I. Introduction and Arrangement

Transcription

1 Joseph Firrantello - Mechanical Option Primary Faculty Consultant: Freihaut Laboratory Facility, Eastern Pennsylvania Mechanical Assignment 3 Existing Conditions Report Executive Summary The purpose of this report to present a summary of the existing HVAC system conditions in the Laboratory Facility. This summary is intended as an examination of different aspects of the mechanical systems in order to better understand the systems purposes and method of operation. First, design objectives and requirements were looked at. These were broken down into three main issues: occupant comfort, maintaining clean room purity, and first cost minimalization. Energy suppliers and rates for the site were then established. Electricity is provided by PECO under their General Service (GS) tariff. Natural Gas is provided by PGW under an as-yet-undetermined interruptible (IT) rate. The main cost factor, as already stated, is first cost. The firm had decided that utility costs could be passed onto clients, so operational costs were not a large factor. There were no significant site factors that influenced the design. The summer outdoor design conditions meet those in ASHRAE Fundamentals at 93 F DBT and75 F WBT, while the winter outdoor design conditions are quite severe: 0 F compared to ASHRAE s 30 F. The indoor design conditions are not ASHRAE standard. The clean rooms are maintained at 68 F, non- clean labs at 72 F, and office spaces at 75 F. The resulting design heating and cooling loads are 3399 BTUH and 8066 BTUH (672 tons) respectively. The sequence of operations for the process chiller, process boiler (steam), and air side (AHUs, CAV and VAV systems) are examined and listed. Finally, the system was found to adequately meet the design requirements, at an HVAC construction cost of $45/sf for a high technology facility. However, there seems to be room for improvement in operational costs Page 1 of 27

2 Joseph Firrantello - Mechanical Option Primary Faculty Consultant: Freihaut Laboratory Facility, Eastern Pennsylvania Mechanical Assignment 3 Existing Conditions Report I. Introduction and Arrangement The purpose of this report to present a summary of the existing HVAC system conditions in the Laboratory Facility. This summary is intended as an examination of different aspects of the mechanical systems in order to better understand the systems purposes and method of operation. It is arranged as follows: I. Introduction and Arrangement II. Design Objectives and Requirements III. Energy Sources and Rates IV. Cost and Site Factors V. Indoor and Outdoor Design Conditions VI. Design Heating and Cooling Loads VII. Description of System Operation VIII. Critique of System Appendix A Schematic Diagrams of Chiller, Boiler, and Air Side Appendix B Schedules of Major Mechanical Equipment Page 2 of 27

3 Joseph Firrantello - Mechanical Option Primary Faculty Consultant: Freihaut Laboratory Facility, Eastern Pennsylvania Mechanical Assignment 3 Existing Conditions Report II. Design Objectives and Requirements The design of a laboratory facility needs to address all of the issues that deal with normal commercial spaces, plus some items unique to the laboratory building type. The design of the facility has three main thrusts: occupant comfort, maintaining clean laboratory conditions, and first cost. A. Occupant Comfort Occupant comfort is necessary to ensure the efficiency and productivity of employees. In this case, occupant comfort can be split into three subsections, being thermal comfort, indoor air quality, and safety. 1. Thermal Comfort The HVAC system needs to maintain the thermal comfort of the occupants. In this case, that means dealing with variable occupancy (and therefore variable loads) for spaces such as conference rooms and process rooms. It also means dealing with the substantial heat load that can be generated by laboratory equipment, as well as the large variation in outdoor air conditions that can occur at the building s location (see V. Indoor and Outdoor Design Conditions). 2. Indoor Air Quality The HVAC system needs to maintain indoor air quality. ASHRAE has performed numerous studies indicating that better indoor air quality directly affects occupant comfort and therefore occupant productivity. Along with occupant comfort, bad indoor air quality can begin to adversely affect occupant health. 3. Safety The HVAC system needs to help maintain the safety of the occupants. Since the space is a laboratory with potentially hazardous substances, additional ventilation may be required under the ANSI Lab Safety Standard. B. Clean Room Conditions Due to the biological and semiconductor work that is performed at the facility, clean rooms of class 100,000 and class 10,000 are required. 1 This prevents contamination of whatever product is being worked on in the facility. C. First Cost The firm occupying the facility had decided that first cost was a priority for the HVAC design, as they could pass their utility rates onto the fees they would charge their clients. 1 The class refers to the number of particles greater than or equal to 5 microns (micrometers) per cubic foot of air. (from Energy Efficiency in California Laboratory-Type Facilities, 1996) Page 3 of 27

4 Joseph Firrantello - Mechanical Option Primary Faculty Consultant: Freihaut Laboratory Facility, Eastern Pennsylvania Mechanical Assignment 3 Existing Conditions Report III. Energy Sources and Rates The facility has two utility services: electricity and natural gas. Electricity is provided by PECO under the GS (General Service Rider). The rate structure is outlined below. PECO Electricity Charges Fixed Distribution Service Charge for polyphase service $ Variable Distribution Service Charge 1st 80 hours use of billing demand $ per kwh * next 80 hours use of billing demand $ per kwh for additional use, except $ per kwh over both 400 hours use of billing demand and 2,000 kwh $ per kwh Competitive Transition Charge 1st 80 hours use of billing demand $ per kwh * next 80 hours use of billing demand $ per kwh for additional use, except $ per kwh over both 400 hours use of billing demand and 2,000 kwh $ per kwh Demand Charges Variable Distribution $ 0.85 per kw Competitive Transition $ 1.85 per kw * denotes the during October through May this block is eliminated Ratchet Clause: From October through May the billed demand shall not be less than 40% of the highest billing demand in the previous months of June through September Page 4 of 27

5 Joseph Firrantello - Mechanical Option Primary Faculty Consultant: Freihaut Laboratory Facility, Eastern Pennsylvania Mechanical Assignment 3 Existing Conditions Report Natural Gas is provided by PGW (Philadelphia Gas Works) under an interruptible rate tariff. PGW defines its interruptible rates in terms of contracting for the minimum amount of gas to be purchased per year. The rate structure is described below. Estimates for yearly gas use were not available, so an applicable tariff was not chosen. Minimum Dth/year PGW Interruptible Rates Other requirements $ per meter per month Distribution charge ($/Dth) IT-1: 75 n/a if IT-2 through IT-8 do not apply IT-2: 75 2,500 standby non-gas energy source IT-3: 150 5,000 standby non-gas energy source IT-4: 150 5,000 standby No. 4 oil IT-5: 150 5,000 standby No. 5 or 6 oil IT-6: ,000 standby non-gas energy source IT-7: ,000 standby non-gas energy source IT-8: 250 n/a cogeneration Dth = Dekatherm = 1,000,000 BTUs IV. Cost and Site Factors First cost was the primary driving force between design decisions (i.e. 15 packaged rooftop AHUs vs. a chiller plant). The firm is capital poor, and can pass on utility and operational costs to its customers. Site factors were not a large consideration for the mechanical design of the project. Although the south face of the facility is noticeably absent of glazing (thereby reducing solar gain), this was purely a coincidence. The rooms that were placed there (i.e. cell production suites) are designed to have no windows. Page 5 of 27

6 Joseph Firrantello - Mechanical Option Primary Faculty Consultant: Freihaut Laboratory Facility, Eastern Pennsylvania Mechanical Assignment 3 Existing Conditions Report V. Indoor and Outdoor Design Conditions The cooling load was calculated using outdoor design conditions of 93 F dry-bulb temperature and 75 F wet-bulb temperature, corresponding with ASHRAE 0.4% design conditions for the Philadelphia area. The heating load was calculated using a 0.0 F outdoor dry-bulb temperature, which is well below ASHRAE design conditions for the area, as you can see in Table 1. The indoor design conditions vary a bit from space to space, but some trends are noticeable, as one can see in Table 2. Table 1 - Outdoor Design Conditions Cooling (0.4%) DBT WBT Facility 93 F 75 F ASHRAE 93 F 75 F Heating (0.4%) DBT Wind Speed Facility 0 F n/a ASHRAE 30 F 19 mph The clean rooms all have a design space temperature of 68 F. The relative humidity requirements for those spaces are not specified, but this is because the supply air is cooled to the neighborhood of 47 to 49 F for those spaces, thereby taking care of dehumidification. The office spaces are set to be maintained at 75 F DBT and 50% RH, while the laboratory spaces that are not clean rooms are set at either 72 F and 50% RH or 68 F and 45% RH. AHU-15 seems to be a special case, with some storage and warehouse spaces having design temperatures in the 80s and up to 90 F. Table 2 - Indoor Design Conditions AHU # General Service DBT F RH 1 Clean Room Labs 68 N.L. 2 Clean Room Labs 68 N.L. 3 Clean Room Labs 68 N.L. 4 Clean Room Labs 68 N.L. 5 Clean Room Labs 68 N.L. 6 Clean Room Labs 68 N.L. 7 Clean Room Labs 68 N.L. 8 Clean Room Labs 68 N.L. 9 Clean Room Labs 68 N.L. 10 Office Space 75 50% 11 Labs (not clean room) 72 50% 12 Labs (not clean room) 72 50% 13 Labs (not clean room) 72 50% 14 Labs (not clean room) 68 45% 15 Labs, Storage, Corridors 72, 75, 80, 85, 90 50% N.L. = Not Listed Page 6 of 27

7 Joseph Firrantello - Mechanical Option Primary Faculty Consultant: Freihaut Laboratory Facility, Eastern Pennsylvania Mechanical Assignment 3 Existing Conditions Report VI. Design Heating and Cooling Loads The design cooling load, taken directly from the cooling coil loads on the 15 AHUs, amounts to 672 tons. Split up, that comes to 467 tons sensible load and 205 tons latent load. BTUH values can be found in Table 3. Table 3 - Design Cooling Load Sensible Latent Total Tons BTUH The heating load, once again taken directly from the design documents, amounts to about 3400 BTUH. The breakdown of the systems supplying the heating and their sources of energy can be found in Table 4. Table 4 - Design Heating Load System Source MBTUH AHUS (Preheat) Gas 6 Duct Heaters (CAV) Electric 3056 VAV boxes Electric 157 Unit Heaters Gas 180 Total 3399 Page 7 of 27

8 Joseph Firrantello - Mechanical Option Primary Faculty Consultant: Freihaut Laboratory Facility, Eastern Pennsylvania Mechanical Assignment 3 Existing Conditions Report VII. Description of System Operation The facility has three main HVAC systems that require control: the process chilled water system, the process steam boiler, and the air side conditioning and distribution. The design drawings are not complete control schematics, as the controls are subcontracted out. However, they provide enough information to get a feel as to how the systems work. A. The Process Chiller 1. General The chiller, a packaged rooftop air-cooled unit, is controlled by the integral chiller sequence control panel. The two chiller pumps are controlled by the Building Automation System (BAS), which is subcontracted to a controls contractor. 2. Sequence of Chiller Operations When the chiller is indexed on (by a call for chilled water from the process equipment), the chiller will signal the BAS to start P-CH-1, the first of the two parallel chiller pumps. (see Appendix A - Schematics for the chiller schematic) When the differential pressure switch (DPS) has proof of chilled water flow, the chiller is energized, and the packaged controls are to maintain a supply water set point of 55 F. This supply point is checked through the temperature monitors present on the supply side of the chiller. The DPS monitors the chilled water pumps. If P-CH-1 fails, the BAS shows an alarm condition and starts P-CH-2. So, while upon first glance the pumps look like they are parallel flow, they are in fact redundant. The differential pressure transmitter (DTS) operates to maintain a differential pressure determined during balancing by modulating the bypass valve. B. The Process Steam Boiler 1. General Boilers B-1 and B-2 are controlled by the boiler sequence control panel. Deaerator DA-1 is controlled by the deaerator control panel. The boiler feed water pumps are controlled through the deaerator control panel. The BAS monitors the steam pressure via the two pressure transmitters (PT) located in the steam headers. See Appendix A for the schematics. 2. Sequence of Boiler Operations When B-1 is on, the PT checks steam pressure. Upon a decrease in steam pressure (less than 125psig), the boiler begins operation. The boiler control panel modulates the gas supply to maintain steam pressure, as transmitted by PT. If these is a decrease in steam pressure below 120 psig for 5 minutes, the boiler controls start B-2 in the same manner as B-1. Upon sensing an increase in steam pressure, the boiler control panel de-energizes B Sequence of Deaerator Operations The boiler feedwater pumps (P-BF-1, P-BF-2, P-BF-3) are monitored by the deaerator controls. Upon failure of P-BF-1 or 2, the BAS shows and alarm condition, and starts P-BF-3. Page 8 of 27

9 Joseph Firrantello - Mechanical Option Primary Faculty Consultant: Freihaut Laboratory Facility, Eastern Pennsylvania Mechanical Assignment 3 Existing Conditions Report C. The Air Side Upon a decrease in deaerator water level, the control panel will modulate the make-up water valve (not shown) to maintain the set water level. Upon an increase in water level, the control panel will modulate the same valve to maintain water level. If there is an increase in water level for greater than 5 minutes, the BAS will indicate an alarm. 1. General The spaces are conditioned via 15 packaged rooftop AHUs. 14 serve CAV systems (generally laboratory space), and AHU-10 serves the office space through a VAV system. While the AHU systems have certain differences (see Appendix A), their basic sequence of operation in the controls drawings is the same, though vague. The CAV and VAV systems have their own general sequence. Both have fail-safe positions in the event of a power failure. 2. Sequence of Operations - AHUs The units are listed as being controlled via systems supplied by the manufacturer. There is no real sequence, only the minimum variables that must be monitored: supply air temperature for cooling, supply air temperature for heating, airflow, and filter differential pressure. The control drawings also indicate that the AHUs will be connected to the BAS, which is how the AHU controls will be coupled with individual room sensors. 3. Sequence of Operations CAV These are generally the laboratory spaces. Space temperature is maintained through the electric duct heaters (EDH) on the supply side. These are controlled via temperature sensors (TT) on either the return ducts or inside the rooms in order to maintain space temperature. Humidity is monitored via a sensor (H) in the room, and the BAS indicates an alarm upon a variation from the humidity set point. 4. Sequence of Operations VAV The VAV system is composed of 1 AHU (AHU-10) serving all of the general office spaces. The terminal units (TUH) modulate to maintain the space temperature, which is monitored by temperature sensors (TT) in the room. Some contain reheat coils, and some do not. If there is an increase or decrease in space temperature, the first step is to modulate the reheat coils in order to get back to the desired temperature. If there is a further increase or decrease in temperature, then the terminal unit modulates to open. The VAV system does have a night set-back. During that period, the supply dampers will move to the minimum position. During winter warm-up, the reheat coil will operate at capacity with the unit fully open until desired space temperature is achieved. At that point, normal modulating controls will be reinstated During summer cool-down, the unit will operate fully open until desired space temperature is achieved. At that point, normal modulating controls will commence. Page 9 of 27

10 Joseph Firrantello - Mechanical Option Primary Faculty Consultant: Freihaut Laboratory Facility, Eastern Pennsylvania Mechanical Assignment 3 Existing Conditions Report VIII. Critique of System A. In Reference to the Design Objectives and Requirements 1. Occupant Comfort The system appears to satisfy occupant comfort. The CAV and VAV systems adequately supply thermal comfort, and the relatively high OA% supplied to the spaces (mostly because of ANSI standards) provide more than acceptable indoor air quality (see technical assignment 1 for more detailed IAQ calculations). There is always the possibility of control and IAQ problems, however, with the VAV system, due to issues such as inadequate supply air during low supply air volume settings. The ability of the HVAC system to ensure the safety of the occupants is not known, as I have yet been unable to get a copy of the ANSI Laboratory Safety Standard. Given the seriousness of the need to meet the standard, it is reasonable to assume that it has been met. If a further analysis is done, it will be posted in an addendum. 2. Clean Room Conditions The clean rooms conditions seem to be adequately satisfied, via filters and a high air change rate. In addition to the 30% and 90% HEPA filters present on each AHU, there is a 99.99% terminal air filter that supplied the air to the clean room spaces. The class 100,000 clean rooms have a displacement rate of 20 ACH, and the class 10,000 clean rooms have a displacement rate of 40 ACH. Additionally, the rooms are strategically pressurized so that the spaces with the most stringent clean requirements have a relatively higher pressure than the spaces around them. 3. First Cost The mechanical construction cost is Table 5 - HVAC Construction Costs estimated at about $90/sf for the clean Square room spaces, and $35/sf for the office $ per sf Feet Cost spaces. This comes to about $46/sf for Office $ ,000 $2,100,000 HVAC construction, as in Table 5. Clean Room $ ,000 $1,350,000 This appears to be a reasonably low Total $ ,000 $3,450,000 number for an attempt at first cost reduction. B. In Reference to Other Issues 1. Operating Cost While hard numbers for the HVAC operating cost of the facility are not available, it is reasonable to assume that the operational costs may be higher than average because of the first cost-driven design. This explains the lack of heat recovery on the significant of exhausted air, and the lack of a (higher cost than AHUs) central plant for space conditioning. 2. Maintainability The plenum infrastructure (i.e. ductwork, piping, terminal units, etc) should not be hard to maintain, as there is a plenum catwalk to permit access for maintenance. This is done in order to maintain both the operation and purity of the clean room spaces. Page 10 of 27

11 Joseph Firrantello - Mechanical Option Primary Faculty Consultant: Freihaut Laboratory Facility, Eastern Pennsylvania Mechanical Assignment 3 Existing Conditions Report The rooftop AHUs themselves are standard package units with standard controls, and are located the easy-to-access roof. They should prevent no surprises to either on-site or manufacturer provided maintenance persons. Not enough is known about maintenance issues with boiler and chiller plants in order to make a conclusion about them. Page 11 of 27

12 Appendix A - Schematic Diagrams of Boiler, Chiller, and Air Side Page 12 of 27

13 Appendix A - Schematic Diagrams of Boiler, Chiller, and Air Side Page 13 of 27

14 Appendix A - Schematic Diagrams of Boiler, Chiller, and Air Side Page 14 of 27

15 Appendix A - Schematic Diagrams of Boiler, Chiller, and Air Side Page 15 of 27

16 Appendix A - Schematic Diagrams of Boiler, Chiller, and Air Side Page 16 of 27

17 Appendix A - Schematic Diagrams of Boiler, Chiller, and Air Side Page 17 of 27

18 Appendix A - Schematic Diagrams of Boiler, Chiller, and Air Side Page 18 of 27

19 Appendix A - Schematic Diagrams of Boiler, Chiller, and Air Side Page 19 of 27

20 Appendix B - Schedules of Major Mechanical Equipment REFRIGERATION UNIT DATA (CHILLER) - AIR COOLED Chilled Water Ambient Condenser Fans Electrical Number System Serving Nom Tons Type Air F on Starter GPM EWT F LWT F PD Feet Quant HP FLA V-P-Hz Comp kw FLA LRA V-P-Hz P.F. Unit Type R-1 Process Chilled Water 117 Screw Across Ln 95% Number System Serving gpm PUMP DATA Motor HP RPM V-P-Hz P-CH-1 Process Chilled Water P-CH-2 Process Chilled Water Number Max Oper System Serving Boiler HP Type Steam or Water Design PSI PSI BOILER DATA SRV Setting PSI MBH H 2 O B-1 Plant Steam 200 Fire Steam Gas yes B-2 Plant Steam 200 Fire Steam Gas yes Fuel Fuel/Air Control Capacities MBH Output lbs/hr Steam Gas Firing Rate Natural Gas Press in. Fan HP Electrical V-P-Hz DEAERATOR - BOILER FEED EQUIPMENT DATA Number System Serving Type Max Load Receiver Max Steam Heater Make-up Assembly Design SRV Setting PSI Gallons Gallons Cond Return Allowable O Design PSI lbs/hr Boiler HP Size Total Mins Stor 2 lbs/hr psi Max GPM Mixing Deaer lbs/hr Avg Temp F Concentratio GPM inlet DA-1 Boilers 1 & 2 Spray , x DEAERATOR - BOILER FEED EQUIPMENT DATA (CONT.) Boiler Feed Pumps Number Quantity GPM per Motors Disch feet Oper Stand pump HP Each RPM V-P-Hz DA PRESSURE POWERED CONDENSATE PUMP SKID Number System Serving Motive Back Actual Capacity Number of Packaged Flash Flash Inlet Pressure lbs/hr Pumps Assembly Receiver Size Vent Size Pressure psig PPC-1 Boiler System Yes 20 gal 4" BLOWDOWN SEPERATOR Connections Number System Serving Diameter Height Vent Drain Blowdown Quench BS-1 Boiler System 14" 34" 5" 5" 2" 2" Page 20 of 27

21 Appendix B - Schedules of Major Mechanical Equipment Number System/Serving SP Inches H 2O Supply Air Fan Max OV Number cfm TSP ESP Fan Type Fan RPM FPM HP RPM V-PH-Hz Type Unit Quant HP Each FLA Each kw RLA Each LRA Each Quantity V-PH-Hz AHU-1 Area 1 SF-1-1 9, AF DWDI R yes AHU-2 Area 2 SF , AF DWDI R yes AHU-3 Area 3 SF-3-1 7, AF DWDI R yes AHU-4 Area 4 SF-4-1 7, AF DWDI R yes AHU-5 Area 5 SF-5-1 4, AF DWDI R yes AHU-6 Area 6 SF-6-1 4, AF DWDI R yes AHU-7 Area 7 SF , AF DWDI R yes AHU-8 Area 8 SF , AF DWDI R yes AHU-9 Area 9 SF-9-1 7, AF DWDI R yes AHU-10 Area 10 SF , AF DWDI R yes AHU-11 Area 11 SF , AF DWDI R yes AHU-12 Area 12 SF , AF DWDI R yes AHU-13 Area 13 SF , AF DWDI R yes AHU-14 Area 14 SF , AF DWDI R yes AHU-15 Area 15 SF , AF DWDI R yes AHU DATA (CONT.) Cooling Coil Heating - Natural Gas Number Max Face Number of E.A.T. F L.A.T. F Mbtu/h PD (wet) in. Air F PD in. Natural Gas Stages Number Rows Fins/in Type Number Type Velocity Coils DB DB WB Total Sensible H 2O L.A.T. H 2O BTUH Input BTUH Output Gas Press in. H 2O AHU-1 CC DX PH AHU-2 CC DX PH-2-1 Preheat AHU-3 CC DX PH-3-1 Preheat AHU-4 CC DX PH-4-1 Preheat AHU-5 CC DX PH-5-1 Preheat AHU-6 CC DX PH-6-1 Preheat AHU-7 CC DX PH-7-1 Preheat AHU-8 CC DX PH AHU-9 CC DX PH AHU-10 CC DX PH-10-1 Preheat AHU-11 CC DX PH-11-1 Preheat AHU-12 CC DX PH-12-1 Preheat AHU-13 CC DX PH-13-1 Preheat AHU-14 CC DX PH-14-1 Preheat AHU-15 CC DX PH-15-1 Preheat AHU DATA (CONT.) Number Filters Filters Average Average PD in. H Number Type Eff % 2O Number Eff % PD in. H 2O Vibration Isolation (ASHRAE) Initial Final (ASHRAE) Initial Final Type Defl in inches AHU-1 F-1-1 Cartridge F Spring 2 AHU-2 F-2-1 Cartridge F Spring 2 AHU-3 F-3-1 Cartridge F Spring 2 AHU-4 F-4-1 Cartridge F Spring 2 AHU-5 F-5-1 Cartridge F Spring 2 AHU-6 F-6-1 Cartridge F Spring 2 AHU-7 F-7-1 Cartridge F Spring 2 AHU-8 F-8-1 Cartridge F Spring 2 AHU-9 F-9-1 Cartridge F Spring 2 AHU-10 F-10-1 Cartridge F Spring 2 AHU-11 F-11-1 Cartridge F Spring 2 AHU-12 F-12-1 Cartridge F Spring 2 AHU-13 F-13-1 Cartridge F Spring 2 AHU-14 F-14-1 Cartridge F Spring 2 AHU-15 F-15-1 Cartridge F Spring 2 Motor Minimum Outside Air-cfm AHU DATA Refrigerant # of circuits Ambient Air F on Condenser Fan Compressor Crankcase Heater Control Circuit Voltage Page 21 of 27

22 Appendix B - Schedules of Major Mechanical Equipment Number System Serving cfm FAN DATA SP in. Max Out Motor Vibration Fan Type Class Fan RPM H 2 O Velocity (FPM) HP RPM V-P-Hz Isolation EF-2-1 AHU centrifugal spring EF-3-1 Cell Culture 4 Room P centrifugal spring EF-4-1 Cell Culture 3 Room P centrifugal spring EF-7-1 AHU-7 / AHU-9 Relief Air centrifugal spring EF-7-2 Rooms P233, P234, P249, P centrifugal spring EF-8-1 Rooms P204, P201, P278, P centrifugal spring EF-9-1 Rooms C213 & C centrifugal spring EF-1 Mechanical Room P centrifugal spring EF-2 Ceiling Plenum centrifugal spring EF-3 Ceiling Plenum centrifugal spring EF-4 Ceiling Plenum centrifugal spring EF-5 Mechanical Room P centrifugal spring EF-6 Mechanical Room P centrifugal spring EF-7 Mechanical Room P centrifugal spring EF-8 Mechanical Room P centrifugal spring EF-9 Mechanical Room P centrifugal spring EF-10-1 Men & Women Room centrifugal spring EF-10-2 Men & Women Room centrifugal spring EF-11-1 AHU-11, AHU-12, AHU centrifugal spring EF-14-1 BL3 Labs centrifugal spring EF-14-2 BL3 Labs centrifugal spring EF-15-1 Chemical Waste, Medical Waste centrifugal spring EF-15-2 Radioactive Waste centrifugal spring EF-15-3 Medical Waste, Liquid Nitrogen centrifugal spring EF-16-1 Men & Women Room centrifugal spring Page 22 of 27

23 Appendix B - Schedules of Major Mechanical Equipment TERMINAL AIR FILTER MODULE DATA Number System Serving cfm Average Eff % Cell Size Pressure Drop in. H 2 O (ASHRAE) L (in.) W (in.) Initial Final TAF-1 various lab various TAF-2 various lab various the two types of TAFs are used repeatedly throughout the facility, cfm depends on supply at diffuser AIR DEVICE DATA Number Type Use Blow Damper AD-1 Louvered Supply Air 1 Way Opp Blade AD-2 Louvered Supply Air Corner Opp Blade AD-3 Louvered Supply Air 3 Way Opp Blade AD-4 Louvered Supply Air 4 Way Opp Blade AD-5 Grille Return Air n/a Opp Blade AD-6 Grille Return Air n/a Opp Blade AD-7 Grille Return Air n/a None AD-8 Egg Crate Return Air n/a None AD-9 Perforated Supply Air n/a None AD-10 Perforated Supply Air n/a None Finish Baked White Enamel Baked White Enamel Baked White Enamel Baked White Enamel Baked White Enamel Baked White Enamel Stainless Steel Baked White Enamel Baked White Enamel Baked White Enamel Page 23 of 27

24 Appendix B - Schedules of Major Mechanical Equipment ELECTRIC DUCT HEATER DATA Number CFM Max Face Size of Coil Air F Electric Type of Vel. (FPM) LxH E.A.T L.A.T. MBH PD in. H 2 O kw V-P-Hz Control EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR Page 24 of 27

25 Appendix B - Schedules of Major Mechanical Equipment ELECTRIC DUCT HEATER DATA Number CFM Max Face Size of Coil Air F Electric Type of Vel. (FPM) LxH E.A.T L.A.T. MBH PD in. H 2 O kw V-P-Hz Control EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR EDH x SCR Page 25 of 27

26 Appendix B - Schedules of Major Mechanical Equipment UNIT HEATER DATA Motor Natural Gas Number Location BTUH BTUH Gas Press. Type Arrangement cfm hp rpm V-P-Hz Vent Size Input Output in. H 2 O UH-1 Ceiling Plenum 380 1/ ,000 20, Fan Gravity Vent UH-2 Ceiling Plenum 380 1/ ,000 20, Fan Gravity Vent UH-3 Ceiling Plenum 380 1/ ,000 20, Fan Gravity Vent UH-4 Ceiling Plenum 980 1/ ,000 60, Fan Gravity Vent UH-5 Ceiling Plenum 980 1/ ,000 60, Fan Gravity Vent Number System Serving cfm Entering Air DB Temp Grains DB Temp Grains HUMIDIFIER DATA (STEAM TO STEAM) Room Air Plant Steam Humidification Steam lbs/hr Distance (in.) H-2-1 AHU-2 12, Softened 40"x40" H-7-1 AHU-7 11, Softened 40"x40" H-11-1 AHU-11 8, Softened 32"x30" H-12-1 AHU-12 23, Softened 48"x46" H-13-1 AHU-13 17, Softened 42"x40" H-14-1 AHU-14 3, Softened 24"x22" psig lbs/hr psig Feed Water Type Duct Size (WxH) Duct Velocity (fpm) Max Absorption TERMINAL AIR UNT DATA cfm SP in. H 2 O Sound Data (NC) Reheat Coil Number System Serving terminal system Air F min max Disc Radiated unit only min EAT LAT kw V-P-Hz TUS-10-1 AHU-10 Room TUS-10-2 AHU-10 Room 094, TUS-10-3 AHU-10 Room TUS-10-4 AHU-10 Room TUS-10-5 AHU-10 Room 060, TUS-10-6 AHU-10 Room TUS-10-7 AHU-10 Room 067, 068, TUS-10-8 AHU-10 Room TUS-10-9 AHU-10 Room TUS AHU-10 Room TUS AHU-10 Room 009, 018, TUS AHU-10 Room 006, TUS AHU-10 Room TUS AHU-10 Room 001, 002, Page 26 of 27

27 Appendix B - Schedules of Major Mechanical Equipment Maximum cfm AUTOMATIC DAMPER DATA Damper Function Control Number System Serving Blade Arrangement L (in.) W (in.) M.O.D. ON OFF D-1 Combustion Air Opposed X D-2 Combustion Air Opposed X D-3 Combustion Air Opposed X D-4 Combustion Air Opposed X D-5 Air Compressor CA-1 Supply Opposed X D-6 Air Compressor CA-1 Supply Opposed X D-7 Air Compressor CA-1 Exhaust Opposed X D-8 Air Compressor CA-1 Exhaust Opposed X D-11-1 EF Opposed X D-14-1 EF Opposed X D-14-2 EF Opposed X D-15-1 EF Opposed X D-15-2 EF Opposed X D-15-3 EF Opposed X Size AIR MEASURING DEVICE DATA Number System Serving cfm Face Pressure Overall Size (inches) Velocity Drop in. W H L AM-1-1 AHU-1 Supply Air AM-2-1 AHU-2 Supply Air AM-3-1 AHU-3 Supply Air AM-4-1 AHU-4 Supply Air AM-5-1 AHU-5 Supply Air AM-6-1 AHU-6 Supply Air AM-7-1 AHU-7 Supply Air AM-8-1 AHU-8 Supply Air AM-9-1 AHU-9 Supply Air AM-11-1 AHU-11 Supply Air AM-12-1 AHU-12 Supply Air AM-13-1 AHU-13 Supply Air AM-14-1 AHU-14 Supply Air AM-15-1 AHU-15 Supply Air Page 27 of 27