MT. AIRY MIDDLE SCHOOL CARROLL COUNTY PUBLIC SCHOOLS

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CARROLL COUNTY PUBLIC SCHOOLS LIFE CYCLE COST ANALYSIS SUMMARY DGS PROCEDURES FOR THE IMPLEMENTATION OF LIFE CYCLE COST ANALYSIS AND ENERGY CONSERVATION OCTOBER, 2010 G.A.I.#09090 GIPE ASSOCIATES, INC. DESIGN DEVELOPMENT SUBMISSION

IV. LIFE-CYCLE COST ANALYSIS - SYSTEM DESCRIPTION PROJECT: MT. AIRY MIDDLE SCHOOL LOCATION: Carroll County, Maryland USING AGENCY Carroll County Public Schools DATE October, 2010 BY (NAME AND TITLE): Jeffrey W. Alban, Vice President, Gipe Associates, Inc. SYSTEM DESCRIPTION The four systems analyzed included: BASE SYSTEM: VERTICAL GEOTHERMAL HEAT PUMP UNITS located in Mechanical Closets used in conjunction with indoor heat recovery type dedicated outdoor air units. ALTERNATE 1: FOUR-PIPE VERTICAL FAN-COIL UNITS located in Mechanical Closets used in conjunction with indoor heat recovery type dedicated outdoor air units. ALTERNATE 2: FOUR-PIPE VARIABLE AIR VOLUME with air handling units strategically located in the Mechanical Equipment Rooms. ALTERNATE 3: STANDARD VERTICAL WATER SOURCE HEAT PUMP UNITS located in Mechanical Closets used in conjunction with indoor heat recovery type dedicated outdoor air units. SUMMARY OF RESULTS: The Geothermal Heat Pump System was the lowest Life Cycle Cost System and was used as the basis of Design. Even though the Fan Coil Unit System uses heat recovery for ventilation air, mechanical cooling was required during the winter season for interior spaces since this system does not utilize a free cooling outside air economizer cycle. For consistency, all systems were based on indoor type air handling units per the County Standard. Similarly, heat recovery units for the fan-coil unit system, geothermal heat pump system and water source heat pump system were based on indoor units requiring the same mechanical penthouse space. For these same three systems, floor square footage was required to house vertical type units in mechanical closets; therefore, additional cost for this area was included in the analysis. The Geothermal System required less net square footage due to the difference in the main mechanical equipment room size. The Water Source Heat Pump System still requires boilers for supplemental heat and cooling towers for heat rejection. The higher flow rates (3 GPM per ton) required for this condenser water loop contributed to higher pumping cost and higher LCC. Site grading is already required to create playing fields, which are located adjacent to the school. Locating the earth heat exchanger at this location reduces differential while increases the operational cost differential between conventional systems and the geothermal system. Based on these conditions, the Geothermal Heat Pump System is the recommended system having the lowest Life Cycle Cost (LCC). G.A.I.#09090 Page - 1

BASE SYSTEM: GEOTHERMAL WATER SOURCE HEAT PUMPS The geothermal (extended range) water source heat pump system consists of a two-pipe (supply and return) condenser water circulating loop system. The loop pipe is sized to absorb space heat as well as the heat generated by inefficiency of the compressor (equivalent to 3.0 gpm/ton). The building distribution circulation pumps will be located in the Main Mechanical Room and will be variable water flow connected to the geothermal water source heat pumps. 1. Cooling: Each extended range type geothermal water source heat pump (ARI 330 Certified) has a selfcontained refrigeration system utilizing a hermetically sealed compressor and water-cooled heat exchangers. Since each room has a dedicated compressor for cooling, the total connected cooling capacity (refrigeration tonnage) is higher equivalent to the sum of each space peak load. The total heat of rejection absorbed in the water loop is then rejected to the ground heat sink. It is estimated that 220 vertical bore holes, 400-450 feet deep each (approximately 37.5 miles) of piping will be required. There is a cost-effective location on the existing site to locate the earth heat exchanger in close proximity to the building at the proposed playing fields. 2. Heating: Each extended range type geothermal water source heat pump, utilizing its self-contained refrigeration system, has a reversing valve, which in the heating mode uses the air stream coil as the condenser, rejecting heat, and the water heat exchanger as the evaporator, absorbing heat from the water. Heat for each space is the sum of the electrical input into the compressor as well as the heat absorbed from the central circulating loop. Heat is introduced into the central circulating loop from heat absorbed from the ground heat sink. Hot water supplied by an Auxiliary Boiler is required to temper the condenser water loop to prevent freezing when heat absorption from the loop by heat pumps exceeds heat absorption into the loop from the earth (i.e. morning warm-up). 3. Supplemental Heat: Hot water type heating units (unit heaters, cabinet unit heaters, etc.) will be used for stairwells, vestibules, mechanical equipment spaces, etc. 4. Geothermal Water Source Heat Pumps: Each educational room will be provided with a dedicated geothermal water source heat pump with its own self-contained refrigeration system. Each unit will be sized to provide sensible heating and cooling only (i.e., no latent load). The unit will be provided with supply air ductwork connected to ceiling type air devices and return air ductwork connected to the room return air filter grille. A separate ventilation air duct served by an independent ventilation air unit will distribute conditioned outside to each occupied space and will be balanced to insure minimum ventilation rates are being introduced into each space. 5. Ventilation Air Units: Multiple indoor type, 100% outdoor air, dual temperature type heat recovery ventilation units will be provided in the various educational zones to provide conditioned ventilation air to geothermal heat pump units. These units will use heat recovery devices such as rotary type enthalpy heat wheels and sensible flat plate heat exchangers to insure ventilation air is conditioned to maintain ASHRAE and MSDE Standards. These units will also contain pre- and high efficiency supply air filters, relief air prefilters, supply air fan and relief air fan. Conditioned ventilation air will be ducted directly to the space for which each heat pump unit serves. Relief air (air purged from the building) systems will utilize the ceiling plenum to minimize construction cost. 6. Air Handling Units: Gymnasium, Cafeteria, Locker Room, Activity Room, and Weight Room areas will utilize a constant air volume single zone air handling units in conjunction with heat recovery for ventilation air. The air handling system will consist of a return air fan, mixing box/economizer section, prefilter, and fan filters, dual temperature coil and supply air fan. G.A.I.#09090 Page - 2

BASE SYSTEM (Continued) Office/Administration & Media Center: These areas will be provided with dedicated geothermal heat pumps in conjunction with the heat recovery ventilation air unit similar to that described hereinbefore for educational spaces. Through the use of water loop zone subcircuit control valves, the Office/Administration Area will remain as an active sub-zone during the summertime, thus reducing pump energy through the use of the variable speed drives. The geothermal water source heat pump system is similar to the standard water source heat pump system except it utilizes the ground as its primary heat source or heat exchanger. The system analysis was based on a vertical loop well field. Information used in the analysis was based on the ASHRAE 1997 Geothermal Heat Pumps: Design of Geothermal Systems for Commercial and Institutional Buildings, Manufacturers= Engineering Information, the Geothermal Heat Pump Consortium, the International Ground Source Heat Pump Association (IGSHPA), and other various information primarily published by Mr. Steven Kavanaugh, Ph.D. The advantage of the geothermal heat pump system is the inherent heat recovery capabilities which transfer rejected heat from the interior spaces during the winter season into the common loop, which allows perimeter units to absorb this wasted heat. Only two pipes, supply and return, are needed, although they do require insulation. Any unit connected to the main water loop can heat or cool at all times. Since these units are self-contained refrigeration systems, there is little to maintain. However, unit failure often requires the unit to be removed and replaced in lieu of serviced in place. Mechanical equipment is minimized as the earth heat exchanger is used in lieu of central plant equipment. G.A.I.#09090 Page - 3

ALTERNATE NO. 1: FOUR-PIPE FAN-COIL UNIT SYSTEM A four-pipe central plant serving fan-coil units throughout the facility will be located in the Main Mechanical Room with the cooling tower located on the building roof. 1. Chilled Water Plant: Two (2) water-cooled centrifugal chillers. The chiller has dedicated condenser water pumps sequenced with the associated chiller which is fed to a standard cooling tower. Chilled water will be distributed to air handling units, fan coil units, and heat recovery units via secondary variable speed/flow pumps. 2. Heating Water Plant: Four (4) equally-sized cast iron type hot water boilers utilizing natural gas. Heating water will be distributed to air handling units, fan-coil units, heat recovery units, and terminal heating devices (e.g., convectors, unit heaters, etc.) via secondary variable speed/flow pumps. 3. Fan-Coil Systems: Each educational room will be provided with a dedicated vertical type four-pipe fan-coil unit. The unit will consist of a supply fan, heating coil and cooling coil with a 2-way control valve for each coil. Each unit will be sized to provide sensible heating and cooling only (i.e., no latent load). The unit will be provided with supply air ductwork connected to ceiling type air devices and return air ductwork connected to the room return air filter grille. A separate ventilation air duct served by an independent ventilation air unit will distribute conditioned outside air to each space to insure minimum ventilation rates are being introduced into each space. Fan coil units will be located in mechanical closets adjacent to the spaces they serve, which increases the footprint to the building. It is not recommended to locate these units above the ceiling due to the increased maintenance requirements and the higher possibility of indoor air quality problems. 4. Ventilation Air Units: Multiple indoor type 100% outdoor air, heat recovery type ventilation units will be provided in the various educational zones to provide conditioned ventilation air to fan-coil units. These units will use heat recovery devices such as rotary type enthalpy and sensible flat plate heat exchagers to pretreat and reheat the air in conjunction with hot water heating coils and chilled water dehumidification coils to insure ventilation air is conditioned to maintain ASHRAE and MSDE Standards. These units will also contain preand high efficiency supply air filters, relief air prefilters, supply air fan and relief air fan. Conditioned ventilation air will be ducted directly to each occupied space. Relief air (air purged from the building) systems will utilize the ceiling plenum to minimize construction cost. Dedicated outdoor air systems must dehumidify outdoor air to prevent high humidity levels and reheat the air to prevent sub-cooling. Refer to ventilation air heat recovery psychometric calculations for information regarding the requirements for conditioning ventilation air. 5. Air Handling Units: Gymnasium, Cafeteria, Locker Room, Activity Room, and Weight Room areas will utilize a constant air volume single zone air handling units. The air handling system will consist of a return air fan, mixing box/economizer section, prefilter, and fan filters, hot water preheat coil with freeze protection circulator pumps, chilled water cooling coil, hot water heating coil and supply air fan. The four pipe fan-coil system utilizes a Dedicated Outdoor Air System (DOAS), which is decoupled from the room units and minimizes possible indoor air quality issues as well as simplifies system operation and maintenance. Terminal fancoil units will be distributed throughout the facility and provide sensible heating and cooling only. The ventilation air units are sized to provide the minimum ventilation air only, minimizing ductwork sizes and simplifying distribution systems. These units provide approximately one third of the air flow as compared to a conventional variable air volume system. Unlike the variable air volume system, the four-pipe fan coil systems do not have air side economizer capability. G.A.I.#09090 Page - 4

ALTERNATE NO. 1 (Continued) The central cooling plant refrigeration equipment is sized based on the building block load (which is less than the sum of individual space peak loads required by small compressor-based systems) and is located in the mechanical equipment room and not scattered throughout the building as in a decentralized system. The advantages of this system include superior indoor air quality through the use of dedicated ventilation air units, energy-conserving heat recovery to minimize central plant equipment and distribution system sizes, individual room control while providing simple operation; and, at the same time, minimizing structural constraints with sheet metal. Fan-coil units are very quiet and are readily available in a wide variety of sizes and capacities. These units can be easily and inexpensively serviced when located in accessible mechanical closets. G.A.I.#09090 Page - 5

ALTERNATE NO. 2: FOUR-PIPE VARIABLE AIR VOLUME SYSTEM: A four-pipe central plant system serving air handling units throughout the facility will be located in the Main Mechanical Room with the cooling tower located on the building roof. 1. Chilled Water Central Plant: Two (2) water-cooled centrifugal chillers. The chiller has dedicated condenser water pumps sequenced with the associated chiller which is fed to a standard cooling tower. Chilled water will be distributed to air handling units, fan coil units, and heat recovery units via secondary variable speed/flow pumps. 2. Heating Water Central Plant: Four (4) equally-sized cast iron type hot water boilers utilizing natural gas. Heating water will be distributed to air handling units, fan-coil units, heat recovery units, and terminal heating devices (e.g., convectors, unit heaters, etc.) via secondary variable speed/flow pumps. 3. Air Handling Systems: Multiple variable air volume air handling systems strategically located in mechanical penthouses will serve associated air handling zones for educational areas as well as office/administration areas. Units consist of a return fan, mixing box/economizer section, prefilters and high efficiency final filters, preheat coil with freeze protection pumps, chilled water cooling coil and supply air fan. Supply and return fans will be provided with variable speed drives and duct-mounted air flow measuring stations to volumetrically track supply to return air volumes. Variable air volume fan-powered terminal units will be equipped with hot water heating coils. Induced air will be ducted to terminal units and will be connected to room return air filter grilles. Air Handling Units: Gymnasium, Cafeteria, Locker Room, Activity Room, and Weight Room areas will utilize a constant air volume single zone air handling units in conjunction with heat recovery for ventilation air. The air handling system will consist of a return air fan, mixing box/economizer section, prefilter, and fan filters, hot water preheat coil with freeze protection circulator pumps, chilled water cooling coil, hot water heating coil and supply air fan. The advantages of this system include full air side economizer cycles and the fact that it does not require the use of dedicated ventilation air units. The cooling central plant refrigeration equipment is sized based on the building block load (which is less than the sum of individual space peak loads required by small compressorbased systems) and all central plant generating equipment being located in the boiler/chiller room and not scattered throughout the building. G.A.I.#09090 Page - 6

ALTERNATE NO. 3 - STANDARD WATER-TO-AIR HEAT PUMPS (WATER SOURCE) 1. The water source heat pump system consists of a two-pipe (supply and return) condenser water circulating loop system. The loop pipe is sized to absorb space heat as well as the heat generated by inefficiency of the compressor (equivalent to 3.0 gpm/ton). These primary circulation pumps will be located in the Main Mechanical Room and will be variable volume/flow connected to water source heat pumps serving educational spaces. a. Cooling: Each water source heat pump (ARI 320 Certified) has a self-contained refrigeration system utilizing a hermetically sealed compressor and water-cooled heat exchanger. Since each room has a dedicated compressor for cooling, the total connected cooling capacity (refrigeration tonnage) is higher than the block load and is the sum of each space peak load. The total heat of rejection absorbed in the water loop is then rejected to the atmospheric heat sink via two equally sized cooling towers. Open loop type cooling towers are proposed. To separate the closed water source heat pump circulating loop from the open cooling tower condenser water loop, a flat plate heat exchanger is used with a 5 F approach. Therefore, all heat pumps are sized (i.e., derated) based on 90 F entering water temperature with a 10 F temperature rise. b. Heating: Each water source heat pump, utilizing its self-contained refrigeration system, has a reversing valve, which in the heating mode uses the air stream coil as the condenser, rejecting heat, and the water heat exchanger as the evaporator, absorbing heat from the water. Heat for each space is generated from the sum of the electrical input into the compressor as well as the heat absorbed from the central circulating loop. This loop is maintained at a minimum of 70 F. When heat absorption from the loop drops the water temperature to this setpoint, supplemental heat is added from the central heating plant via a water-to-water heat exchanger. A water-to-water heat exchanger is necessary to separate boiler water from low temperature (70 F) heat pump water to insure proper operation (i.e., avoid thermal shock and flue condensation) of the heating plant. Total supplemental heat input is typically about two thirds of the total heating capacity. 2. Central Heating Plant: Two equally-sized hot water boilers utilizing natural gas as the primary fuel source. Each boiler has a dedicated pump to be sequenced with the boiler to minimize standby losses. Heating water will be distributed to air handling units, water source heat pump loop water-to-water heat exchanger, and terminal heating devices, such as convectors, unit heaters, and cabinet unit heaters. 3. Water Source Heat Pumps: Each educational room will be provided with a dedicated vertical type water source heat pump with its own self-contained refrigeration system. Each unit will be sized to provide sensible heating and cooling only (i.e., no latent load). The unit will be provided with supply air ductwork connected to ceiling type air devices and return air ductwork connected to the room return air filter grille. A separate ventilation air duct served by an independent ventilation air unit will be connected to each unit=s return air duct and will be balanced to insure minimum ventilation rates are being introduced into each space. The building hydronic loop will be zoned with piping branches for each zone being equipped with solenoid valves such that areas can be isolated. The main distribution pump will be provided with a variable speed drive controller such that only the required condenser water will be pumped, based on occupancy (i.e., Office / Administration, Dining, etc.). Each unit requires its full water flow rate when the compressor is operating. Water flow rates for water source heat pumps are 3 gpm/ton versus 2.4 gpm/ton for chilled water systems. The additional flow rate associated with condenser water systems is required to reject the heat absorbed from the space, as well as the heat resulting from compressor inefficiency. G.A.I.#09090 Page - 7

ALTERNATE NO. 3 (Continued) 4. Ventilation Air Units: Indoor type 100% outdoor air, heat recovery type water source heat pump ventilation units will be provided in the various educational zones to provide conditioned ventilation air to the water source heat pump units. These units will use heat recovery devices such as rotary type enthalpy and sensible heat wheels to pretreat the air in conjunction with heating and dehumidification coils to insure ventilation air is conditioned to maintain ASHRAE and MSDE Standards. These units will also contain pre- and high efficiency supply air filters, relief air prefilters, supply air fan and relief air fan. Conditioned ventilation air will be ducted directly into each space. Relief air (air purged from the building) systems will utilize the ceiling plenum to minimize construction cost. Refer to ventilation air heat recovery psychometric calculations for information regarding the requirements for conditioning ventilation air. 5. Air Handling Units: Gymnasium, Cafeteria, Locker Room, Activity Room, and Weight Room areas will utilize a constant air volume single zone air handling units in conjunction with heat recovery for ventilation air. Office/Administration & Media Center: These areas will be provided with dedicated heat pumps in conjunction with the heat recovery ventilation air unit similar to that described hereinbefore for educational spaces. Through the use of water loop zone subcircuit control valves, the Office/Administration Area will remain as active sub-zones during the summertime, thus reducing pump energy through the use of the variable speed drives. The water source heat pump system does not require the same central mechanical space; however, it will require a small mechanical closet in each classroom to house the heat pump. Vertical units in closets are used to ease maintenance and reduce noise. The advantage of the water source heat pump system is the inherent heat recovery capabilities which transfer rejected heat from interior spaces during the winter season into the common loop which allows perimeter units to absorb this wasted heat. Only two pipes, supply and return, are needed; and they do not require insulation. Any unit connected to the main water loop can heat or cool at all times. Since these units are self-contained refrigeration systems, there is little to maintain; however unit failure often requires the unit to be removed and replaced in lieu of serviced in place. The disadvantages of these units are the multitude of refrigeration systems and their associated compressor cycling noise which is distributed throughout the building. This system is penalized in the winter due to the cooling requirements associated with a building having an efficient envelope and large interior spaces resulting in a winter-time cooling requirement. The larger flow rates and pressure requirements for the main circulating pumps increases pumping cost for this system. G.A.I.#09090 Page - 8

V. ENERGY COST ESTIMATE: A. COST OF ENERGY ENERGY TYPE ESTIMATED AVERAGE ESCALATION RATE UNIT COST ELECTRIC ENERGY CHARGE $0.14735 (Summer) 3% $0.13873 (Winter) 3% ELECTRIC DEMAND 7.67 $ PER KW (Summer) 3% CHARGE 7.21 $ PER KW (Winter) BGE STEAM ENERGY N/A $ PER MLB(Winter) N/A CHARGE N/A $ PER MLB(Summer) N/A STEAM DEMAND N/A $ PER MLB(Winter) N/A CHARGE N/A $ PER MLB(Summer) N/A GAS 0.85 $ PER THERM 5% FUEL OIL N/A $ PER GALLON N/A COAL N/A $ PER TON N/A OTHERS N/A $ PER N/A N/A $ PER N/A UTILITY SUMMER RATE MONTHS N/A TO N/A UTILITY WINTER RATE MONTHS: N/A TO N/A USEFUL EQUIPMENT LIFE 45 YEARS (per IAC) DISCOUNT RATE 30.03 (.05 ESCALATION RATE,.07 DISCOUNT RATE) (Present Worth Factor) A.I.#09090 Page 9

VI. INITIAL COST ESTIMATE A. HVAC MAJOR EQUIPMENT ITEM QUANTITY CAPACITY UNIT PRICE TOTAL PRICE (UNITS) MATERIAL LABOR MATERIAL LABOR TOTAL 1. CHILLERS Tons EACH 2. BOILERS BHP EACH 3. PUMPS GPM TOTAL FT HEAD 4. AIR CFM HANDLING UNITS MBH COOLING MBH HEATING MOTOR H.P. 5. FANS CFM SUPPLY MOTOR H.P. RETURN CFM EXHAUST POWER ROOF VENTILATOR OTHERS MOTOR H.P. CFM MOTOR H.P. CONDENSING EACH UNITS NOTE: Refer to itemized breakdown and comparison of Alternate Systems at the end of the Analysis for incremental cost differences between system types. G.A.I.#09090 Page 10

VI. INITIAL COST ESTIMATE A. HVAC MAJOR EQUIPMENT (Cont.'d) ITEM QUANTITY CAPACITY UNIT PRICE TOTAL PRICE (UNITS) MATERIAL LABOR MATERIAL LABOR TOTAL 6. SPLIT AND TONS UNITARY SYSTEM 7. THRU THE TONS WALL HVAC UNITS 8. HEAT MBH PUMPS COOLING MBH HEATING 9. TERMINAL UNITS (V.A.V.) ETC. (UNIT VENTI- LATOR) CFM/EA. 10. WATER GPH HEATER MBH 11. HOT WATER GPM CONVERTORS GPM & HEAT EXCHANGERS MBH COOLING MBH 12. COOLING TONS EA. TOWERS NOTE: Refer to itemized breakdown and comparison of Alternate Systems at the end of the Analysis. G.A.I.#09090 Page 11

VI. INITIAL COST ESTIMATE A. HVAC MAJOR EQUIPMENT (Cont.'d) ITEM QUANTITY CAPACITY UNIT PRICE TOTAL PRICE (UNITS) MATERIAL LABOR MATERIAL LABOR TOTAL 13. DOMESTIC STORAGE WATER GAL HEATERS RECOVERY GPH MBH 14. TEMPERATURE CONTROL SYSTEM 15. MISCELL- ANEOUS EQUIPMENT a. FUEL OIL SYSTEM b. TEST & BALANCE c. HEATING WATER PUMPS & DISTRIBUTION d. INSULATION e. CHILLED WATER PUMPS & DISTRIBUTION f. DUCTWORK g. SPRINKLERS h. PLUMBING NOTE: Refer to itemized breakdown and comparison of alternate systems at end of Analysis. GRAND TOTAL G.A.I.#09090 Page 12

VII. ANNUAL COST BASE SYSTEM: VERTICAL GEOTHERMAL HEAT PUMP UNITS A. ENERGY (EXCLUDING LIGHTING, RECEPTACLES) UNIT TOTAL ENERGY OF ENERGY DEMAND ENERGY SOURCE MEASURE ENERGY CONSUMPTION COST CHARGE COST ELECTRIC KWH 579,238 $82,040 $18,158 $100,198 GAS THERM - (SUMMER & WINTER) GAS MCF OR - THERM STEAM MLB/HR - (Winter) STEAM MLB/HR - (Summer) FUEL OIL GAL - COAL TON - OTHERS - - Total $100,198 G.A.I.#09090 Page 13

VII. ANNUAL COST ALTERNATE NO: 1 FOUR-PIPE FAN-COIL UNITS A. ENERGY (EXCLUDING LIGHTING, RECEPTACLES) UNIT TOTAL ENERGY OF ENERGY DEMAND ENERGY SOURCE MEASURE ENERGY CONSUMPTION COST CHARGE COST ELECTRIC KWH 611,537 $87,092 $18,972 $106,064 GAS THERM 7,083 $6,441 --- $6,441 (SUMMER & WINTER) GAS MCF OR - THERM STEAM MLB/HR - (Winter) STEAM MLB/HR - (Summer) FUEL OIL GAL - COAL TON OTHERS - Total $112,505 G.A.I.#09090 Page 14

VII. ANNUAL COST ALTERNATE NO: 2 FOUR-PIPE VARIABLE AIR VOLUME UNITS A. ENERGY (EXCLUDING LIGHTING, RECEPTACLES) UNIT TOTAL ENERGY OF ENERGY DEMAND ENERGY SOURCE MEASURE ENERGY CONSUMPTION COST CHARGE COST ELECTRIC KWH 632,169 $90,370 $20,976 $111,346 GAS THERM 3,861 $3,702 $3,702 (SUMMER & WINTER) GAS MCF OR - THERM STEAM MLB/HR - (Winter) STEAM MLB/HR - (Summer) FUEL OIL GAL - COAL TON - OTHERS - - Total $115,048 G.A.I.#09090 Page 15

VII. ANNUAL COST ALTERNATE NO: 3 STANDARD WATER SOURCE HEAT PUMPS A. ENERGY (EXCLUDING LIGHTING, RECEPTACLES) UNIT TOTAL ENERGY OF ENERGY DEMAND ENERGY SOURCE MEASURE ENERGY CONSUMPTION COST CHARGE COST ELECTRIC KWH 673,603 $95,737 $21,455 $117,192 GAS THERM 1,764 $1,920 --- $1,920 (SUMMER & WINTER) GAS MCF OR - THERM STEAM MLB/HR - (Winter) STEAM MLB/HR - (Summer) FUEL OIL GAL - COAL TON - OTHERS - - Total $119,112 G.A.I.#09090 Page 16

VII. ANNUAL COST (Continued) BASE SYSTEM: VERTICAL GEOTHERMAL HEAT PUMP UNITS B. SERVICE AND MAINTENANCE COSTS TOTAL SERVICE AND MAJOR EQUIPMENT SERVICE COST MAINTENANCE COST MAINTENANCE COST 1. CHILLERS 0 2. BOILERS 0 3. PUMPS 5,250 4,654 9,904 4. AIR HANDLING 24,500 14,000 38,500 UNITS 5. FANS: Supply 0 Return 0 Exhaust 9,000 9,000 6. SPLIT & 0 UNITARY EQUIPMENT 7. THRU THE WALL N/A UNITS-PACKAGED TERMINAL AIR CONDITIONING UNITS 8. HEAT PUMPS 35,000 19,000 54,000 9. TERMINAL UNITS (VAV 0 BOXES, FCU, ETC.) G.A.I.#09090 Page 17

VII. ANNUAL COST (Continued) BASE SYSTEM: VERTICAL GEOTHERMAL HEAT PUMP UNITS B. SERVICE AND MAINTENANCE COSTS (Cont'd) TOTAL SERVICE AND MAJOR EQUIPMENT SERVICE COST MAINTENANCE COST MAINTENANCE COST 10. HOT WATER CONVERTORS, 2,000 5,000 7,000 FTR, UHs, CUHs, ETC. 11. COOLING 0 TOWERS 12. DOMESTIC WATER 0 HEATERS 13. TEMPERATURE CONTROL 17,500 12,500 30,000 SYSTEM 14. MISCELLANEOUS 0 EQUIPMENT WATER TREATMENT TOTAL 84,250 64,154 $148,404 G.A.I.#09090 Page 18

VII. ANNUAL COST (Continued) ALTERNATE NO.: 1 FOUR-PIPE VERTICAL FAN-COIL UNITS B. SERVICE AND MAINTENANCE COSTS TOTAL SERVICE AND MAJOR EQUIPMENT SERVICE COST MAINTENANCE COST MAINTENANCE COST 1. CHILLERS 17,500 11,000 28,500 2. BOILERS 10,000 15,000 25,000 3. PUMPS 10,000 10,939 20,939 4. AIR HANDLING 24,500 14,000 38,500 UNITS 5. FANS: Supply - Return - Exhaust 9,000 9,000 6. SPLIT & UNITARY 7,000 7,000 EQUIPMENT 7. THRU THE WALL N/A UNITS-PACKAGED TERMINAL AIR CONDITIONING UNITS 8. HEAT PUMPS N/A 9. TERMINAL UNITS (VAV 40,000 22,000 62,000 BOXES, FCU, ETC.) G.A.I.#09090 Page 19

VII. ANNUAL COST (Continued) ALTERNATE NO. : 1 FOUR-PIPE VERTICAL FAN-COIL UNITS B. SERVICE AND MAINTENANCE COSTS (Cont'd) TOTAL SERVICE AND MAJOR EQUIPMENT SERVICE COST MAINTENANCE COST MAINTENANCE COST 10. HOT WATER CONVERTORS, 2,000 5,000 7,000 FTR, UHs, CUHs, ETC. 11. COOLING 5,000 7,000 12,000 TOWERS 12. DOMESTIC WATER 0 HEATERS 13. TEMPERATURE CONTROL 19,000 26,000 45,000 SYSTEM 14. MISCELLANEOUS 0 EQUIPMENT TOTAL $128,000 $126,939 $254,939 G.A.I.#09090 Page 20

VII. ANNUAL COST (Continued) ALTERNATE NO. : 2 FOUR-PIPE VARIABLE AIR VOLUME UNITS B. SERVICE AND MAINTENANCE COSTS TOTAL SERVICE AND MAJOR EQUIPMENT SERVICE COST MAINTENANCE COST MAINTENANCE COST 1. CHILLERS 17,500 11,000 28,500 2. BOILERS 10,000 15,000 25,000 3. PUMPS 10,000 11,670 21,670 4. AIR HANDLING 24,500 14,000 38,500 UNITS 5. FANS: Supply - Return - Exhaust 9,000 9,000 6. SPLIT & UNITARY 7,000 7,000 EQUIPMENT 7. THRU THE WALL N/A UNITS-PACKAGED TERMINAL AIR CONDITIONING UNITS 8. HEAT PUMPS 0 9. TERMINAL UNITS (VAV 24,000 13,000 37,000 BOXES, FCU, ETC.) G.A.I.#09090 Page 21

VII. ANNUAL COST (Continued) ALTERNATE NO. : 2 FOUR-PIPE VARIABLE AIR VOLUME UNITS B. SERVICE AND MAINTENANCE COSTS (Cont'd) TOTAL SERVICE AND MAJOR EQUIPMENT SERVICE COST MAINTENANCE COST MAINTENANCE COST 10. HOT WATER CONVERTORS, 2,000 5,000 7,000 FTR, UHs, CUHs, ETC. 11. COOLING 0 TOWERS 12. DOMESTIC WATER 0 HEATERS 13. TEMPERATURE CONTROL 19,000 26,000 45,000 SYSTEM 14. MISCELLANEOUS 0 EQUIPMENT TOTAL 107,000 111,670 218,670 G.A.I.#09090 Page 22

VII. ANNUAL COST (Continued) ALTERNATE NO. : 3 STANDARD VERTICAL WATER SOURCE HEAT PUMP UNITS B. SERVICE AND MAINTENANCE COSTS TOTAL SERVICE AND MAJOR EQUIPMENT SERVICE COST MAINTENANCE COST MAINTENANCE COST 1. CHILLERS 0 2. BOILERS 5,000 2,000 7,000 3. PUMPS 8,000 5,654 13,654 4. AIR HANDLING 24,500 14,000 38,500 UNITS 5. FANS: Supply - Return - Exhaust 9,000 9,000 6. SPLIT & N/A UNITARY EQUIPMENT 7. THRU THE WALL N/A UNITS-PACKAGED TERMINAL AIR CONDITIONING UNITS 8. HEAT PUMPS 35,000 19,000 54,000 9. TERMINAL UNITS (VAV 0 BOXES, FCU, ETC.) G.A.I.#09090 Page 23

VII. ANNUAL COST (Continued) ALTERNATE NO. : 3 STANDARD VERTICAL WATER SOURCE HEAT PUMP UNITS B. SERVICE AND MAINTENANCE COSTS (Cont'd) TOTAL SERVICE AND MAJOR EQUIPMENT SERVICE COST MAINTENANCE COST MAINTENANCE COST 10. HOT WATER CONVERTORS, 2,000 5,000 7,000 FTR, UHs, CUHs, ETC. 11. COOLING 5,000 2,000 7,000 TOWERS 12. DOMESTIC WATER 0 HEATERS 13. TEMPERATURE CONTROL 17,500 12,500 30,000 SYSTEM 14. MISCELLANEOUS 0 EQUIPMENT WATER TREATMENT TOTAL 97,000 69,154 166,154 G.A.I.#09090 Page 24

VIII. SUMMARY A. LIFE CYCLE COST ANALYSIS PROJECT: MT. AIRY USING AGENCY DATE MIDDLE SCHOOL CARROLL COUNTY OCTOBER, 2010 LOCATION: PUBLIC SCHOOLS CARROLL COUNTY BASE SYSTEM ALTERNATIVE ALTERNATIVE ALTERNATIVE GEOTHERMAL NO. 1 NO. 2 NO. 3 HP 4-PIPE FCU 4 - PIPE VAV STANDARD WSHP INITIAL COST - MECHANICAL INSTALLATION $5,125,300 $4,775,300 $4,765,300 $4,925,300 - INCREMENTAL COST OF $115,000 $105,000 $115,000 ARCHITECTURAL COMPONENTS (+ OR - OVER BASE SYSTEM) - INCREMENTAL COST OF $10,000 $10,000 $10,000 STRUCTURAL COMPONENTS (+ OR - OVER BASE SYSTEM) - INCREMENTAL COST OF ELECTRICAL COMPONENTS ($20,000) ($20,000) $15,000 (+ OR - OVER BASE SYSTEM) (a) TOTAL INITIAL COST $5,125,300 $4,880,300 $4,860,300 $5,065,300 ANNUAL COSTS - ENERGY $100,198 $112,505 $115,048 $119,112 - SERVICE $84,250 $128,000 $107,000 $97,000 - ROUTINE MAINTENANCE $64,154 $126,939 $111,670 $69,154 (b) TOTAL ANNUAL COST $248,602 $367,444 $333,718 $285,266 (c) PRESENT VALUE OF TOTAL $7,465,518 $11,034,343 $10,021,552 $8,566,538 ANNUAL COST (b x P.W. Factor of 30.03) TOTAL LIFE CYCLE COST (a + c) $12,590,818 $15,914,643 $14,881,852 $13,631,838 RECOMMENDED SYSTEM: BASE SYSTEM: $12,590,818 The Geothermal Heat Pump System is recommended based on the total Life CycleCost; however, it remains the highest installation cost. G.A.I.#09090 Page 25

VIII. SUMMARY (cont.'d) B. ENERGY CONSUMPTION ANALYSIS FOR ENTIRE FACILITY ANNUAL ENERGY CONSUMPTION (BTU'S) SELECTED MECHANICAL SYSTEM* (EXCLUDING LIGHTING RECEPTACLES/ AND RECEPTACLES) LIGHTING MISCELLANEOUS TOTAL ELECTRIC POWER 1,976,939,294 1,823,199,888 1,037,672,276 4,837,811,458 GAS 0 FUEL OIL 0 COAL --- --- --- 0 OTHERS --- --- --- 0 TOTAL BTU'S 1,976,939,294 1,823,199,888 1,037,672,276 4,837,811,458 BUILDING AREA (NET SQUARE FT.) 117,000 117,000 117,000 117,000 ANNUAL KWH/SQ. FT. 4.95 4.57 2.59 12.11 ANNUAL BTU/SQ. FT. 16,897 15,583 8,869 41,349 EPI (TOTAL ANNUAL BTU/SQ. FT. = 41,349 FROM ABOVE) NOTES: 1. *This number reflects the State of Maryland Technology Requirements Standards for Information and Communication Distribution Systems, and Education Specification Requirements 2. Conversion: 1 KWH = 3413 BTU. 2000 hours per year of operation. 3. KWH/sq.ft. shall apply to electricaloeprated equipment (i.e., motors, electric heating elements, etc.) lighting fixtures, receptacles, and hard connected appliances and equipment. 4. Energy Performance Index (EPI) for buildings shall not exceed the maximum values listed on the EPI Table in the Energy Conservation Guidelines for State Buildings. G.A.I.#09090 Page 26

LIFE CYCLE COST ANALYSIS MECHANICAL CONSTRUCTION COST The Life Cycle Analysis is a comparison of systems which can successfully be applied to a unique facility. Depending on the building layout, flexibility of the design, location on the site, utilities available, and other factors, certain systems will have advantages over other systems. Since none of these systems are fully designed, the cost estimates for each alternative is compared to the Base System and incremental differences for each Alternative are developed. It is intended that the system design approach is consistent for all Alternatives. The following is a brief description of equipment, which would be employed in each of the systems being analyzed. Plumbing equipment and cost, as well as fire protection systems, remain unchanged, regardless of the system alternative. G.A.I.#09090 Page 27

BASE SYSTEM GEOTHERMAL HEAT PUMPS 2 Main Geothermal Circulating Pumps +/-50 Water-to-Air Heat Pumps 14 Energy Recovery Units 220 400 Feet Deep Bore Holes with 1 Tubing, 6 Diameter ALTERNATE NO. 1 FOUR-PIPE FAN-COIL SYSTEM 4 Cast Iron Boilers with Flues 2 Primary Heating Water Pumps 2 Secondary Heating Water Pumps 1 Water-Cooled Centrifugal Chillers 2 Primary Chilled Water Pumps 2 Secondary Chilled Water Pumps +/-50 Four-Pipe Fan-Coil Units 14 Energy Recovery Units (4-Pipe) Total Deduct Cost From Base System ($350,000) G.A.I.#09090 Page 28

ALTERNATE NO. 2 FOUR-PIPE VAV SYSTEM 4 Cast Iron Boilers with Flues 2 Primary Heating Water Pumps 2 Secondary Heating Water Pumps 1 Water-Cooled Centrifugal Chillers 2 Primary Chilled Water Pumps 2 Secondary Water Pumps +/-50 Fan-Powered Terminal VAV Boxes 4 Constant Volume AHU s (4-Pipe) 10 VAV AHU s (4-Pipe) Total Deduct Cost from Base System ($360,000) ALTERNATE NO. 3 STANDARD WATER SOURCE HEAT PUMP 2 Main Water Source Circulating Pumps 1 Open Cooling Towers 1 Flat Plate Heat Exchangers 2 Condenser Water Pumps 2 Cast Iron Boilers 2 Heating Water Pumps 1 Shell and Tube Heat Exchangers +/-50 Water-to-Air Heat Pumps 14 Energy Recovery Units Total Deduct Cost From Base System ($200,000) G.A.I.#09090 Page 29

MAINTENANCE COST SUMMARY ASHRAE MAINTENANCE COST (2003 APPLICATIONS) BASE SYSTEM = 0.3338 / SQUARE FOOT Includes: Heating = Fire Tube Boilers Cooling = Centrifugal Chillers Distribution = Variable Air Volume Equation: C = 0.3338 +.0018N + h + c + d C = Total Annual Building HVAC Maintenance Cost + Age Adjustment Factor x Age in Years (N) + Heating System Adjustment Factor (h) + Cooling System Adjustment Factor (c) + Distribution System Adjustment Factor (d) N = 45 Years I. For Heat Pumps (Geo & Standard WSHP) C = 0.3338 +.0018(45) + (-.0969) + (-.0472) + (-.027) C = 0.2437 / Square Foot II. For 4-Pipe FCU s C = 0.3338 +.0018(45) +.0094 + 0 +.0580 C = 0.4822 / Square Foot III. For VAV C = 0.3338 +.0018(45) +.0094 + 0 + 0 C = 0.4242 / Square Foot G.A.I.#09090 Page 30

Geothermal Heat Pumps and Standard Water Source Heat Pumps C = (0.2437/square foot) x (117,000 square foot) = $28,513 (in 1983 Dollars) $28,513 x 225% = $64,154 (in 2010 Dollars) For 4-Pipe FCU C = (0.4822/square foot) x (117,000 square foot) = $56,417 (in 1983 Dollars) $56,417 x 225% = $126,939 (in 2010 Dollars) For VAV System C = (0.4242/square foot ) x (117,000 square foot) = $49,631 (in 1983 Dollars) $49,631 x 225% = $111,670 (in 2010 Dollars) CPI 2009 = 215 CPI 1983 = 98 117% by 2010, say 125% increase G.A.I.#09090 Page 31