TSU (E, F & G) Engineering Data - Baltimore Aircoil Company
TSU (E, F & G) Engineering DataNOMINAL 5’ WIDE UNITS:MODELS TSU-125E TO TSU-235E AND TSU-145F TO TSU-270FRefrigeration ConnectionAir InletSee Note (4)Air Outlet Overflow4'-9"7'-7" Water outDrain Water in 6"A18"LW/2WLBS of ”5’-3 1/8”10’-1”4.5”320102753”5’-3 1/8”12’-1”4.5”2,960380123253”5’-3 1/8”14’-1”4.5”33,400440133554”5’-3 1/8”16’-0”5”41,90033,840490154104”5’-3 ��-3 5’-3 553”5’-3 104”5’-3 4”5’-3 1/8”18’-0”5”E SeriesF SeriesNOTES:2. Pounds of ice capacity is based on R-717. For other refrigerants,consult your BAC Representative.5. Refrigerant charge listed is operating charge for gravity floodedsystem at 15 F (-9 C). For other feed systems, consult your BACRepresentative.3. Dimensions showing location of connections are approximate andshould not be used for prefabrication of connecting piping.6. ICE CHILLER Thermal Storage Units should be continuouslysupported on a flat level surface.1. All dimensions are in feet and inches. Weights are in pounds.4. Dimension is installed height. Coils are capped for shipping andstorage. Add 3 inches for shipping height.G22Q U E S T I O N S ? C A L L 4 1 0 . 7 9 9 . 6 2 0 0 O R V I S I T W W W. B A LT I M O R E A I R C O I L . C O M
Refrigeration ConnectionAir InletAir Outlet Overflow Water Out4'-9"See Note (4)7'-7"NOMINAL 8’ AND 10’ WIDE UNITS:MODELS TSU-190E TO TSU-505E AND TSU-220F TO TSU-580F Water In DrainA6"*LW/2W*18" On TSU-190E-365E; TSU-220F-420F*16" On TSU-290E-505E; TSU-330F-580FLBS of 20154104”7’-10 034,000510174654”7’-10 034,700600195154”7’-10 0035,400700226004”7’-10 0036,100800246506”7’-10 035,040640215706”9’-9 0035,920760236256”9’-9 0036,800860267056”9’-9 0037,080980297906”9’-9 0038,5501090328706”9’-9 033,29060164354”7’-10 033,99070195154”7’-10 0034,68090215704”7’-10 0035,380100246504”7’-10 0036,070110267056”7’-10 0035,02095236256”9’-9 1035,890110267056”9’-9 0036,770130297906”9’-9 0037,640140328706”9’-9 0038,520160359506”9’-9 /OutWLAE SeriesF SeriesNOTE: See notes on previous page.PRODUCT & APPLICATION HANDBOOK VOLUME VG23
TSU (E, F & G) Engineering DataNOMINAL 10’ WIDE UNITS (CONTINUED):MODELS TSU-590E TO TSU-1080E AND TSU-675F TO TSU-1230FRefrigeration ConnectionAir InletSee Note (4)Air Outlet OverflowWater Out4'-9"7'-7" Water In DrainL6"A16"W/2WLBS of 401,320421,1406”9’-9 ,500312,0301,540471,2756”9’-9 ,400513,7901,760531,4408”9’-9 ,200515,5401,990581,5758”9’-9 6,200518,1802,330671,8208”9’-9 00190461,2506”9’-9 n/OutWLAE SeriesF ,980230521,4106”9’-9 ,700513,700260591,6008”9’-9 1,300515,480290651,7658”9’-9 7,500518,100340742,0108”9’-9 3/8”41’-9”7”NOTES:2. Pounds of ice capacity is based on R-717. For other refrigerants,consult your BAC Representative.5. Refrigerant charge listed is operating charge for gravity floodedsystem at 15 F (-9 C). For other feed systems, consult your BACRepresentative.3. Dimensions showing location of connections are approximate andshould not be used for prefabrication of connecting piping.6. ICE CHILLER Thermal Storage Units should be continuouslysupported on a flat level surface.1. All dimensions are in feet and inches. Weights are in pounds.4. Dimension is installed height. Coils are capped for shipping andstorage. Add 3 inches for shipping height.G24Q U E S T I O N S ? C A L L 4 1 0 . 7 9 9 . 6 2 0 0 O R V I S I T W W W. B A LT I M O R E A I R C O I L . C O M
NOMINAL 12’ WIDE UNITS:MODELS TSU-840F TO TSU-1520F AND TSU-940G TO TSU-1710GRefrigeration ConnectionAir InletSee Note (4)Air Outlet7’-11 1/2" Overflow5'-2" Water Out Water In DrainL6"A22"W/2WLBS of rge(lbs)[5]WaterConn.In/OutWLAF SeriesG 4901002,7108”11’-9”41’-9”7”NOTES:2. Pounds of Ice Capacity is based on R-717. For other refrigerants,consult your BAC Representative.5. Refrigerant charge listed is operating charge for gravity floodedsystem at 15 F (-9 C). For other feed systems, consult your BACRepresentative.3. Dimensions showing location of connections are approximate andshould not be used for prefabrication of connecting piping.6. ICE CHILLER Thermal Storage Units should be continuouslysupported on a flat level surface.1. All dimensions are in feet and inches. Weights are in pounds.4. Dimension is installed height. Coils are capped for shipping andstorage. Add 3 inches for shipping height.PRODUCT & APPLICATION HANDBOOK VOLUME VG25
Engineering Considerations –Refrigeration››Suitable For: Industrial Refrigeration,Process Cooling, and Batch CoolingFor industrial applications, stored cooling using ICE CHILLER Thermal Storage Units provides many opportunities for savings: smallercompressors and likewise smaller system components and electricalequipment; shifting or leveling of energy usage peaks; and efficientuse of equipment. Also, since ice storage systems are sized to operateprimarily at full capacity, compressor wear from capacity adjustmentis minimized, providing maintenance savings over the life of thecompressor. Stored cooling from ICE CHILLER Thermal Storage Unitssupplies consistently low temperature water, making it appropriate fordaily and/or infrequent cooling loads in many industrial processes suchas: Bakeries Laboratories Dairies Food Product Cooling Breweries, Wineries, Distilleries Bottling Process Chemical/Plastics Manufacturers Vegetable/Fruit CoolingRefrigerationSystemProcessLoadAirBlowerIce WaterPump ICE CHILLERThermal Storage UnitFigure 10ProcessLoad PRINCIPLE OF OPERATIONThe basic ice storage system includes an ICE CHILLER ThermalStorage Unit, a refrigeration system, and ice water pump as shown inFigure 10.When no cooling load exists, the refrigeration system operates tobuild ice on the outside surface of the coil. This refrigeration effectis provided by feeding refrigerant directly into the coil. To increasethe heat transfer during the ice build cycle the water is agitated byair bubbles from a low pressure air distribution system beneath thecoil. When the ice has reached design thickness, BAC’s exclusiveICE-LOGIC Ice Thickness Controller sends a signal to turn off therefrigeration system.When chilled water is required for cooling, the ice water pump isstarted, and the meltout cycle begins. Warm water returning from theload circulates through the ICE CHILLER Thermal Storage Unit andis cooled by direct contact with the melting ice. During this cycle,the tank water is agitated to provide more uniform ice melting and aconstant supply water temperature of 34 F (1 C) to 36 F (2 C).For a closed chilled water loop, see Figure 11. With this system,warm return water from the load is pumped through a heat exchangerand cooled by the ice water circuit from the ICE CHILLER ThermalStorage Unit.G26Q U E S T I O N S ? C A L L 4 1 0 . 7 9 9 . 6 2 0 0 O R V I S I T W W W. B A LT I M O R E A I R C O I L . C O MIce WaterPumpFigure 11HeatExchangerChilled WaterPump
››Energy Efficient DesignThe ICE CHILLER Thermal Storage Unit coils are designed for efficient energy use in building ice and constant leaving watertemperatures during the meltout cycle.Compared to traditional ice builders used in the past for industrial refrigeration, the ICE CHILLER Thermal Storage Unitdesign with its smaller diameter coil circuits and thinner ice (Figure 12) results in more evaporator surface per ton-hour oflatent storage. Ice builds to a thin 2.0 inches, which results in more than a 16% gain in refrigeration system efficiency bypermitting compressor operation at higher suction pressures.OthersBAC1.66" O.D. Coil1.05" O.D. Coil2.0"2.5"Coil Surface: 3.0 FT2/TON-HOURIce Surface: 14.5 FT2/TON-HOURFigure 122.8 FT2/ton-hour11.1 FT2/ton-hourThe ICE CHILLER Thermal Storage Unit is specifically designed to provide consistent 34- 36 F supply water temperaturesthroughout the melt cycle. Two keys to maintaining this consistently low temperature are an extensive ice surface area anddirect contact of the water to be cooled with the ice. As shown in Figure 12, the unique BAC coil design provides over 30%more ice surface than traditional designs. This provides a greater surface area for the warm return water to come into directcontact, making consistent cold temperatures available throughout the entire melt cycle.The ICE CHILLER Thermal Storage Unit is designed for efficient operation with either of two liquid refrigerant feed systems:gravity flooded with surge drum or pumped recirculation. With either arrangement, liquid refrigerant is supplied to the coilsat a rate several times greater than that required to satisfy the load. This excess flow rate thoroughly wets the entire internalsurface of the coil, assuring high heat transfer coefficients throughout to efficiently utilize the entire coil surface for icebuilding.PRODUCT & APPLICATION HANDBOOK VOLUME VG27
Engineering Considerations –Refrigeration››System Design FlexibilityThe system design involving an ICE CHILLER Thermal Storage Unit can range from full storage to partial storage of thecooling load requirements. Full Storage – With full storage, the ICE CHILLER Thermal Storage Unit generates and stores ice to handle the entirecooling load. The refrigeration system operates to build the ice only during no-load periods when utility rates are usuallylowest. This design offers the maximum energy cost savings, but requires the largest ice storage capacity and refrigerationsystem. Partial Storage – A partial storage system builds ice during no-load periods as with the full storage system. However, therefrigeration system continues to operate during the cooling load period. The compressor operation supplements the storedcooling capacity of the ICE CHILLER Thermal Storage Unit to satisfy the cooling requirements. Since a portion of thecooling requirement is supplied by the refrigeration system, a partial storage system will require less storage capacity. Parallel Chilled Water Evaporator – The most common type of partial ice storage is the parallel evaporator system. Duringthe melt cycle, cooling is provided by the refrigeration system to a separate evaporator for direct water chilling. By using aseparate evaporator, the refrigeration system gains system efficiency from operation at higher suction pressures.The refrigeration system will operate continuously during full design load. At less than full load the compressor operatesonly as needed to supplement the ICE CHILLER Thermal Storage Unit. When the load is less than 50% of design, thissystem can operate in the full storage mode. Systems which often operate at part load can benefit most from a partialsystem with equipment sizes typically over 50% smaller than required for full storage. For additional information on ICECHILLER Thermal Storage Units and their system design options consult your BAC Representative. System Load – The system load is the amount of cooling capacity that must be generated and stored, expressed in ton-hours or Btu. (1 ton-hour 12,000 Btu 83.3 pounds of ice). This load is equal to the area under the typical system loadprofile curve (Figure 13).G28Q U E S T I O N S ? C A L L 4 1 0 . 7 9 9 . 6 2 0 0 O R V I S I T W W W. B A LT I M O R E A I R C O I L . C O M
Full Storage1.2.3.From the system load profile (Figure 13) establish the requiredsystem cooling capacity in ton-hours. This is the ton-hours ofstorage required.Determine the build time, which is the number of hours with noload that is available for ice building. If less than ten (10) hours,consult your BAC Representative.For a gravity flooded ammonia feed system, continue the selectionwith the gravity flooded procedure on pages G30 and G31. For apump recirculated ammonia feed system, continue the selectionwith the pump recirculated procedure on pages G31 and G32.Cooling Load Tons››Thermal Storage Unit SelectionArea Cooling CapacityIn Ton-HoursM3AM6AM9AMN3PM6PM9PMM6PM9PMMTime, HoursFigure 131.2.3.From the system load profile (Figure 13), establish the requiredsystem cooling capacity in ton-hours and the number of hours thiscooling is needed.Determine the cooling capacity in tons of the compressor operatingwith the parallel evaporator (Figure 14) during the cooling loadhours established in Step 1.Multiply the cooling capacity of the compressor operating withparallel evaporator found in Step 2 times the number of coolingload hours found in Step 1. This gives the capacity in ton-hoursthat will be handled by direct refrigeration during the coolingperiod.4.Subtract the direct cooling ton-hours found in Step 3 from thetotal system cooling capacity found in Step 1. This is the storagecapacity in ton-hours that are required in ice storage.5.Determine the build time, which is the number of hours withthe compressor dedicated to ice building. If less than ten hours,consult your local BAC Representative.6.For gravity flooded ammonia feed system, continue the selectionwith the gravity procedure on pages G30 and G31. For a pumprecirculated ammonia feed system, continue the selection with thepump recirculated procedure on pages G31 and G32.Cooling Load Tons Parallel Chilled Water Evaporator Partial StorageLoad Handledby Stored IceLoad Handledby ParallelEvaporatorM3AM 6AM9AMN3PMTime, HoursFigure 14PRODUCT & APPLICATION HANDBOOK VOLUME VG29
Unit Selection - Ammonia SELECTION PROCEDURE – GRAVITY FLOODED1.Enter Table 2 and read down the base ton-hours columnto the capacity which meets or exceeds the ton-hours ofstorage required. Select either an E, F, or G series unit.(Units are grouped by tank width in Table 2. Refer to pagesG22 thru G25 for unit dimensions.)2.Read the selected unit from the model number column onthe left.3.Calculate the Storage Factor for the selected unit.5.7.16,700 lbs ice required storage capacity83.3 lbs ice per Ton-Hour 201 Ton-HoursEnter the base ton-hours column of Table 2 and find 211ton-hours, which is the smallest value that meets or exceedsthe 201 ton-hours of storage required.2.Read to the left to find the selected model number, in thiscase a TSU-230E.Using the Storage Factor from Step 3 and the availablebuild time, enter Table 3 to find the design evaporatortemperature.3.Calculate the Storage Factor.Determine the design compressor capacity in tons.4.Using the Storage Factor of 1.05 from Step 3 and the buildtime of 14 hours, enter Table 3 to find the design evaporatortemperature of 19.9 F.5.Calculate the design compressor capacity.Ton-Hours of Storage RequiredBuild Time (hrs)6.Given: 16,700 lbs ice required storage capacity, 14 hoursavailable build timeTo get ton-hours of storage required:1.Base Ton-HoursTon-Hours of Storage Required4. EXAMPLE: Gravity Flooded Ammonia Storage Factor211 Ton-Hours of Storage Required201 Ton-Hours of Storage Required Compressor TonsUsing the design conditions from Steps 4 and 5, select acompressor. (Note: The evaporator temperature must beadjusted for the system suction line losses to arrive at thecompressor saturated suction temperature.)201 Ton-Hours of Storage Required14 Hours of Build Time 1.05 14.4 Tons6.Based on the design evaporator conditions of 14.4 tons ata 19.9 F evaporator temperature (17.9 F saturated suctiontemperature, with 2.0 F estimated suction line losses),select an ammonia refrigerant compressor.7.Select a BAC Evaporative Condenser or Cooling Towerto match the compressor manufacturer’s heat rejectionrequirements.Once the compressor has been selected, use the compressormanufacturer’s heat rejection data to size a BAC EvaporativeCondenser or Cooling Tower.APPLICATION NOTES:1. To use the selection procedures, the ton-hours of storage capacityrequired and the available build time must first be known. Forguidance on estimating these values refer to the TSU selection onpage G29 or contact your local BAC Representative.2. The evaporator temperatures for each build time are “average”values. During the build cycle, the temperature will initially be about8 F (-13 C) above the “average” and gradually drop through the cycleto about 4 F (-15 C) below the “average” when full ice is reached.Throughout the cycle the refrigeration system should be allowed to runfully loaded. Reciprocating and rotary screw compressors are suitablefor this duty. If in doubt about the use of a particular compressor,review the application with the compressor manufacturer.G303. The capacities of all BAC ICE CHILLER Thermal Storage Units arebased on latent storage (ice) only. The temperature of the watersupplied from the storage tank for most system designs will be 34 (1 C) - 36 F (-2 C) throughout the latent storage discharge (melt)cycle. For specific system design requirements, contact your local BACRepresentative.4. For selections based on other refrigerants, contact your local BACRepresentative.5. These procedures assume that no system cooling load occurs whileice is being formed. For ICE CHILLER Thermal Storage Unit selectionsinvolving systems with continuous cooling loads consult your localBAC Representative.Q U E S T I O N S ? C A L L 4 1 0 . 7 9 9 . 6 2 0 0 O R V I S I T W W W. B A LT I M O R E A I R C O I L . C O M
Table 3. Design Evaporator Temperature ( F) forGravity Flooded Ammonia Feed[1]Table 2. Base Storage Capacity (ton-hours) For Gravity Flooded Ammonia Feed[1]TSUE-Series UnitsF-Series UnitsF-Series 1290FTSU-1520F7568941,0311,1691,375G-Series UnitsBaseTon-Hrs8511,0071,1631,3151,550Enter Table 4 and read down the base ton-hours columnto the capacity which meets or exceeds the ton-hours ofstorage required. Select either an E, F, or G Series unit.(Units are grouped by tank width in Table 4. Refer to pagesG22 thru G25 for unit dimensions.2.Read the selected unit from the model number column onthe left.3.Calculate the Storage Factor for the selected unit.Base Ton-HoursTon-Hours of Storage Required4.5.6.7. Compressor TonsUsing the design conditions from Steps 4 and 5, select acompressor. Note: The evaporator temperature must beadjusted for the system suction line losses to arrive at thecompressor saturated suction temperature.Once the compressor has been selected, use thecompressor manufacturer’s heat rejection data to size aBAC Evaporative Condenser or Cooling .422.11.3019.420.321.221.922.6NOTE:1. Interpolation between values is permitted, butextrapolation of values is not.1.Enter the base ton-hours column of Table 4 and find771 ton-hours, which is the smallest value that meets orexceeds the 700 ton-hours of storage required.2.Read to the left to find the selected model number, in thiscase a TSU-800F.3.Calculate the Storage Factor.4.Using the Storage Factor of 1.10 from Step 3 and thebuild time of 11 hours, enter Table 5 to find the designevaporator temperature of 17.7 F.771 Base Ton-Hour700 Ton-Hours of Storage Required5. 1.10Calculate the design compressor capacity.700 Ton-Hours of Storage Required11 Hours Build TimeDetermine the design compressor capacity in tons.Ton-Hours of Storage RequiredBuild Time (hrs)11GIVEN: 700 ton-hours required storage, 11 hours availablebuild time Storage FactorUsing the Storage Factor from Step 3 and the availablebuild time, enter Table 5 to find the design evaporatortemperature.10 EXAMPLE: Pump Recirculated Ammonia SELECTION PROCEDURE – PUMP RECIRCULATED1.Build Time (hrs)StorageFactor 63.6 Tons6.Based on the design evaporator conditions of 63.6 tonsat a 17.7 F evaporator temperature (15.7 F saturatedsuction temperature, with 2.0 F estimated suction linelosses), select an ammonia refrigerant compressor.7.Select a BAC Evaporative Condenser or Cooling Towerto match the compressor manufacturer’s heat rejectionrequirements.PRODUCT & APPLICATION HANDBOOK VOLUME VG31
Unit Selection - AmmoniaTable 4.Base Storage Capacity (ton-hours) For Pump Recirculated Ammonia Feed[1]E Series UnitsG32F-Series UnitsF-Series 0FTSU-1520FTable 5. Design Evaporator Temperature ( F) forPump Recirculated Ammonia Feed[1]Build Time 161,2631,4801.0014.315.717.118.119.1G-Series 21.622.323.09121,0761,2291,3781,593Q U E S T I O N S ? C A L L 4 1 0 . 7 9 9 . 6 2 0 0 O R V I S I T W W W. B A LT I M O R E A I R C O I L . C O MNOTE:1. Interpolation between values is permitted, butextrapolation of values is not.
MODELS TSU-125E TO TSU-235E AND TSU-145F TO TSU-270F: TSU (E, F & G) Engineering Data: Refrigeration Connection Air Outlet 18" W/2 W See Note (4) 7'-7" 4'-9" 6" L A Overflow Water out Water in: Drain Air Inlet: PRODUCT & APPLICATION HANDBOOK : VOLUME V: G23: NOTE: See notes on previous page. Model : Number LBS of Ice [2] Approx .
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Is the TSU-MSW Program accredited by the Council on Social Work Education (CSWE)? No. The Council on Social Work Education will be reviewing the TSU-MSW Program self-study to determine whether they will grant accreditation status to the TSU-MSW Program at their February 2022 meeting. All degrees conferred prior to August 15, 2021
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