 8.927505 MUw 2.965835 2.965835 2.965835 2.965835 Muratio 0.792617 0.890046 0.947812 0.976745 ' h 215.1227 245.5798 262.7925 271.2019 Uc 60.14922 67.49885 71.54308 73.49111 , U 43.09171 46.73756 48.64146 49.53416 -
'Cmin 120735.3 120579.4 120494.8 120454.4 ;
NTUp 0.690791 0.776201 0.823285 0.845986 i EFF. 0.539849 0.561013 0.570866 y 0.498821 Op 921446.6 499149.1 238520.6 106510.7 , deltaT 7.631957 4.139588 1.979509 0.884241 I , .I 1
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1 i 100 tons & 240 gpm APPENDIX 8.b Calc. No. MC-6429 Page 82d N Red 2- if{ ig-q-1,3 Ototal Tout 1.50E+06
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53.1 j BASED ON CLEAN COEFFICIENT? YES ! 1 Tin 40.7 47.23581 50.71302 52.37331 i Tsat 53.7 53.7 53.7 53.7 l gpm 240 240 240 240 .j Ap 1386.6 1386.6 1386.6 1386.6 j spvo! 0.01602 0.01602 0.01602 0.01602 { viso 3.713514 3.362538 3.189536 3.1101 ! G 294299.8 294299.8 294299.8 294299.8 ; D 0.051 0.051 0.0 51 0.051 .: Re 4041.802 4463.679 4705.791 4825.984 , Dol 0.003701 0.003701 0.003701 0.003701 i j 0.003783 0.003888 0.003933 0.003952 ; Cp 1.004681 1.00357 1.002979 1.002697 , K 0.33433 0.337594 0.339331 0.34016 i Pr 11.15934 9.995851 9.427478 9.167691 I MUw 3.048049 3.048049 3.048049 3.048049 , Muratio 0.820799 0.906473 0.95564 0.980049 ! h 217.9014 244.0744 258.4941 265.5042 f Uc 60.83026 67.14145 70.54037 72.17322 .i U 43.44013 46.56593 48.17587 48.93193 I Cmin 120725.1 120591.6 120520.5 120486.6 l NTUp 0.698672 0.772014 0.811573 0.830593 ! EFF. 0.502755 0.537918 0.555841 0.564209 ! Op 789036.5 419321.6 200098.9 90188.27 > deltaT 6.535812 3.477205 1.660289 0.748533 l 1 l I l, i 8 f
i I 100 tons & 250 gpm APPEND!X 8.c Calc. No. MC-6429 Page b of f - ACV 2. tt.t 93 Ototal 1.50E +06
% h-\ 46 ,
Tout 53.2 j f BASED ON CLEAN COEFFICIENT 7 YES Tin 41.2 47.54142 50.86849 52.44515 Tsat 53.7 53.7 53.7 53.7 i gprn 250 250 250 250 Ap 1386.6 1386.6 1386.6 1386.6 spvol 0.01602 0.01602 0.01602 0.01602 [ visc 3.685416 3.346964- 3.182012 3.106707 G 306562.3 306562.3 306562 3 306562.3 D 0.051 0.051 0.051 0.051 f Re 4242.31 4671.301 4913.456 5032.556 Dol 0.003701 0.003701 0.003701 0.003701 J 0.003838 0.003927 0.003965 0.003981 > Cp 1.004596 1.003518 1.002952 1.002684 l K 0.334579 0.337747 0.339409 0.340196 Pr 11.0657 9.944542 9.402839 9.156614 MUw 3.048049 3.048049 3.048049 3.048049 e MUratio 0.827057 0.910691 0.9579 0.981119 5 h 231.7584 257.8533 272.0155 278.6136 f Uc 64.19478 70.39048 73.67862 75.24571 U 45.12923 48.10591 49.61928 50.32511 { Cmin 125744.7 125609.7 125538.9 125505.4 ; NTUp 0.707883 0.777037 0.813794 0.831325 EFF. 0.507314 0.540234 0.556826 0.564528 Op 797400 417912.6 197931.8 88907.64 l dettaT 6.341423 3.327072 1.576657 0.708397 l l v P a I l m _ _ _ _ _ . . _ _ __ _
t v 1 100 tons & 200 gpm APPENDIX 8.d Cale. No. MC-6429 Page 8Yof N f feb R Qgyg-9] t Ototal Tout 1.50E+06 52.9 hM M ' BASED ON CLEAN COEFFICIENT? YES Tin 38 45.37044 49.67547 51.86069 : Tsat 53.7 53.7 53.7 53.7 l gpm 200 200 200 200 f Ap 1386.6 1386.6 1386.6 1386.6 '! spvol 0.01602 0.01602 0.01602 0.01602 i visc 3.868988 3.459182 3.240204 3.134412 _ i G 245249.8 245249.8 245249.8 245249.8 D 0.051 0.051 0.051 0.051 Re 3232.82 3615.809 3860.171 3990.458 Dol 0,003701 0.003701 0.003701 0.003701 J 0.00344 0.003633 0.003726 0.003768 f Cp 1.00514 1.003887 1.003155 1.002784 ! K 0.332981 0.336663 0.338813 0.339904 Pr' 11.67897 10.31486 9.593577 9.247122 l MUw 3.048049 3.048049 3.048049 3.048049 Muratio 0.7t!7815 0.881147 0.940696 0.972447. I h 159.3462 185.4277 201.2838 209.5143 ! i Uc 46.00977 52.73477 56.72515 58.76808 ! U 35.31633 39.14841 41.30548 42.3782 [ t Cmin 100650.2 100524.7 100451.5 100414.3 NTUp 0.63385 0.727403 0.783016 0.811516 l EFF. 0.469455 0.516838 0.542974 0.555816 l Op 741836.3 432762.3 219508 102655.4 dettaT { 4 7.37044 4.305033 2.185215 1.022319 4 1 I i i l 1 l 1 l I 4
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