ASHRAE Student System Selection Competition New Office Building - Nashville, Tennessee Spring 2009

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1 ASHRAE Student System Selection Competition New Office Building - Nashville, Tennessee Spring 2009 Kansas State University Department of Architectural Engineering and Construction Science 240 Seaton Hall Manhattan, KS 66506

2 Prepared By: Kelly Griffith 5 th Year Architectural Engineering Anticipated Graduation: Dec West 146 th St. Gardner, KS kgriffi2@ksu.edu James Newman 5 th Year Architectural Engineering Anticipated Graduation: Dec 2009 R.R. 2 Box 136 Hoxie, KS newmy@ksu.edu Phillip Podlasek 5 th Year Architectural Engineering Anticipated Graduation: May West 61 st St. Shawnee, KS philpodlasek@gmail.com Darren Rottinghaus 5 th Year Architectural Engineering Anticipated Graduation: May H Road Seneca, KS drr@ksu.edu ii

3 Faculty Advisors: Fred Hasler, P.E., LEED AP Assistant Professor Department of Architectural Engineering Kansas State University 249 Seaton Hall Manhattan, KS Julia Keen, P.E., HBDP Assistant Professor Department of Architectural Engineering Kansas State University 248 Seaton Hall Manhattan, KS Signatures Date Kelly Griffith James Newman Phillip Podlasek Darren Rottinghaus Fred Hasler Julia Keen iii

4 TABLE OF CONTENTS List of Tables... vi List of Figures... vi 1.0 Executive Summary Introduction Building Description Design Parameters ASHRAE Standards Standard Standard Standard Load Concepts Pressurization Zoning Descriptions of Systems Considered Baseline: Packaged Rooftop Air Conditioners Option 1: Ice Storage Packaged Rooftop Units Major Components Ventilation Operations Option 2: Ground Source Heat Pumps Major Components Ventilation Option 3: Radiant Heating and Cooling Major Components Ventilation Condensation Prevention Life Cycle Cost Analysis First Cost Operating Cost Replacement Cost Maintenance Cost Year Life Cycle Cost Decision Matrix Design Criteria Performance Requirements Capacity Requirements Spatial Requirements First Cost Operating Cost iv

5 5.1.6 Reliability Flexibility Maintainability Sustainability Major Design Goals Low Environmental Impact Low 20 Year Life Cycle Cost Comfort and Health Creative High Performance Green Design Synergy with Architecture Conclusion and Recommendation Recommendations Innovative Ideas REFERENCES Appendix A System Schematics Appendix B Zone Maps Appendix C Initial Cost Comparisons Appendix D Lifecycle Cost Comparisons Appendix E TRACE 700 Inputs v

6 LIST OF TABLES Table 1 Design Conditions... 2 Table 2 Interior Design Loads... 3 Table 3 Schedule of Operations Table 4 Utility Rate Structures Table 5 System Operating Schedules Table 6 System 1 Alternative Energy Plan Table 7 Design Criteria Matrix Table 8 Major Design Goals Matrix Table 9 Final System Selection LIST OF FIGURES Figure 1 Forced Air vs. Radiant Heat Figure 2 Ice Storage w/ Rooftop A/C... 6 Figure 3 Energy Recovery Ventilator... 7 Figure 4 Ice Unit Operations Diagram Figure 5 GSHP Heat Transfer Figure 6 Anatomy of a Heat Pump... 9 Figure 7 Radiant Cooling Ceiling Panel Figure 8 Radiant Floor Detail Figure 9 Radiant Window vi

7 1.0 EXECUTIVE SUMMARY The objective of this proposal is to evaluate, compare and select the best HVAC system for the office building located in Nashville, Tennessee. To complete this task, the engineer must become very familiar with the building s physical parameters, the functionality of the spaces, and site conditions. Next, an understanding of the design criteria and major goals outlined by the owner and architect need to be analyzed to better understand what limitations exist, and what expectations are to be met. The building is then zoned and the system loads are calculated using Trane TRACE 700. Once all the required information is gathered as outlined above, it is further analyzed to determine the three most suitable HVAC options. This is done by comparing the load parameters and given physical constraints to the goals and criteria set forth by the owner and architect. In this case the focus is primarily on sustainability goals, two different occupant schedules, lifecycle costs, and creative high performance design that exceeds ASHRAE Standard 90.1 minimums. The three systems selected to be analyzed for the new office building are ice storage packaged rooftop units, ground source heat pumps, and radiant heating and cooling. With the systems selected, a simultaneous process of considering system enhancements and checking for code compliance is executed. To accomplish this, Appendix G of ASHRAE Standard 90.1 was referenced to determine what baseline system would be used for comparison. Several system enhancements are considered including energy recovery ventilators, CO 2 sensors, radiant windows, and variable frequency drives on motors. In addition to more efficient equipment, these options are placed on specific systems to ensure operations that exceed ASHRAE Standard 90.1 by 20% as defined in the selection criteria. After all the system components are determined along with the method of control, a detailed energy consumption analysis is created using Trane TRACE 700. This information is then used to develop each system s operating costs. Initial costs for each system are estimated using R.S. Means Mechanical Cost Data; and with the aid of engineering economics, a 20 year life cycle cost is determined. To adequately compare each system, two matrices were created; one for the major design goals and one for the design criteria. In these matrices, items were given proportional values for comparison based on the importance outlined by the owner and architect. A rating system of 1-10 was applied to each system for each item, with 10 being the best. Ultimately the final conclusion for the best HVAC system came from totaling the ranked points, and selecting the system with the highest value. The ground source heat pump system resulted in the highest score among the systems. A few of the major advantages to this system are flexibility, redundancy, low environmental impact, and the lowest 20-year life cycle cost of the three systems. The system is the most flexible for adaptations in the retail tenant spaces, and becomes extremely redundant by serving each occupant zone with a separate heat pump. With the system being the most efficient of the three proposed it has the lowest 20-year life cycle cost. This, along with the fact that no carbon emissions are produced and no ozonedepleting refrigerant is used, creates a system with a very low environmental impact. This design is highly green and has the potential to achieve many LEED points. Finally, this system has a better synergy with architecture than the other two systems. 2.0 INTRODUCTION The intention of this proposal is to analyze and select the HVAC system that best suits the defined three story office building located in Nashville, Tennessee. In order to choose the ideal system, this proposal analyzed three options described in Section 3.0. Each alternative was then evaluated using weighted design criteria and major design goals as discussed in section 5.0. The following sections discuss the particular building being considered, codes being utilized for design, and some particular aspects of the required HVAC system design. 1

8 2.1 Building Description The new office building is a three-story, multipurpose building in Nashville, Tennessee. The first floor is 5,600 square feet and consists of an open-air parking garage, main street level entrance, storage and mechanical space. The second floor is 5,028 square feet and is composed of approximately 50% unfinished tenant space and 50% office space. The third floor is 5,028 square feet and is entirely office space. There is also a 592 square foot terrace located on the roof that does not require any mechanical conditioning as it is only to be occupied during mild weather. Per the owner s requirements, separate metering does not have to be offered for multiple tenants. Tenants are subject to monthly utility costs based on square footage. 2.2 Design Parameters The design parameters for the building s heating and cooling requirements are based on 2005 Fundamentals of ASHRAE Handbook, ASHRAE Standards , , , and Exhibit 2 Design Information and Assumptions from the ASHRAE website. The outdoor and indoor design conditions are listed below in Table 1. Summer Winter 1% Cooling Design DB Nashville, TN 1% Cooling Design MWB Daily Range Indoor Condition (1) New Office Building Setback Temperature (2) Tempered Space Condition (3) 92 F 75.2 F 18.6 F 75 F DB, 50% RH 80 F 85 F 99% Heating Design 1% Wind Design Indoor Condition (1) Setback Temperature (2) Tempered Space Condition (3) 16.7 F 22.1 MPH 72 F 67 F 62 F (1) Indoor temperature and humidity set points are for occupied hours. (2) Setback temperatures are the thermostatic set points for unoccupied hours. (3) Tempered space conditions are the thermostatic set points of the equipment, stairway, and storage spaces not occupied continuously. Table 1 Design Conditions, produced from ASHRAE Design Competition 2009 Website. The building occupancy schedules include the following: Office: 8 A.M. to 5 P.M., Monday through Friday Retail/Tenant: 9 A.M. to 9 P.M., Monday through Saturday The building ventilation criteria are based on ASHRAE Standard using the space-by-space method. The following utilities are available on site: natural gas provided at 5 psig, city water at 80 psig, city sewer and electrical power provided at 480/3Ø. The utility capabilities are assumed to adequately support the proposed systems. For specific utility rate information see Table 4 in Section 4.2. The building s interior design loads are listed in Table 2, on the next page. 2.3 ASHRAE Standards The ASHRAE Standards are a set of guidelines used to measure building performance. ASHRAE Standard 55 covers criteria on occupant comfort, Standard 62.1 sets forth minimum ventilation requirements for acceptable indoor air quality, and Standard 90.1 defines minimums for energy efficient operations Standard 55 ASHRAE standard 55 is written to provide acceptable thermal comfort for the majority of the occupants based on the combination of indoor environmental factors and personal factors. The six primary factors addressed in defining thermal comfort are: metabolic rate, clothing insulation, air temperature, radiant temperature, air speed and humidity. While all of these factors vary over time, a steady state is used to find thermal comfort conditions. As these factors vary from steady state, occupants may not feel immediately comfortable, especially when entering the space from a different environment and activity level. 2

9 Space Occupancy Lighting (W/SF) Power Office Per Exhibit W/SF Retail 25 SF/person W/SF Equipment Parking Garage Stairs Conference Rooms 20 SF/person W/SF Break Room 9 SF/person BTU/h (1)(3) Coffee BTU/h (4) Plotting W Men/Women Elevator Reception 33.3 SF/person W (2) Lobby 100 SF/person Corridors Storage (1) Power load consists of a large refrigerator, dishwasher and microwave. (2) Power load consists of computer and desktop copier/printer. (3) Value consists of the total BTU/h of heat gain, sensible load = 4490 BTU/h, latent load = 420 BTU/h. (4) Value consists of the total BTU/h of heat gain, sensible load = BTU/h, latent load = 790 BTU/h. Table 2 Interior Design Loads To ensure that comfort exists for the majority of occupants in the new office building, design parameters were compared to Figure of ASHRAE Standard 55 for compliance. By using a thermostatic set point of 75 F and a relative humidity of 50%, it was found that 80% of the occupants having a clothing factor between 0.5 and 1.0 with a metabolic rate between 1.0 and 1.3 would be comfortable. Air velocity was verified to be maintained between 30 and 40 feet per minute from Figure of Standard 55. This air velocity is utilized to reduce drafts and maintain a comfortable environment for occupants Standard 62.1 ASHRAE Standard 62.1 is used to specify minimum ventilation rates and acceptable indoor air quality to minimize adverse health effects on the occupants. Section 6 from Standard 62.1 outlines the procedure for determining the proper ventilation rate for each method of outdoor air delivery. From Standard 62.1, Table 6-1 was used to determine the required outdoor air for each room and Table 6-4 was used to determine the minimum exhaust rates for rooms requiring exhaust. For the multiple zone re-circulating system, the total outdoor air required is greater than that of the 100% outdoor air delivery system. Where zone delivery is being utilized, the zone cubic feet per minute (cfm) was determined by calculating which room under that zone has the greatest percent demand of outdoor air and that percentage was then applied to the total zone supply air cfm Standard 90.1 ASHRAE Standard 90.1 is used to provide minimum performance requirements for the energy efficient design of buildings. As it pertains to this project, the performance rating method in Appendix G of Standard 90.1 was used to verify that each system being compared would be 20% more energy efficient than the baseline system. Trane TRACE 700 was used to model the energy consumption of each system. Each system used the same weather data and energy rates. Also, each system was modeled to meet the mandatory requirements of Standard 90.1, Sections 5.4, 6.4, 7.4, 8.4, 9.4, and The baseline system was determined using ASHRAE Standard 90.1 Table G3.1.1A in Appendix G. The new office building is 16,248 sq ft and is three floors in height. Therefore, Option 3 (packaged rooftop air conditioners) is required as the baseline system. The packaged rooftop unit is to be constant volume with direct expansion (dx) cooling and natural gas furnace heating. As required, all baseline system equipment was modeled to meet the minimum Energy Efficiency 3

10 Ratings (EER) and Coefficients of Performance (COP) found in Tables 6.8.1A thru 6.8.1J of Standard Economizer options are not required per Table G Aof Standard Since the other systems do not have any natural gas consumption, the baseline natural gas consumption is converted into equivalent kilowatt-hours (kwh) using the conversion: 1 therm of natural gas = 29.3 kwh. 2.4 Load Concepts In order to make an accurate system selection, heating and cooling loads for the building were calculated using Trane TRACE 700. The design parameters, as defined in Section 2.2, were first entered into the program. Schedules and wall construction types were then created to accurately model the building s occupancy schedule, energy consumption and building materials. The wall and roof constructions were established using the architectural wall and roof sections provided. Since exact window construction was not defined, percent fenestration dictated construction values per ASHRAE Standard Rooms were then individually input including each spaces area, envelope construction, airflows and internal loads. Ventilation rates were determined using ASHRAE Standard 62.1 and internal loads were calculated referencing equipment, lighting, and occupant loads from the 2005 ASHRAE Fundamentals. The heating and cooling system, building zones as described in Section 2.6, and plant components were entered to correctly model the operation of the baseline system per ASHRAE Standard The software is able to find the peak and block loads for the system being analyzed and can also compute the hour, day, and month of the peak loads. Trane TRACE 700 also calculates loads for each room, zone and system. Once the three system options were defined, the system and plant information was input for each system, as with the baseline system. The cooling load for the baseline system was calculated to be 35.5 tons. The load for the first, second and third options were calculated to be 30.4 tons, 33.0 tons and 32.4 tons, respectively. The ranges in system loads are due to differences in equipment types and configurations. 2.5 Pressurization Overall building pressurization is an important aspect of any building. Maintaining a slightly positive pressure reduces infiltration into the space. This allows for a more accurate calculation of the HVAC loads and therefore a more precise HVAC design. It also reduces the damage related to the infiltration of humid air. A few important spaces in this building must maintain a specific pressure differential for occupant safety and comfort. All of the rooms adjacent to the parking garage on the first floor must maintain a higher pressure with respect to the garage to keep vehicle exhaust and odors from entering into the building. The garage is considered to be open according to ASHRAE Standard 62.1 because of the size of the openings to atmosphere and therefore does not need mechanical ventilation. As a result, the adjacent spaces are slightly positively pressurized by supplying more outside air than what is being exhausted. Some spaces require a net negative pressure such as toilet rooms and janitor s closets. This is done to evacuate any potential odors or harmful vapors and to prevent them from moving to other areas of the building. Air is exhausted at a higher cfm than is supplied to maintain negative pressure. To ensure that these spaces do not become too negatively pressurized, transfer ducts and grilles are provided. The exhaust fans operate only when the building is occupied to maintain the proper building pressure during off hours when no outside air is being supplied. This can be done because the odors will not accumulate to an unacceptable level in spaces that need to be exhausted when they are not in use and there are no hazardous vapors to address. 2.6 Zoning Two different types of occupancies are included in this building, office and tenant space. These spaces are separated due to differences in ventilation requirements, possible separate metering by the owner and the tenant, and schedule variations. Throughout this analysis, it is assumed that the tenant space is to be used for retail purposes due to the given information. Ventilation rates for retail space are greater than for offices because of people density, therefore creating a more conservative value. The occupancy for each room was calculated using a combination of the architect s furniture plan and ASHRAE Standard s occupant densities as indicated on Table 2 under Section 2.2. Typically with office spaces in the winter, perimeter zones will require heating while interior zones may need cooling. This was accounted for by zoning interior rooms separate from exterior rooms. Exterior zones were then further divided up by their exposure and usage. Spaces located on each corner of the building were given an independent zone since they 4

11 have multiple exposures. Interior zones were similarly separated depending on the type of room. The first floor consists of only one zone, excluding the stairs and elevator shaft, because the lobby is the only room on the first floor that requires total conditioning. The other rooms just need to be tempered since they are for storage and equipment uses only. The stairs also need to be tempered but due to the height of the stairwells, heat must be supplied at the bottom of the stairs and cooling at the top. This naturally allows the air to rise or fall, depending on its temperature and density, to adequately temper the space. The stairs are therefore separated onto their own zones. While the tenant space was zoned completely separate from the rest of the building, the approach was the same. Interior and exterior rooms were separated and then exterior spaces were broken up by their different exposures. A zoning diagram is located in Appendix B. Thermostat locations were also considered in determining the building s zones. No more than three offices are in a single zone together to increase controllability and comfort. All conference rooms are on their own zones because of the sporadic schedules and occupancies they are known to have. Since the exact floor plan and use of tenant space is yet to be determined, thermostatic locations will be determined once the space is finished. 3.0 DESCRIPTIONS OF SYSTEMS CONSIDERED Many systems and configurations were considered for the initial proposal for the new office building in Nashville. Several of the options considered could be ruled out due to the small load requirements including co-generative capabilities, and absorption and centrifugal chillers. The warmer climate of this location eliminates the practicality of solar wall systems. Asphalt thermal collectors would not work for this situation due to the lack of an exposed parking lot or alternate location that the collectors could work adequately. Due to the large latent loads from the outside air, additional system options such as heat pipes, fixed-plate heat exchangers and coil loops were eliminated because they do not account for these loads. Other options were removed because they were not aesthetically pleasing or complimentary to the architecture. Those systems eliminated include packaged terminal air conditioners and radiators. The first system option was intended to be one that might be commonly applied to a building of this type. Packaged rooftop units have a low first cost and are readily available in most locations making them a viable option for most owners. Specialized rooftop units with thermal storage were then chosen to take advantage of the reduced utility rates during off peak hours. The special unitary ice making equipment works well with the new office building as they are designed to handle smaller building loads, on the order of approximately 5-10 tons per rooftop unit, and can be mounted on the roof working well with the building floor plan and nearly no mechanical room space. Also, it was noticed that the building operational schedule would allow for enough off-peak time to make a system like this plausible. Variable air volume (VAV) boxes equipped with electric reheat were located at each zone to satisfy the needs of this building. This system is further described in Section 3.2. Several alternatives were explored in deciding upon the second system option, ground source heat pumps. Water source heat pumps were seriously considered for this comparison and even though they have a lower first cost, they were not determined to be as beneficial in the long run due to a higher operating cost. A dx ground source heat pump and hybrid systems are available in addition to the conventional ground source heat pump. While the dx ground source heat pump system needs less bores and smaller pipe sizes, the high cost of copper, potential for pipe corrosion, and possibility of large refrigerant leaks contaminating the local environment are all too high of a concern for this building. Figure 1 Forced Air vs. Radiant Heat (Reproduced from Young and Sons HVAC: Furnaces and Radiant Heating). Hybrid ground source heat pumps can be advantageous in certain applications but were not as favorable as straight ground source for this particular building. This system is meant for more severe climates where heating and cooling values are greatly unbalanced which is not the case for this location. Ultimately, the conventional ground source heat pump system was selected for the second option in the comparison. This option is further described in Section

12 The third system option is a little less conventional but was selected due to its superior human comfort. Radiant systems provide more uniform heating and cooling to the space and reduce noise and drafts that are associated with air-based HVAC systems. The reduction of drafts in the building allows the temperature in each space to be set higher for cooling and lower for heating without sacrificing comfort. This reduces heat loss or gain and lowers energy consumption of fans and pumps. Figure 1, on the previous page, shows the more uniform heat distribution and reduction of drafts of the radiant heating system. The radiant cooling system is very similar in terms of uniformity and drafts. This option is further described in Section 3.4. Once these system ideas were narrowed down, they were developed into overall system concepts. Components and controls were selected to work best for the application. From there, each system could be compared to one another according to the design criteria and goals as described in Section 5.0. The three systems considered, as well as the baseline system from ASHRAE 90.1, are described in the following sections. 3.1 Baseline: Packaged Rooftop Air Conditioners In order to accurately evaluate and compare the energy efficiency of the three options, a baseline system must first be created to establish ASHRAE Standard 90.1 minimums. This system becomes the model for which each system must consume at least 20% less energy than. The baseline system shows compliance with the mandatory provisions by using templates and efficiencies available in Trane TRACE 700 to match Standard 90.1 minimum EER and COP ratings. The baseline system consists of five packaged rooftop units (RTU), two for the tenant spaces and three for the office spaces. Each rooftop unit consists of dx cooling and natural gas furnace heating. According to ASHRAE Standard 90.1, this building is located in climate zone 4a; therefore, preheat coils and economizer modes are not required. This system becomes a great baseline for comparison as it is a system that is readily available with a low first cost. 3.2 Option 1: Ice Storage Packaged Rooftop Units The first option considered for the new office building is a thermal storage system in conjunction with VAV RTU s and zone-level VAV boxes with electric reheat. A system schematic can be found in Appendix A.1 for a visual description of the equipment and operations Major Components Each RTU will have one or more dedicated ice units. The ice unit is a dx-based system that creates ice during off peak utility rate hours as a source for cooling during onpeak utility rate hours. Each ice unit has a thermal storage capacity of 5 tons and provides 30 ton/hrs of cooling. The rooftop units are coordinated with the ice unit manufacturer to include a special liquid overfeed coil (ice coil), which is in addition to the standard dx cooling coil. See Figure 2, left, for integration of the ice coil. The system has both coils for separate cooling modes and to provide redundancy. Figure 2 Ice Storage w/ Rooftop A/C (Reproduced from /resources/tabid/54/default.aspx) Each RTU serves several zones. Each zone will have one VAV box that has an electric reheat coil, allowed per Section of ASHRAE Standard The RTU will supply 56 F air, as calculated from a psychrometric chart, using building design conditions. The VAV box will modulate airflow as demanded by the space thermostat. Only when the damper in the VAV box reaches its minimum position will the reheat coil be used to heat the air being delivered to the 6

13 space. The minimum position is different for each VAV box, as each zone has a different outdoor air and heating load requirement. The minimum damper position is set to the higher of the two requirements. All return air is routed back to the RTU, where control dampers will modulate such that the appropriate amount of air is returned and the remaining air is sent through an energy recovery ventilator (ERV), to maintain proper building pressurization as mentioned in Section Ventilation The ventilation for this system was calculated to comply with ASHRAE Standard 62.1 and utilizes the multiple zone re-circulating system calculation method. Each RTU is coupled with an ERV. The exhaust/relief air enters the ERV and passes through the energy recovery wheel. The wheel slowly rotates from the exhaust/relief air path into the incoming outdoor air path. Sensible and latent heat is transferred between the air streams preconditioning the outdoor air and saving energy. Figure 3, right, illustrates a section through an ERV Operations Based on the hours of operation for the building, and the times of the year when the utility company provides discounted rates for offpeak operation, three operational modes arise. The operation schedule is outlined in Table 3, below. Each RTU is supplied with enough storage capacity to meet onpeak loads. Therefore the dx cooling system operates during the charging cycle and during off peak rate hours (Mode 1). During peak utility rates, the ice unit operates in cooling mode to handle the cooling demand (Mode 2). When off peak utility rates are in effect during occupied hours, ice cooling mode takes priority over operation of the dx cooling system within the RTU. During unoccupied and off utility rate hours, ice make mode is executed and the dx cooling system within the RTU operates as necessary to maintain thermostat set points (Mode 3) Ice Cooling Mode (Mode 2) During ice cooling mode, the internal condensing unit is off. A refrigerant pump located within the ice unit, circulates refrigerant through the system s heat exchanger and the ice coil, located in the RTU. This process is regulated by the refrigerant management system. The main function of the refrigerant management system is to maintain a fixed amount of refrigerant level in the heat exchanger, to ensure that all refrigerant is kept at the temperature and pressure needed for operation. As air passes over the ice coil, sensible and latent heat is extracted from the air stream to maintain a constant supply Figure 3 Energy Recovery Ventilator (Reproduced from Trane, 2009: TRACE 700 Users Manual) Onpeak Hours Offpeak Hours May - September Weekdays 10 A.M P.M. 10 P.M A.M. Ice Unit Runs to Charge Tank (Mode 3) RTU Runs to Meet Load (Mode 1) Ice Storage Runs to Meet Load 10 A.M. 10 P.M. (Mode 2) Table 3 Schedule of Operations. October - April Weekdays 6 A.M P.M. 4 P.M P.M. 10 P.M. - 6 A.M. 12 P.M. - 4 P.M. 10 P.M. 7 A.M. 10 P.M. 6 A.M. 7 A.M. 10 A.M. 12 P.M. 4 P.M. 6 A.M. 12 P.M. 4 P.M. 10 P.M. temperature of 56 F. The refrigerant returning to the ice unit is in a mixed phase; part liquid and part vapor. The vapor is delivered to the top header of the storage heat exchanger where it condenses to a liquid. To complete the cycle, liquid refrigerant from the receiver combines with the condensed refrigerant from the heat exchanger and is pumped back to the ice coil. 7

14 Ice Make Mode (Mode 3) During the ice make mode, the internal condensing unit provides high pressure, low temperature R- 410A refrigerant to the ice storage tank via the refrigerant management system. The refrigerant evaporates as it moves up the circuits in the storage tank, absorbing heat from the water to form layers of ice. Each 5 ton unit requires approximately 10 hours of operation (variant on ambient temperature) to convert all 3,000 pounds of water into a nearly solid block of ice. Reference the ice unit operations diagram in Figure 4, right. Figure 4 Ice Unit Operations Diagram. Figure 5 GSHP Heat Transfer (Reproduced from McQuay International, 2009: What is a Geothermal Heat Pump System ). 3.3 Option 2: Ground Source Heat Pumps The second option considered for this building is a ground source heat pump (GSHP) system. Figure 5, left, shows the basic concept of using the earth as a heat source and sink for this system. The following sections describe the components and operation of this system. A system schematic drawing illustrating this option can be found in Appendix A Major Components Each zone will have one heat pump that has a reversible refrigeration loop to heat or cool the space. The refrigeration cycle works similarly to a typical cycle except a reversing valve is added to allow the condenser and evaporator coils to switch functions with one another, allowing for heating and cooling operations. The refrigeration cycle is illustrated in Figure 6 on the following page. A ground source water loop will run through a heat exchanger in each heat pump to act as the refrigeration circuit s heat source or sink depending on the system s need. Each heat pump is piped in a direct return loop throughout the building. This was chosen instead of reverse return because of the large amount of piping that can be saved. The length of piping is less in a direct return loop and the size of the piping decreases the farther away from the pump it gets. The piping in a reverse return loop must remain at the constant size it is designed for because the water supply for all heat pumps flows through the entire loop. Also, the water loop has a different pressure loss through each heat pump, so a reverse return loop would not eliminate the necessary balancing valves. Each heat pump would also have a two-way control valve to allow the flow of water through the heat pump only when heating or cooling is needed. Using two-way valves also require the hydronic pumps to be controlled with variable frequency drives (VFD). A bypass could be incorporated into the system instead, but the VFD s save on energy costs by decreasing the flow through the hydronic pumps, reducing energy consumption of the pumps. The ground source water loop is a closed loop and piped in a primary/secondary scheme. This arrangement can have the added benefit of pumping water just through the secondary loop when the return temperature of the building loop is within 8

15 Figure 6 Anatomy of a Heat Pump (Reproduced from HowItWorks/AnatomyofaHeatPump/index.htm? an acceptable operating temperature range. This range is the same range as the supply temperatures that the heat pumps would be selected at, typically between F. This is possible during times when some zones need cooling while others require heating. The primary loop is the ground loop through the well field, while the secondary loop is the building loop through the heat pumps. This arrangement allows the water to be pumped through both loops as one large loop or just through the secondary loop. Two hydronic pumps are included in both primary and secondary loops. Base-mounted, end-suction pumps were selected because of the considerable pressure loss through the two loops and because floor space was readily available in the mechanical room on the first floor. Two pumps add redundancy and prevent the system from being completely inoperable if one pump is not functioning or in need of maintenance. The primary loop is piped through vertical bores located on site near the building. Horizontal trenches were eliminated as an option because of lack of property space. A pond loop was dismissed due to the lack of a body of water. Finally, an open well system was not selected because of the possibility of adverse environmental effects. The vertical bores are approximately 250 feet deep and are spaced at 15 feet on center. Each bore is estimated to provide one ton of cooling Ventilation Because each zone s heat pump only recirculates the air in its zone, two heat pumps were added to operate as dedicated outside air systems (DOAS). Each DOAS unit is equipped with an integral total energy wheel to precondition the outside air. The operations of the energy wheel are similar to that in Option 1 for the ERV. One heat pump supplies outside air to the office spaces, while the other heat pump supplies outside air to the retail spaces. This allows the two types of spaces to operate with different occupancy schedules. The DOAS heat pump for the office spaces is controlled by a time schedule and operates when the office is scheduled to be occupied. The DOAS heat pump for the retail spaces is also controlled by a time schedule, which is a different schedule based on the retail s hours of occupancy. CO 2 sensors were considered for the retail space to lower the ventilation from the large required CFM while at maximum occupancy. This level would be much lower during most hours of operation because the number of occupants may be lower than that designed for at peak occupancy. However, since the DOAS heat pump is either on or off and cannot be modulated, the CO 2 sensors would only be able to tell it whether or not it needs to run. Considering, a few people will most likely be in the retail spaces during all store hours, the CO 2 sensors would provide the same result as a time schedule, but would have increased first costs due to the lack of sensors. Therefore, the schedule was chosen to better suit this application. 3.4 Option 3: Radiant Heating and Cooling The third and final option consists of a radiant floor and window heating system and chilled ceiling panels for cooling. Illustrations for this system s layout are depicted in Appendix A Major Components The air-cooled scroll chiller, located on the roof, is used for its higher ability to perform part-loading during times when the cooling loads are lower than what is designed for. The chiller uses a refrigeration cycle to produce chilled water at 58 F. The water is piped throughout the building to serve the ceiling mounted cooling panels. This water temperature was determined by finding the dew point of the room and comparing it to the chilled water supply temperature. The average dew point of each space was calculated to be 55 F so the chilled water supply temperature was established as 58 F to prevent condensation from forming on chilled ceiling panels. Two chilled water pumps in a parallel configuration pump chilled water throughout the system. As with Option 2, using two provides redundancy and allows the system to operate if one needs to be serviced or replaced. This piping configuration is two-pipe direct return like Option 2 for the same advantage of less piping. 9

16 The radiant ceiling panels are 24 wide so they can fit directly in a 2 x2 ceiling grid system. Depending on the cooling need of each room, panel lengths range from 2 to 10 long in 2 increments. Both supply and return connections are on the same end of the ceiling panel and the pipe runs down and back once through the panel. A cover is provided on the bottom side of the panels to hide the components from view and insulation is provided on the upper side to more efficiently cool the occupied space. Figure 7, right, illustrates the chilled ceiling panel s construction. The piping that serves each chilled ceiling panel contains an automatic pressure-independent balancing valve that limits the amount of chilled water that can flow through each panel. This allows for system balancing and ensures flow through all panels. A two-way modulating control valve is also located on the branch to each panel. This control valve varies the amount of flow through the cooling panels, so as less cooling is needed the control valve closes in response to the demand. This is done through communication with a control panel that receives input from the zone located thermostats. This also gives more precise control than an on/off control valve and keeps the room temperature more constant. Pumps controlled by VFD s are specified to work along with the modulating control valves, enabling the pumps to ramp down and use less energy when less flow is required by the system. Figure 8 Radiant Floor Detail (Reproduced from My Green Home Blog, 2007: Is Radiant Floor Heating For You? ). Figure 7 Radiant Cooling Ceiling Panel (Reproduced from Mumma, 2002: Chilled Ceilings in Parallel with Dedicated Outside Air Systems: Addressing the Concerns of Condensation, Capacity, and Cost ). The electric boiler, located in the garage level mechanical room, is utilized due to its high efficiency and compact size, allowing it to fit in the mechanical room comfortably. The boiler uses electricity to produce 130 F heating hot water. This temperature was selected from the operational range of 120 F to 140 F. 130 F water allows for the heating required in the space to be met, and will not be too hot based on the floor finishes for occupant comfort. The hot water is pumped and piped in a loop through the building with several distribution manifolds branching off to serve multiple zones. The branch for each radiant floor loop serving a zone has an automatic pressureindependent flow valve and a two-way modulating control valve. As with the radiant ceiling panels, the valves are controlled through communication with a control panel that receives input from thermostats located in each zone. Polyethylene tubing (PEX) is routed in a serpentine pattern throughout each zone forming a continuous loop to create the radiant floor. See Figure 8, above, for a detail section of the radiant floor. The tubing is spaced at 18 on center and covers the entire second and third floors. This loop is installed directly in the concrete floor slab. As with the chilled ceiling panels, the radiant floor has two pumps in parallel controlled by VFD s moving the water through the two-pipe direct return loop. When the building is in heating mode, the only loads taken into account come from the building s envelope. The window loads for this particular building came out to be a very large percentage of the overall envelope load, so it was desired to find a way to deal with these loads directly. For this reason, radiant heating windows were chosen for all exterior windows except for those in the stairways. These windows were also selected because they provide a high level of comfort in the winter for the occupants that work near an exterior window. Radiant windows also reduce the load on the radiant flooring. The windows use 48 volt direct current (DC), two copper buss bars, and a metal oxide coating between the glass panes to conduct electricity from one side of the window to the other, heating the inside window pane. 85% of the heating provided by the windows is directed into the space by the special coating and 15% of the heating is lost to the exterior. The radiant windows heat the space to its desired temperature in approximately 10 minutes. Once the thermostatic temperature has been achieved, the windows cycle off until power is required to bring them up to temperature again. Figure 9, on the next page, illustrates the radiant window s components. The windows look like ordinary double paned windows and don t have any electrified surface that the occupants could come in contact with. Being 48V DC, the windows would work great in conjunction with solar energy panels and battery energy storage. To avoid heating and cooling systems running at the same time and fighting each other, the thermostatic controls for the radiant windows are controlled through the same thermostat used for the radiant floors and chilled ceilings at the zone level. 10

17 Figure 9 Radiant Window (Reproduced from Radiant Glass Industries) Ventilation For ventilation, two AHU s located on the roof will serve as DOAS s for the building occupants. AHU s are utilized because total energy recovery wheels can be directly incorporated as an integral unit and can be sized for a custom fit to the system. Also, AHU s allow for the use of CO 2 sensors for added control and energy savings. Supplemental cooling and dehumidification is done by dx from an air-cooled condensing unit and electric resistance coils will provide supplemental heating. The DOAS units are not tied into the source for the radiant heating system as the boiler delivers hot water at 130 F which is too low for coil operation in the AHU. This is similar for the cooling system where the chiller does not deliver water at low enough temperatures for coil operation as it is dedicated to the chilled ceiling panels. It is possible to use mixing valves on the loops that create the radiant heating and cooling, but a significant amount of energy is wasted by doing so. The outside air is ducted to ceiling diffusers in each zone and airflow is balanced with balancing dampers to ensure proper ventilation in all spaces. CO 2 sensors are located in the tenant space and a schedule is used for the office space to control ventilation loads. The CO 2 sensors control the dampers to modulate the outside air cfm brought into the space. As static pressure increases in the duct, a sensor will communicate with the VFD on the fan to modulate accordingly. This allows the AHU to use less electricity when the amount of CO 2 in the space decreases, while still being able to maintain acceptable indoor air quality. The schedule set for the office space shuts down the DOAS AHU and exhaust fans at night Condensation Prevention Since the chilled ceilings can be prone to condensation in a humid climate, a control sequence is used to adequately manage the room dew points. The dew point can rise when the DOAS is turned off and infiltration of humid air occurs during unoccupied periods of time, when rooms become highly populated, or when food preparation equipment gives off steam. It was determined, however, that the dew point would never increase high enough to create condensation because of people or equipment loads. Since both DOAS units are constantly supplying some outside air during occupied hours, pressurization will prevent infiltration. Infiltration of humid air could occur at night, however, raising the dew point. Therefore, a humidity sensor is located in each exterior room to alert the DOAS AHU it is being served by to cycle on to supply air which is dryer and will lower the dew point and will also minimize infiltration. 4.0 LIFE CYCLE COST ANALYSIS The life cycle cost analysis contains four main components: initial cost, operating cost, replacement cost, and maintenance cost. The following sections describe how these costs were determined and how the options compare with one another. 4.1 First Cost The three options were initially compared to determine the differences in materials and components of those systems. A first cost was calculated for each system based on comparative costs of the other systems. Only items that weren t equal in size and quantity among the three systems were calculated. The sizes of components were determined using the heating and cooling loads calculated by Trane TRACE 700 and the zones that were created for the building. Most of the 11

18 price estimates were found in Mechanical Cost Data from RS Means. The remaining costs were provided by either a local sales representative or from engineering professionals. The amount of diffusers for each system was estimated on their calculated cfm s which make the systems with higher cfm s have more diffusers. Pipe and duct differences for the three systems were calculated by taking a common area in the building and estimating the differences in amounts and sizes. The control systems for the three systems were all different in the amount of controls and the types of controls; therefore each system has its own controls listed. A summary of the first cost comparisons can be found in Appendix C.1, C.2, and C Operating Cost The operating cost for each option is calculated as a function of its energy consumption and the utility rates applicable for this location using Trane TRACE 700. The energy use was modeled by monthly consumption and hourly demand for the thermal storage operation. Utility rates were determined for the Nashville, TN, area from the utility providers websites and are summarized in Table 4, right. Utility Base Charge Cost per Unit Electricity $ $ kwh Natural Gas $29.00 $ therm Table 4 Utility Rate Structures Units System Operating Cost Utility Electricity Natural Gas (kwh) Cost ($) (therm) Cost ($) % Better than 90.1 Total Operating Cost Option 1 - Packaged Rooftop Units 70,357 $8, $ % $8, Option 2 - Heat Pump 47,256 $6, $ % $6, Option 3 - Radiant Heat. & Cool. 70,149 $8, $ % $8, Baseline 35,515-1, Table 5 System Operating Schedules The utilities being used are electricity for each considered system s components and natural gas for the baseline RTU. The energy consumption for the baseline system is listed because this is what was considered to be the maximum energy usage of an ASHRAE Standard 90.1 compliant system. The energy consumption for each system was compared to the energy consumption of the Standard 90.1 baseline system to determine if each option consumes at least 20% less energy. Table 5, above, shows the yearly utility consumptions and costs, the percent less energy consumption than Standard 90.1, and the total yearly operating cost for each system. A separate calculation of the electricity costs for the thermal storage system was performed based on the time-of-day utility rate available. This rate had lower demand and consumption charges for off-peak times, which is when the ice unit runs to create the ice storage. A summary of the electricity usage and costs is provided in Table 6 on the next page. The electricity rate structure for this usage is based off the fact that the largest demand of the system is between 50kW and 1000kW and is outlined as follows: Base Charge - $ Distribution Capacity Charge - $2.55 per kw per month of the highest demand Demand Charge - $10.76 per kw of onpeak demand and $1.46 per every kw of offpeak demand that is above the onpeak demand Energy Charge - $7.605 per kwh of onpeak energy use and $5.356 per kwh of offpeak energy use This utility rate structure did not result in a lower operating cost due the larger base charge and the addition of the demand charge and distribution capacity charge. The rate structure would have been more favorable had the largest demand been lower than 50 kw, eliminating the distribution capacity charge and the demand charge from the rate structure. 12

19 Ice Storage Packaged Rooftop Units Energy Usage Jan Feb Mar Apr May June July Aug Sept Oct Nov Dec Onpeak Consumption(KWH) 6,360 5,923 3,734 1,195 1,032 1,073 1,041 1, ,229 3,450 5,306 Offpeak Consumption(KWH) 4,307 4,003 2,699 1,442 2,949 3,466 3,274 3,488 2,741 1,848 2,498 3,629 Onpeak Demand(KW) Offpeak Demand(KW) Annual Base Charge $2,807 Annual Distribution Capacity Charge $1,039 Note: Annual charges are simply the total of all monthly Annual Demand Charge $4,302 charges. Monthly charges are the product of the charge rate Annual Energy Charge Onpeak $2,541 and respective energy usage. The total annual energy charge is Annual Energy Charge Offpeak $1,947 the sum of all annual charges. Total Annual Energy Charge $12,636 Table 6 System 1 Alternative Energy Plan 4.3 Replacement Cost To perform a life cycle cost, the anticipated life and the required replacement for components of the three options were considered. The length of time before the components needed replacing was determined using Facilities Maintenance and Repair Cost Data from RS Means. The replacement cost was calculated to be equal to the initial cost of the component plus the inflation incurred using an inflation rate of 3.5%. The least common multiple of replacement years between systems was sixty; therefore, all components replacement values were then taken out to sixty years using the interest rate of 6%. Finally, these values were brought back to 20 years at this interest rate to be able to compare similar values. An analysis of the replacement costs for the three systems can be found in the 20-Year Life Cycle Cost Analysis tables in Appendix D.1, D.2, and D Maintenance Cost The final information needed for the lifecycle analysis is the amount spent on annual maintenance for each option. The maintenance cost per a specified number of years was also found in Facilities Maintenance and Repair Cost Data. To calculate the annual maintenance cost, the listed price was divided by the number of years specified for each piece of equipment. Once yearly maintenance costs were known, future values at 20 years were calculated using the interest rate of 6%. The maintenance cost results can also be found in Appendix D.1, D.2, and D Year Life Cycle Cost The life cycle cost is simply the sum of the first, maintenance, operating, and replacement costs at year 20 of the building s life. This piece of information is very valuable for a commercial building owner because the individual is likely to own the building for a long period of time. The owner may want a system that will cost them little upfront, but may be willing to pay more initially for a low life cycle cost. 5.0 DECISION MATRIX In order to compare and select the most appropriate HVAC system for this office building, design criteria and goals were predefined by ASHRAE were referenced. Certain design requirements were set that each system needed to meet in order to be considered. Then, the three systems are compared to each other by rating how they performed in each category of the design criteria and the design goals. They are rated from 1-10 with 1 indicating the system shows no concern for that category and 10 indicating the system could not possibly improve in that category. Each category is weighted to show preference to the more important categories of concern. The design criteria weights are given by ASHRAE and the design goals are weighted evenly at 20%. All five of these goals are considered to have equal importance in this system selection. The design criteria and major design goals are each given 50% influence on the final system comparison. This is because they are considered to be a completely separate but equal set of objectives. The following sections describe the design criteria and major design goals and how the systems compare in each category. 13

20 5.1 Design Criteria The following sections are design criteria that are set by ASHRAE to compare and select the most appropriate HVAC system. Table 7, below, outlines the rankings chosen for each criterion for the system options. The following sections more precisely discuss the methods used to choose these ranking. DESIGN CRITERIA MATRIX (10 = best, 1 = worst) Performance Requirements Meets Requirements Meets ASHRAE Standard 55 Meets ASHRAE Standard 62.1 % energy use reduction beyond ASHRAE Standard 90.1 Meets sound criteria Capacity Requirements Meets Requirements Meets calculated peak loads Spatial Requirements Meets Requirements Equipment is contained within spacess allotted First Cost (20%) Rating Comparative system initial cost Operating Cost (20%) Rating System operating cost Reliability (15%) Rating Equipment lead time Redundancy System longevity Flexibility (15%) Rating System flexibility Cost for system alterations Maintainability (15%) Rating Labor skill level required for preventative maintenance Annual maintenance required Interruptionn to productivity Sustainability (15%) Rating Disturbance to site Duration of Constructionn LEED points available System Total YES yes yes 38.6% yes YES yes YES yes $276, $299,966. $295, $8, $6, $8, YES yes yes 58.3% yes YES yes YES yes YES yes yes 38.3% yes YES yes YES yes Table 7 Design Criteria Matrix

21 5.1.1 Performance Requirements (Gate Requirement) Performance requirements were set for each system before they could be considered as a viable option for this building. These requirements are as follows: Comfort: The system must be able to maintain the proper temperature and humidity per ASHRAE Standard 55 and the indoor design conditions set by ASHRAE. Ventilation: The system must meet or exceed the requirements of ASHRAE Standard 62.1 for acceptable indoor air quality. Energy Consumption: The system must consume 20% less energy than ASHRAE 90.1 according to the Performance Rating Method in Appendix G. Sound: The system must meet the design sound criteria set by ASHRAE, listed below. o Office Area RC 35N o Lobby/Corridor RC 45N All three of the system options meet the performance requirements defined. 20% less energy consumption than ASHRAE Standard is determined as described in Section Ventilation minimums are calculated using ASHRAE Standard 62.1 and input into Trane TRACE 700 and Standard 55 is met as outlined in Section Sound criteria are checked with air distribution calculations along with noise criteria values given by diffuser and equipment specification sheets Capacity Requirements (Gate Requirement) Each option must have a capacity that is able to meet or exceed the heating and cooling loads of the building as calculated by Trane TRACE 700. These loads are based on the following factors: ventilation, indoor design conditions, outdoor design conditions, internal heat gains, and envelope loads. Each HVAC system option adequately meets the capacity requirements for this building Spatial Requirements (Gate Requirement) The third requirement for each system is the spatial requirement. All equipment, ductwork, and piping need to fit into the available space of the mechanical room, shaft spaces, plenums, and roof. This is necessary to maximize the amount of space that can be rented to occupants. The size and location of equipment also affect the ease of maintenance, noise in the occupant space, and aesthetic look of the building. These characteristics were considered respectively in Performance Requirements, Maintainability, and Synergy with Architecture. Each of the three options is quite different in terms of the location of equipment. Option 1, rooftop units, is mostly located on the roof of the building in addition to ductwork in the ceiling plenums. The second option, ground source heat pumps, occupy mostly plenum space, piping is outside below grade and pumps in the mechanical room. Option 3, radiant heating and cooling, has equipment located in basically every space available. The chiller is on the roof, the pumps and water heater occupy the mechanical room, chilled ceiling panels and ductwork are in the plenum and radiant windows are in the occupied building space. Options 2 and 3 also both have DOAS units on the roof of the building. All three system options meet the spatial requirements and are maintained in the locations allotted First Cost (20% Design Criteria / 10% Decision Matrix) Option 1: 7.0; Option 2: 3.0; Option 3: 4.0 The first cost of the HVAC system is a very important consideration for all project owners. Being able to minimize the first cost is always significant to the owner in order to have a successful and profitable building. This criterion was, therefore, weighted at 20% of the total design criteria weight. The process of first cost comparison of the three systems can be found in Section 4.1. The systems are compared using comparative cost; therefore items that were common among all systems are not listed or calculated. The first cost (comparative cost) table for each system can be found in Appendix C.1, C.2, and C.3. Option 1 has the lowest initial cost of the three systems because of the relative simplicity of the system. The packaged rooftop units, ice units, and controls package comprised the largest costs of this system. Option 2 has the highest initial cost of all the systems primarily due to the excavation costs and large number of heat pumps. Option 3 also has a fairly high initial cost that was just below Option 2. This is mainly due to the large air-cooled chiller, the radiant windows, and amount of piping. 15

22 5.1.5 Operating Cost (20% Design Criteria / 10% Decision Matrix) Option 1: 4.0; Option 2: 9.0; Option 3: 3.0 Operating cost is also an important consideration for owners because it is a continuous cost that the owner must pay. For this building application, most or all of the operating costs could be charged to the tenants of the building. Since this building has a single point of metering for utilities, the tenants are charged a higher pro-rated monthly rent based on a square foot basis to cover the utilities. However, it is still a significant factor for the owner when determining an HVAC system, because the lower the operating costs, the more appealing the building is to potential tenants. With higher demand, the owner could charge more and make a higher profit. The operating costs for an HVAC system could include water consumption, electricity consumption, natural gas consumption, and sewer fees. These costs are affected by the following: heating and cooling loads, amount of outside air needed, overall system efficiency, and make-up water needed. The overall system s efficiency is affected in many ways including the configuration of piping and ductwork, pre-conditioning of outside air, equipment efficiencies, use of variablefrequency drives on pumps and fans, and use of schedules for temperature setbacks or ventilation minimization. The operating cost comparison of the three systems can be found in Table 5 in Section 4.2. Option 1 has a relatively low operating cost as it consumes approximately 38% less energy than the ASHRAE Standard Even with the offpeak operations not reducing energy cost, it is still a very efficient system. However, the option still consumes quite a bit more than Option 2. Option 2 has the lowest operating cost of all the options. This system is approximately 58% more efficient than the ASHRAE Standard 90.1 minimum which shows that energy consumption is less than half of the baseline system. Heat pumps run efficiently since they use the ground as the source of heating and cooling rather than using mechanical means. They are also more efficient in a large system that has heating and cooling taking place at the same time. This allows the primary pumps to be shut off. Option 3 uses approximately 38% less energy than ASHRAE Standard 90.1, and slightly more than Option 1. This system is able to exceed Standard 90.1 as the heating and cooling delivery methods of the system are very efficient which allow for the system to use less energy to condition spaces. However, the operations of the radiant windows are less efficient due to heat loss to the exterior Reliability (15% Design Criteria / 7.5% Decision Matrix) Option 1: 4.0; Option 2: 7.5; Option 3: 4.0 Reliability is evaluated based on longevity and dependability of equipment and the value of the building s operations. Any time this building is inoperable, the businesses occupying the building could lose profit and productivity. The retail tenants customer sales may fail due to unconditioned space or major repairs. It is important for the HVAC system to minimize the possibility of total system failure if one component fails, so the building can remain operable as much as possible. It is also advantageous that if a major component must be repaired or replaced, only part of the building would have to be shut down, so not all businesses would have to close. Redundancy of equipment can allow a piece of equipment to be repaired or replaced without any change in the system s operation. However, too much redundancy can result in unnecessarily high first costs. Packaged rooftop units are readily available, but the addition of the ice units can lengthen the lead time for this system. Option 1 has the least reliability as the major system equipment has a life expectancy of 15 years. Also this system has a medium degree of redundancy because each rooftop unit can operate without the ice storage and still meet the full cooling demand. Option 2 is expected to have the shortest lead time for the equipment given the growing popularity of the system. An increased number of manufacturers and distributors are available in more locations. The longevity of a ground source heat pump is estimated to be 20 years extending the system life beyond Option 1. The redundancy of Option 2 is moderately high since each heat pump is its own system and there are two hydronic pumps for each loop. The major system equipment and components for Option 3 all have a relatively high lead time. The chilled ceiling panels and radiant windows are not produced by many manufacturers and may be difficult to repair. The life of the boiler and chiller is estimated at 30 years giving the radiant heating and cooling system the greatest system longevity of the three options. 16

23 5.1.7 Flexibility (15% Design Criteria / 7.5% Decision Matrix) Option 1: 4.5; Option 2: 7.0; Option 3: 2.0 For this building, flexibility of the HVAC system is important because desired changes to the spaces are foreseeable. It is probable that the unfinished tenant space and even the office spaces will change tenants throughout the building s life. The owner may want the ability to change heating and cooling zones to accommodate these changes in occupancy. The more flexible the HVAC system, the quicker and less expensive it is to alter the spaces and zones and provide proper conditioning and control. Option 1 is fairly flexible as ductwork can be rerouted and VAV boxes moved within the plenum space. However, a remodel could require new duct chases which can affect usable space of multiple tenants. The system can accommodate additions to the building fairly well, by simply sizing and selecting an additional rooftop and ice unit. The cost of small system alterations is fairly low because moving a VAV box and its associated ductwork is relatively simple and quick. The cost of larger alterations can be high because of the need to change existing chases, plenum space, and roof or floor penetrations. Option 2 has a high adaptability for room reconfigurations in the unfinished tenant space, and accommodates rezoning well. Each zone requires only the duct and diffusers or grilles to be relocated to accommodate the changes, affecting only the zones involved in the reconfigurations. Also, this form of alteration does not require additional or changes to chases and penetrations. The cost for small alterations is relatively low because the movement of a heat pump and its associated ductwork and piping is similar to the movement of a VAV box in Option 1. Adding a few heat pumps is also a fairly small cost since the system can accommodate a small addition without the need for resizing major components or adding bores. Adding many heat pumps to the system may be problematic and costly as pipe sizes, pumps, and well field size may all need to increase. Option 3 is the most difficult to alter or rezone as the heating piping is embedded in the concrete floor. The floor will most likely need to be removed and reconstructed to rezone the piping. The radiant windows are also complicated to repair but can be easily replaced. The chilled ceiling panels are the most flexible part of this system as rezoning or additions need only to be moved with little to no extra piping or valves. The ventilation for this system is able to accommodate space additions with duct, diffuser, and damper placement. The cost for any alteration of this system is very high because the labor skill level required is advanced and the effects to the existing building would have a large impact on tenants Maintainability (15% Design Criteria / 7.5% Decision Matrix) Option 1: 5.0; Option 2: 5.5; Option 3: 6.0 Maintainability of the HVAC system considers the work that is necessary after installation to continue operation. Maintainability includes the following: the skill level required of the maintenance staff, location and accessibility of the equipment, and the extent of the expected maintenance and repairs. The more complex a system is, the more knowledge and skill are needed of the maintenance staff. The more accessible the equipment is, the less time it takes to perform maintenance and the more often preventative maintenance will be performed. Also, the more equipment that is located in plenums in the occupied space, the more interruptions to productivity are expected for maintenance. Rooftop units are generally considered to be easy to maintain but the ice storage boxes add complexity to the skill level required for installation and preventative maintenance of the units. Annual maintenance is typically not too involved for RTU s, but because of the volume of units in Option 1 and the added ice storage boxes, more filter changing and other frequent maintenance is required. Most of the building s occupants will not be affected by maintenance performed to this system with the exception of occupants on the roof terrace. Option 2, ground source heat pumps are becoming more and more common so skilled laborers are becoming increasingly educated and easier to find for both installation and preventative maintenance. However annual maintenance can be more troublesome because it contains a large amount of equipment and components that could fail. Option 2 also requires maintenance at the zone level which can be difficult due to the heat pumps being located in the plenum. In addition, the probability of interrupting the building occupants may increase. Option 3 has the least moving parts of the three systems requiring the least amount of preventative maintenance. However, the maintenance to the cooling system and radiant windows can result in disruption to the occupants. Radiant windows require an increased knowledge base with the maintenance staff as they are a new technology, but the rest of the equipment is common and well known to most servicing crews. 17

24 5.1.9 Sustainability (15% Design Criteria / 7.5% Decision Matrix) Option 1: 7.0; Option 2: 3.0; Option 3: 4.0 ASHRAE s GreenGuide defines sustainability as providing for the needs of the present without detracting from the ability to fulfill the needs of the future. Sustainability has recently become a very important factor to building owners and engineers in building design and the selection of the HVAC system. This is primarily due to increased knowledge of how HVAC systems affect the environment and natural resources. Many owners are also aware of and attracted to potential tax credits and Leadership in Energy and Environmental Design (LEED) certification that can result from a sustainable design. ASHRAE s GreenGuide and the United States Green Building Council s (USGBC) LEED Green Building Rating System are great resources for designing towards a sustainable future. Sustainability of the three systems in this selection is compared based on initial impacts on the environment. These impacts include location of available resources, availability of recycled material, use of ozone depleting refrigerants, construction methods and installation time, amount of disturbance to the existing site, and amount of material waste that is created. All three options have the ability to achieve many LEED Credits. The credit areas include Energy and Atmosphere (EA), Indoor Environmental Quality (EQ) and Innovation and Design (ID). For example, EA Credit 1, optimizing energy performance above ASHRAE Standard 90.1, can potentially earn up to 9 points for Option 1, 10 points for Option 2 and 8 points for Option 3. All three of the HVAC system options can earn multiple Indoor Environmental Quality credits but Option 3 is the only system that qualifies for EQ Credit 1, outdoor air delivery monitoring. This is due to the use of CO 2 sensors in densely populated areas and the ability to monitor the ventilation rates in both the office and tenant spaces. Multiple credits can also be earned for the category of innovation and design. Using more efficient equipment with uncommon creative capacities is the key to earning these credits. Also, all three systems require the use of refrigerant, and as a result all systems are specified to use non-cfc based, and non-ozone depleting refrigerants. The amount of time that installation equipment is on site for Option 1 is relatively short because the rooftop units are easier to install and do not require as much labor as the other systems. This also helps to reduce the site disturbance. A relatively low amount of waste is created when installing rooftop units but it is difficult to estimate exactly how much of the materials can effectively be recycled. A drawback to ground source heat pumps is the amount of time and effort required to install this system, causing an increase in the duration of time that equipment is on site. The bore field adds additional disturbance to the site during installation. However once installed the site can be used in many applications including landscaping, sports fields, and parking lots. The radiant heating and cooling system is estimated to have the longest amount of equipment on site due to the large volume of system components and complexity of installation. Again, site disturbance potential is increased because the amount of time of system installation is greater. 5.2 Major Design Goals The major design goals are the second half of the decision matrix. These design goals further emphasize what is important to the owner and need to be considered in the HVAC system selection. Although these goals may use principles from the design criteria, they are generally broader, showing the bigger picture of what the owner is looking for out of the HVAC system. The following sections describe these goals and how the HVAC systems compare in meeting them. Table 8, on the next page, shows a summary of the design goals and how each system was ranked in each goal. 18

25 MAJOR DESIGN GOALS MATRIX Low Environmental Impact (20%) Rating Water consumption Fuel consumption Electricity consumption Building emissions & greenhouse gases Low 20 Year Life Cycle Cost (20%) Rating 20 Year Life Cycle Cost Comfort and Health (20%) Rating Quality of indoor air Thermal comfort Controllability of systems Creative High Performance Green Design (20%) Rating System sustainability Creative design Synergy with Architecture (20%) Rating Equipment located in occupied spaces Equipment located in exterior spacess Noise created by equipment System Total Table 8 Major Design Goals Matrix Low Environmental Impact (20% Design Goals / 10% Decision Matrix) Option 1: 7.0; Option 2: 8.5; Option 3: 7.5 Setting a goal of creating a low environmental impact reinforces the importance of sustainability. The two concepts are inseparable and practically identical in many definitions, but for this report the initial impacts of the system will control the sustainability comparison, while the ongoingg impacts will define the environmental impact. The environmental impact of the system is determined by the amount of carbon emissions, the amount of water, power, and fuel use, and the effect on the quality of indoor air. ASHRAE Standardd 90.1 was used to guide the system selection by ensuring each system would be capable of Standard 90.1 compliance as outlined in Section The baselinee system was designed to meet Standard 90.1 minimums, while all other systems are required to consume 80% or less energy than the baseline system. Option 1 uses the least amount of water, which is only needed to fill the ice storage tanks upon installation and minor make-up water during system maintenance. This system uses dx cooling coils and electric heating coils so no fuel is consumed but a great deal of electricity is equired to operate the RTU s. Option 1 also emits a sizable amount of greenhouse gasess that can have a negativee impact on the atmosphere as well as the indoor environment. These emissions mostly come from multiple RTU s, but exhaust and relief air also contribute to the issue. 19

26 Aside from charging the system, Option 2 uses a minimal amount of make-up water that is required to maintain the system s operating pressure. Option 2 also uses only electricity to power the system but a better rating is given to the heat pumps because of more efficient equipment and the use of energy recovery wheels to reduce coil sizes. Using the ground as the heat source or sink also decreases electricity consumption for this system and greatly reduces the amount of greenhouse gases released into the atmosphere. Option 3 falls in between the first two system options in terms of low environmental impact. Similar to the first two systems, natural gas is not utilized and water consumption is minimal since it is a closed system. Electricity consumption for the radiant heating and cooling system is less than the RTU s but not as efficient as the ground source heat pumps. The use of CO 2 sensors in the tenant space increases the efficiency of this option. The third system option also has less building emissions than Option 1 but the added air-cooled chiller and radiant windows increase Option 3 s effect on the atmosphere over Option Low 20 Year Life Cycle Cost (20% Design Goals / 10% Decision Matrix) Option 1: 5.0; Option 2: 8.0; Option 3: 2.0 The life cycle cost, as described in Section 4.0, incorporates all costs of the HVAC system throughout its life, including first costs, operating costs, maintenance costs, and replacement costs. Each one of these costs are important separately because they show the costs at different times of the building s life, but the life cycle cost gives an accurate comparison of all the costs of each HVAC system throughout the building s life. This is important because it shows which system will be the most economical for the owner over time. The reason the first cost and maintenance costs are low for Option 1 is the system is very simplistic. Option 1 has the median price for the replacement cost as the packaged RTU s will have to be replaced after a 15 year period, the shortest life of any system. Option 1 has the highest operating cost of the three systems because it is the least efficient. Overall option 1 came in with the median price for the 20 year life cycle cost because of the low first costs and short replacement period. Option 2 has the lowest operating cost because a heat pump system uses less utility than the other systems. It is more efficient and uses the ground as its source for heating and cooling rather than producing it through mechanical means. The low replacement cost comes from the fact that the main portion of the ground source heat pump system is the geothermal wells. This piping has a long life and therefore is not accounted for in a 20 year lifecycle cost. Option 2 has the median price for maintenance cost as heat pumps have a higher standard of maintenance than most general HVAC equipment. Option 2 has the highest first cost which relates back to the large price tag for the geothermal well field and all the piping involved with it. Overall option 2 comes in with the lowest 20 year life cycle because of its low operating costs. Option 3 has a high upfront cost, due to the complex installation process, and type and volume of equipment. The initial cost is almost as high as the ground source heat pumps, and the operating cost is the highest of the three systems. All of these factors combine to give Option 3 the lowest rating Comfort and Health (20% Design Goals / 10% Decision Matrix) Option 1: 5.5; Option 2: 7.5; Option 3: 9.0 Comfort and health are the main reasons why HVAC systems exist. Therefore, they are imperative to consider when choosing the HVAC system. Comfort involves designing and controlling the temperature and humidity of the space within an acceptable range. The method and manner in which the space is conditioned is very important in the aspect of air speed and noise pollution from air distribution. These comfort issues are important because they affect the alertness and productivity of the occupants. Health is important for the obvious reason of preventing illnesses that could jeopardize the occupants and decrease productivity of the occupants. Health is affected most by the quality of the indoor air, which is improved and maintained by the incorporation of outdoor air and filtration of return air. ASHRAE Standard 55 describes the characteristics of the space that affects comfort and important considerations when designing the HVAC system to maximize comfort. ASHRAE Standard 62.1 aids in providing proper ventilation amounts to all occupied spaces to maintain the indoor air quality. Option 1 received the lowest rating due to the method of outside air delivery. In this system, outside air is mixed with return air and delivered to a space through ducts and dampers. These dampers are set to a minimum position that reflects the ventilation rate; however it cannot be guaranteed that the percent required is delivered. Thermal comfort and controllability of systems are not ranked very high for this option because it is composed of RTU s. Packaged rooftop 20

27 units are only available in incremental sizes which can cause the designer to over or under-size the units. Over-sizing the unit can result in reduced comfort due to a lack of humidity control and extreme system short cycling causing large temperature swings. Under-sizing RTU s result in poor temperature control during extreme design conditions. Option 2 receives a higher rating than Option 1 because the exact amount of outside air is ducted directly to each zone. This ensures that the proper amount of outside air is supplied to the heat pump. Therefore, a smaller percentage of ventilation can be supplied to each zone when compared to Option 1, saving more energy. The controllability of the ground source heat pumps is reasonably higher than Option 1 since the units can be more accurately sized to fit the loads required. In addition better control is acquired by Option 2 because each heat pump only supplies one zone. Option 3 receives the highest rating for indoor air quality because the DOAS units supply the exact amount of ventilation at a space level. The amount of outside air being delivered to the tenant space is controlled through CO 2 sensors. This ensures that air is conditioned and supplied only when needed. Since air velocity is not a major factor, the radiant heating and cooling can also condition the room more uniformly and reduce noise and drafts that are associated with air-based HVAC systems. The only drawback to the system is the speed of response to thermostat change beyond set points Creative High Performance Green Design (20% Design Goals / 10% Decision Matrix) Option 1: 6.5; Option 2: 7.0; Option 3: 6.5 Creative high performance green design reinforces the sustainable criterion and goal of low environmental impact. In addition to designing green, creativity can be a great selling point for the building owner. It can help attract attention by creating a unique feature that sets it apart from other office and retail buildings. ASHRAE s GreenGuide and USGBC s LEED Green Building Rating System can be used as guides to achieving a green design, even when not seeking LEED certification. These resources can also help in creative design, though they should not restrict the designer s imagination to just those ideas. Thinking outside the box to come up with new and innovative solutions is necessary. Using the rating system defined in section 5.0 Discussion of Decision Matrix, Option 2 received the highest overall rating. The majority of the points earned were for system sustainability, as it uses far less energy over the other two options. Also, this system utilizes the energy located on the site to absorb and reject heat. This decreases the atmospheric ejections and the overall demand on public utilities. The ice storage system received 5 points because the energy consumption is much more than Option 2. It should be noted that the energy consumption of a thermal storage system does not change; rather it only shifts the operations to consume the energy when the utility providers have less overall demand and therefore cheaper rates. This means that the load does not contribute to the peak demand at the power plant helping decrease the need for new or larger power plants. The radiant system was found to use about the same amount of energy as the ice storage system, however since no displacement of energy demand to an off peak utility rate is accomplished, the overall energy demand has a greater impact on utilities. All systems scored well in the area of creative design, scoring above average marks. The radiant heating and cooling system is the most creative from the aspect that it deals with the building load directly at the windows. This is done at the source by treating the envelope load through the radiant window system. This system also has minimal forced air due to the ventilation requirements, keeping the occupied space at a very uniform climate. The ice storage system came in second. The offpeak operations were accomplished uniquely by using a completely unitary device that can create ice, store ice, and deliver cold refrigerant to the coil. By having this unitary device, the complexity of a standard ice storage system is reduced to packaged units mounted on the roof within close proximity to the RTU s. Scoring last is the ground source heat pump system. The system is still very creative from the aspect that it uses the surrounding site as a source of heating and cooling. However, since this system is very commonly used it is not as creative as the previous two systems Synergy with Architecture (20% Design Goals / 10% Decision Matrix) Option 1: 6.0; Option 2: 8.0; Option 3: 6.5 In general, buildings are designed to showcase their architectural design, not their HVAC systems. It is important for the HVAC system to enhance the feel or theme of the building design, not to obscure it. Ways that the HVAC system can interact with the architectural design include the amount of equipment in occupied spaces, types of diffusers and grilles used, exposed ductwork, and space required in the plenum, mechanical rooms, or on the roof. In office and retail applications, it is also desired to maximize rentable space in order to maximize profit to the building owner. The first step in selecting an HVAC system that will work productively with the architecture is analyzing the architectural design and determining its theme. 21

28 When rating the three systems on synergy with architecture, the ground source heat pumps are the winner. All the equipment fits in the HVAC plenum or in the specified existing mechanical rooms and chases. Also, the system operates quietly and all the geothermal bores located in the ground can be completely covered with landscaping, parking lots and walkways. The ice storage system is located on the roof and in the HVAC plenum. This comes in last for exteriorly located equipment and sound becausee the architectt will have to supply screens that will reduce sound and visual aesthetics for use on the rooftop terrace. The radiant system scored higher than Option 1 because all of the equipment is located within the mechanical spaces reducing the issue of sound. The disadvantage to the system is the quantity of equipment located within the ceiling plenum. More ceiling space is required for the chilled ceiling panels and zone distribution manifolds located on the walls. 6.0 CONCLUSION AND RECOMMENDATION The purpose of this proposal is to select the most appropriate HVAC system for the building considered. Design criteria and goals are set to ensure the system selected met the needs of the owners. Many systems were considered and we weree able to focus on three systems we believed best suited the building. Those systems were then modeled in Trane TRACE 700 load modeling software for the following reasons: to determine the size of the HVAC equipment necessary to meet the heating and cooling loads, to determine the yearly energy consumption of each system to compare with the ASHRAE Standard 90.1 baseline system and to determine a 20-year lifecycle cost comparison of the three systems. Next, these systems were rated in each design criteria and goal to determine how well each system met the owner s needs. The design goals and criteria were analyzed in separate matrices. Each design criteria and goal was given a percent weight of its specific matrix based on how important that criterion or goal was to the owner. Using the ratings and weights, the systems were compared to one another to determine best HVAC system for this application. The major design goals and the design criteria matrices were given equal weight in the final selection. Table 9, below, shows the final ratings of the major design goals matrix, design criteria matrix and the final system selection. Final System Selection Major Design Goals Matrix Totals Design Criteria Matrix Totals Final System Selection Totals Table 9 Final System Selection Recommendations As you can see from the table above, the ground source heat pump system resulted in the highest score among the options. Therefore, we recommend that ground source heat pumps be selected as the HVAC system, as it will best suit this building and most effectively meet the owner s needs. This option is very flexible, so the office and retail spaces can be altered withoutt much change to the HVAC system. The redundancy of the heat pumps reduces the negative effect on the building s conditioning when one heat pump fails. Each zone can be controlled with its own schedule because of this redundancy. Therefore, the first floor lobby heat pump can be controlled with a schedule that accommodates both the office and retail schedules. This option is also the most efficient and has the lowest environmental impact throughout the life of the building. The very low operating cost of this system also makes it economically viable and causes it to have the lowest 20-year lifecycle cost. High indoor air quality is maintained by the use of the DOAS units and high indoor comfort is achieved by the precise sizing of the heat pumps to the loads they must maintain. Finally, the owner will be very pleased because of the system s highly green design and the number of LEED points that can be achieved through its design. 222

29 Based on using this option as the HVAC system, we have several other recommendations for this design. In the initial stages of design, a test bore should be drilled where the bore field location is and tested to determine the precise amount of heating and cooling capacity the ground soil has in this location. This will increase the precision of design so that enough bores can be provided to handle the loads at all times without too many bores being provided driving up the initial cost. The test bore can still be used after testing as one of the bores in the bore field. Another recommendation is for the DOAS heat pumps on the roof to be provided with sound attenuation and the rooftop terrace screen to be tall enough to hide the units from view. This is suggested to separate the occupants from the negative aesthetic effects of the mechanical equipment. The rooftop terrace could also be provided with shading and electric unit heaters mounted on the screen wall to allow more comfortable use of the terrace for more of the year. Finally, we recommend that commissioning be done once this building is constructed to ensure the correct operation of the HVAC system so that mistakes can be caught and fixed early in the lifetime of the building. 6.2 Innovative Ideas Throughout the selection process, several innovative ideas were considered for inclusion in the system and should be discussed with the owner. The first idea was formed after evaluating the Trane TRACE 700 loads. Rotating the building 135 clockwise would reduce the heating and cooling loads by approximately 6%. This could save a significant amount of money in operating costs. Another idea is to incorporate a mud cleaning system to recycle the drilling mud. This will help keep the site and environment clean. The waste mud is converted to solids which can be mechanically disposed of or recycled. This prevents installers from having to dig large settling pits for the volume of slurry that comes from the drilling process. Another advantage to using this method is that it prevents overspills of mud into streams, gardens and ponds allowing the use of ground source heat pumps in site sensitive areas. An item that was noticed by examining the building plans was that the garage does not seem to be large enough to accommodate all of the office workers in addition to potential customers for the retail stores. One idea that was conceived was to restrict parking to those who pay for parking passes. Customers or visitors could purchase daily or hourly passes that are priced based upon number of people in their vehicles. Less expensive passes for those who carpool promote more environmentally-friendly transportation as well as bringing more potential customers. The employees for the office and retail spaces could buy passes for a longer period of time. These passes could also be less expensive for those who carpool to once again protect the environment and free up parking spaces for possible customers. Finally, an innovative solution to the high window load of the building was found by possibly using thermal louvers. Thermal louvers are vertical blinds that are placed in the interior window frame. In the middle of each blind is a hollow center tube which has a blade on each side making up the blind. The blinds are then turned to a certain degree (commonly 20 ) to the window where the suns heat gain will be picked up by the blinds just like any other shading device. What makes the thermal louver effective is the ability to pump water through the blind and remove the heat from the building with the supplement of a cooling tower during the cooling season. In the winter months the thermal louvers are able to position to not take away from your solar gain but also eliminate envelope load from the window by pumping warm water through them from solar collectors on the roof. The thermal louver is able to eliminate envelope load gains from windows in both the cooling and heating seasons and is able to allow solar heat gain in the winter and eliminate large portions of it during the summer. By eliminating and decreasing these two loads at the source, less conditioning has to take place on the skins of buildings allowing for better efficiencies and better occupant comfort. These thermal louvers were not considered for inclusion in our system because they could not be modeled in Trane TRACE 700 accurately. 23

30 REFERENCES ASHRAE ANSI/ASHRAE, Standard , Thermal Environmental Conditions for Human Occupancy. American Society of Heating Refrigeration and Air Conditioning Engineering, Inc., Atlanta, GA ASHRAE ANSI/ASHRAE, Standard , Ventilation for Acceptable Indoor Air Quality. American Society of Heating Refrigeration and Air Conditioning Engineers, Inc., Atlanta, GA ASHRAE ANSI/ASHRAE, Standard , Energy Standard for Buildings Except Low-Rise Residential. American Society of Heating Refrigeration and Air Conditioning Engineers, Inc., Atlanta, GA ASHRAE ASHRAE Handbook Fundamentals. American Society of Heating Refrigeration and Air Conditioning Engineers, Inc., Atlanta, GA ASHRAE ASHRAE Handbook Applications. American Society of Heating Refrigeration and Air Conditioning Engineers, Inc., Atlanta, GA ASHRAE ASHRAE Handbook Systems and Equipment. American Society of Heating Refrigeration and Air Conditioning Engineers, Inc., Atlanta, GA ASHRAE. GreenGuide. American Society of Heating Refrigeration and Air Conditioning Engineers, Inc., Atlanta, GA HVAC System Selection. ASHRAE. 26 April 2007 < R.S. Means Mechanical Cost Data, 29th Annual Edition. R.S. Means. Kingston, MA. R.S. Means Facilities Maintenance & Repair Cost Data. R.S. Means. Kingston, MA. USGBC LEED. Green Building Rating System For New Construction & Major Renovations. Leadership in Energy and Environmental Design, Washington, DC. Stanley A. Mumma, Ph.D., P.E. ASHRAE Transactions Pgs A Technical Introduction to Thermal Energy Storage Commercial Applications Calmac. < Climate Master Product Selection Guide. Climate Master. 27 March 2009 < /index/comm_gr_gs_page> ICE BEAR Product Information. Ice Energy. 27 March 2009 < /resources/tabid/54/default.aspx> 24

31 ASHRAE Student System Selection Competition APPENDICES Kansas State University Spring 2009

32 APPENDIX A.1 SYSTEM SCHEMATICS Thermal Storage Packaged Rooftop Unit Schematic 25

33 APPENDIX A.2 SYSTEM SCHEMATICS Ground Source Heat Pumps - Hydronic Schematic Ground Source Heat Pumps - Air Side Schematic 26 26

34 APPENDIX A.3 SYSTEM SCHEMATICS Radiant Heating and Cooling - Hydronic Schematic Radiant Heating and Cooling - Ventilation Schematic 27 27

35 APPENDIX B ZONE MAPS 28 28

36 APPENDIX C.1 INITIAL COST COMPARISONS Ice Storage Packaged Rooftop Units Initial Cost Analysis (Option 1) Component Details Quantity Unit Cost Total Cost Rooftop unit 2000 cfm rooftop air handling unit, VAV, VFD 2 Units $15, $30, Rooftop unit 5000 cfm rooftop air handling unit, VAV, VFD 1 Units $22, $22, Rooftop unit 7500 cfm rooftop air handling unit, VAV, VFD 2 Units $26, $52, "Ice Bear" units 5 Ton refrigertive ice storage 5 Units $8, $43, VAV Boxes with electric re-heat 600 cfm (average) with electric reheat coil 1 Box per zone x 29 zones = 29 boxes $ $22, Refrigeration piping 1/2 in. Copper pipe 120 LF from ice storage to rooftop units $9.10 $1, Refrigeration piping 1 in. Copper pipe 120 LF from ice storage to rooftop units $ $1, Refrigeration piping insulation 1/2 in. Polyethylene insulation UV resistant for 1/2 in. pipe 120 LF from ice storage to rooftop units $4.53 $ Refrigeration piping insulation 1 in. Polyethylene insulation UV resistant for 1/2 in. pipe 120 LF from ice storage to rooftop units $4.77 $ Ductwork (main) 40 in. x 26 in. (average size) aluminum duct includes fittings, joints, supports 250 ft. per floor x 2 floors = 500 LF $54.50 $27, Ductwork (trunk) 24 in. x 12 in. (average size) aluminum duct includes fittings, joints, supports 15 ft. From main to each VAV box x 29 boxes = 435 LF $31.00 $13, Ductwork (branch) 12 in. x 6 in. (average size) aluminum duct includes fittings, joints, supports 10 ft. From VAV box to diffuser x 40 rooms x 2 diffusers = 800 LF $9.00 $7, Supply Diffuser 24 in. x 24 in. architectural diffuser cfm Total with 1 diffuser per 250 cfm = 96 diffusers $ $38, Controls package (VAV) VAV control of boxes, incl. thermostat, damper motor, and re-heat coil 1 package per VAV box x 29 boxes = 29 boxes $1, $47, Electrical component addition Additional panelboard for VAV box electric reheat (assume 208/3 PH. per coil) 42 Circuit, 225 amp main lug panelboard x 2 = 2 panelboards $2, $5, Note: This table is based on comparative values, and is not a total initial cost analysis. Subtotal $314, Location Factor Total Cost $276,

37 APPENDIX C.2 INITIAL COST COMPARISONS Ground Source Heat Pumps Initial Cost Analysis (Option 2) Component Details Quantity Unit Cost Total Cost Heat pump 1.5 Ton ground source 1 Heat pump per zone = 29 heat pumps $1, $55, Ground loop pipe (vertical) 1 in. dia. HDPE pipe with fittings 250 ft. per 35 Bores x 2 (both way) = LF $0.66 $8, Ground loop pipe (horizontal) 1.5 in. dia. (average size) HDPE pipe with fittings 15 ft. from bore to bore x 35 bores = 525 LF $1.42 $ Ground loop excavation 250 ft Vertical bore 35 Bores $1, $52, Distribution vault Underground concrete piping distribution vault 1 Distribution vault for valving between primary and ground loop $9, $9, Primary hydronic pump 5 hp. End suction pump package 2 Pump packages $9, $19, Secondary hydronic pump 3 hp. End suction pump package 2 Pump packages $9, $18, Variable Frequency Drive 5 hp. Drive for secondary hydronic pump 2 VFD's $2, $4, Primary hydronic pipe 3 in. dia. HDPE pipe with fittings 150 ft. from building to distribution vault x 2 (both way) = 300 LF $20.50 $6, Secondary hydronic pipe 2 in. dia. (average size) Black steel pipe schedule 40 with couplings and hangers 250 ft per floor loop x 2 floors x supply and return= 1000 LF $22.50 $22, Secondary break-off pipe 3/4 in. dia. (average size) Black steel pipe schedule 40 with couplings and hangers 5 ft. from main to pump x 29 pumps x supply and return = 290 LF $11.10 $3, Zone ductwork (heat pump) 12 in. x 6 in. (average size) aluminum duct includes fittings, joints, supports 30 ft. per heat pump x 29 heat pumps = 870 LF $9.00 $7, Supply diffuser 24 in. x 24 in. architectural diffuser cfm Total with 1 diffuser per 250 cfm = 80 diffusers $ $32, Balancing valve 3/4 in. Thermoflo indicator 1 Valve per heat pump x 29 heat pumps = 29 valves $ $15, Condensate piping 1 in. dia. HDPE pipe with fittings 15 ft. (average) per heat pump x 29 heat pumps = 435 LF $0.66 $ DOAS heat pump 2 Ton ground source 1 Heat pump per unit = 2 heat pumps $1, $3, Outdoor air ductwork (main) 20 in. x 20 in. (average size) aluminum duct includes fittings, joints, supports 200 ft. per floor x 2 floors = 400 LF $49.00 $19, Outdoor air ductwork (branch) 12 in. x 6 in. (average size) aluminum duct includes fittings, joints, supports 10 ft. from main to pump return air path x 29 pumps = 290 LF $18.85 $5, Controls package (water flow) Water flow control 1 package per heat pump x 29 heat pumps = 29 packages $ $27, Controls package (air flow) Space temperature control 1 package per heat pump x 29 heat pumps = 29 packages $ $18, Electrical component addition Additional panelboard for heat pumps (assume 208/1 PH. per pump) 30 Circuit, 100 amp main lug panelboard x 2 = 2 panelboards $1, $3, Note: This table is based on comparative values, and is not a total initial cost analysis. Subtotal $336, Location Factor Total Cost $295,

38 APPENDIX C.3 INITIAL COST COMPARISONS Radiant Heating and Cooling Initial Cost Analysis (Option 3) Component Details Quantity Unit Cost Total Cost Chiller 35 Ton packaged air-cooled chiller 1 Chiller $34, $34, Boiler 80 MBH Electric boiler 1 Boiler $5, $5, PEX Tubing 3/4 in. Tubing 300 LF. per zone x 29 zones = 8700 LF $2.36 $20, PEX Tubing manifolds 1 in. Brass manifolds 1 Manifold per 6 zones = 5 manifolds $ $ Radiant floor piping 2 in. dia. (average size) Black steel pipe schedule 40 with couplings and hangers 250 ft per floor loop x 2 floors x supply and return= 1000 LF $22.50 $22, Chilled ceiling piping (main) 1.5 in. dia. (average size) Black steel pipe schedule 40 with couplings and hangers 250 ft per floor loop x 2 floors x supply and return= 1000 LF $17.45 $17, Chilled ceiling piping (branch) 3/4 in. dia. (average size) Black steel pipe schedule 40 with couplings and hangers 5 ft. from main to panel x 60 panels x supply and return = 600 LF $11.10 $6, Piping Insulation 3/4 in. dia. Piping insulation 600 LF for chilled celing piping (branch) $3.67 $2, Piping Insulation 1.5 in. dia. Piping insulation 1000 LF for chilled ceiling piping (main) $4.08 $2, Piping Insulation 2 in. dia. Piping insulation 1000 LF for radiant a floor piping p $4.41 $2, Chilled ceiling panel 5 ft. Chilled ceiling panel 60 Chilled ceiling panels $ $15, Chilled water pump 1.5 hp. End suction pump package 2 Chilled water pump packages $8, $17, Hot water pump 1.5 hp. End suction pump package 2 Hot water pump packages $8, $17, Variable frequency drive 1.5 hp. Drive for water pump 4 VFD's $2, $9, DOAS AHU 3000 cfm Rooftop air handling unit 1 Unit $13, $13, Outdoor air ductwork (main) 20 in. x 20 in. (average size) aluminum duct includes fittings, joints, supports 200 ft. per floor x 2 floors = 400 LF $33.50 $13, Outdoor air ductwork (branch) 12 in. x 6 in. (average size) aluminum duct includes fittings, joints, supports 10 ft. From main to each room x 40 rooms = 400 LF $9.00 $3, Balancing valve 3/4 in. Thermoflo indicator 1 Valve per panel x 60 panels = 60 valves $ $32, Controls package (water flow) Water flow control 1 Package per heat pump x 60 panels = 60 packages $ $56, Radiant window 48 Volt DC window strips 1 Strip per square foot x 1350 square foot = 1350 strips $35.00 $47, CO 2 Sensor CO 2 Sensor and control 1 Sensor per retail zone x 5 zones = 5 sensors $ $2, Note: This table is based on comparative values, and is not a total initial cost analysis. Subtotal $343, Location Factor Total Cost $301,

39 APPENDIX D.1 - LIFECYCLE COST COMPARISONS Components Replacement Cost Ice Storage Packaged Rooftop Units 20-Year Life Cycle Cost Analysis (Option 1) Replacement Year Replacement Year Worth 60-Year Worth 20-Year Worth Maintenance and Repair Cost/period Period (years) Annual Maintenance 20-Year Worth Initial Cost Operating Cost/yr Packaged rooftop unit $30, $50, $692, $67, $1, $ $4, cfm 30 $84, $484, $47, Qty. (2) 45 $141, $338, $32, $236, $236, $23, Packaged rooftop unit $22, $36, $509, $49, $ $53.00 $2, cfm 30 $61, $355, $34, Qty. (1) 45 $103, $248, $24, $173, $173, $16, Packaged rooftop unit $52, $87, $1,209, $117, $1, $ $4, cfm 30 $147, $845, $82, Qty. (2) 45 $246, $591, $57, $413, $413, $40, "Ice Bear" Unit $43, $86, $890, $86, $5, $1, $39, Ice storage 40 $172, $552, $53, Qty. (5) 60 $342, $342, $33, VAV w/terminal reheat $22, $37, $518, $50, $ $0.00 $ cfm 30 $63, $362, $35, Qty. (29) 45 $105, $253, $24, $177, $177, $17, Control pkg. (VAV) $47, $95, $979, $95, $ $0.00 $0.00 Valve and controls 40 $189, $607, $59, Qty. (29) 60 $376, $376, $36, Totals $1,084, $50, $276, $8, Year Worth $1,084, $50, $886, $339, Year Lifecycle Cost Future Total 20-Year Lifecycle Cost Present Total $2,360, Note: This table is based on comparative values, and is not a total life cycle cost analysis. $736,

40 APPENDIX D.2 - LIFECYCLE COST COMPARISONS Components Replacement Cost Replacement Year Ground Source Heat Pumps 20-Year Life Cycle Cost Analysis (Option 2) Replacement Year Worth 60-Year Worth 20-Year Worth Maintenance and Repair Cost/period Period (years) Annual Maintenance 20-Year Worth Initial Cost Operating Cost/yr Heat pump $55, $109, $1,127, $109, $52, $5, $203, Ton water source 40 $218, $699, $68, Qty. (29) 60 $434, $434, $42, Primary hyd. pump $19, $33, $455, $44, $ $ $6, hp. End suction 30 $55, $318, $30, Qty. (2) 45 $92, $222, $21, $155, $155, $15, Secondary hyd. pump $18, $31, $434, $42, $ $ $6, hp. End suction 30 $52, $303, $29, Qty. (2) 45 $88, $212, $20, $148, $148, $14, Variable freq. drive $4, $8, $111, $10, $ $0.00 $ hp. 30 $13, $78, $7, Qty. (2) 45 $22, $54, $5, $38, $38, $3, Heat pump (DOAS) $3, $7, $80, $7, $4, $ $18, Ton water source 40 $15, $50, $4, Qty. (2) 60 $31, $31, $3, Control pkg. (water) $27, $54, $555, $54, $ $0.00 $0.00 Valve and controls 40 $107, $344, $33, Qty. (29) 60 $213, $213, $20, Control pkg. (air) $18, $36, $376, $36, $ $0.00 $0.00 Valve and controls 40 $72, $233, $22, Qty. (29) 60 $144, $144, $14, Balancing valve $15, $31, $320, $31, $ $0.00 $0.00 3/4 in. 40 $62, $198, $19, Qty. (29) 60 $123, $123, $11, Totals $726, $235, $295, $6, Year Worth $726, $235, $947, $245, Year Lifecycle Cost Future Total 20-Year Lifecycle Cost Present Total $2,154, Note: This table is based on comparative values, and is not a total life cycle cost analysis. $671,

41 APPENDIX D.3 - LIFECYCLE COST COMPARISONS Components Replacement Cost Replacement Year Radiant Heating and Cooling 20-Year Life Cycle Cost Analysis (Option 3) Replacement Year Worth 60-Year Worth 20-Year Worth Maintenance and Repair Cost/period Period (years) Annual Maintenance 20-Year Worth Initial Cost Operating Cost/yr Chiller $34, $68, $704, $68, $35, $3, $137, Ton Air Cooled 40 $136, $436, $42, Qty. (1) 60 $271, $271, $26, Boiler 80 MBH $3, $8, $48, $4, $ $ $5, Qty. (1) 60 $23, $23, $2, Manifolds (PEX) $ $1, $14, $1, $ $0.00 $ in. 40 $2, $9, $ Qty. (5) 60 $5, $5, $ Chilled ceiling panel $15, $25, $345, $33, $ $ $28, ft. 30 $42, $241, $23, Qty. (60) 45 $70, $169, $16, $118, $118, $11, Chilled water pump $17, $29, $407, $39, $ $ $6, hp. End suction 30 $49, $284, $27, Qty. (2) 45 $82, $198, $19, $139, $139, $13, Hot water pump $17, $29, $407, $39, $ $ $6, hp. End suction 30 $49, $284, $27, Qty. (2) 45 $82, $198, $19, $139, $139, $13, Variable freq. drive $9, $15, $209, $20, $ $0.00 $ hp. 30 $25, $146, $14, Qty. (4) 45 $42, $102, $9, $71, $71, $6, AHU (DOAS) $13, $23, $319, $31, $ $53.00 $2, cfm unit 30 $38, $223, $21, Qty. (1) 45 $65, $156, $15, $109, $109, $10, Radiant window $47, $79, $1,089, $105, $ $0.00 $0.00 Window strips 30 $132, $761, $74, Qty. (1350 sf.) 45 $222, $532, $51, $372, $372, $36, Control pkg. (water) $56, $111, $1,149, $111, $ $0.00 $0.00 Valve and controls 40 $222, $713, $69, Qty. (60) 60 $442, $442, $43, CO 2 Sensor $19, $39, $405, $39, $ $ $30, Controls 40 $78, $251, $24, Qty. (5) 60 $155, $155, $15, Balancing valve $32, $64, $663, $64, $ $0.00 $0.00 3/4 in. 40 $128, $411, $39, Qty. (60) 60 $255, $255, $24, Totals $1,262, $216, $301, $8, Year Worth $1,262, $216, $967, $338, Year Lifecycle Cost Future Total 20-Year Lifecycle Cost Present Total $2,785, Note: This table is based on comparative values, and is not a total life cycle cost analysis. $868,

42 APPENDIX E TRACE 700 INPUTS 35 35

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