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THE MCDUSTER: THE NEXT GENERATION OF HVAC SOLAR REACTIVATED DESICCANT DEHUMIDIFICATION & HUMIDIFICATION COUPLED WITH OCEAN SOURCE COOLING, RADIANT SLABS, & HOT WATER STORAGE THE INSTITUTE OF CONTEMPORARY ART FAN PIER, BOSTON By DUSTIN M. EPLEE MECHANICAL OPTION Prepared For The Pennsylvania State University: Department of Architectural Engineering Spring 2005 Senior Thesis Final Report
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Page 1: SOLAR REACTIVATED DESICCANT DEHUMIDIFICATION & H … · house. I used the same radiant floor installation technique on my redesign for this 40+ million dollar museum as I learned

― THE MCDUSTER: ― THE NEXT GENERATION OF HVAC

SOLAR REACTIVATED DESICCANT

DEHUMIDIFICATION & HUMIDIFICATION

COUPLED WITH

OCEAN SOURCE COOLING, RADIANT SLABS, & HOT WATER STORAGE

THE INSTITUTE OF CONTEMPORARY ART FAN PIER, BOSTON

By

― DUSTIN M. EPLEE ― MECHANICAL OPTION

Prepared For

The Pennsylvania State University: Department of Architectural Engineering Spring 2005 Senior Thesis Final Report

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- DUSTIN M. EPLEE -

The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

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- DUSTIN M. EPLEE -

The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Table of Visual Aids…………………………………………………………………………………. 5 Acknowledgments…………………………………………………………………………………… 8 Executive Summary…………………………………………………………………………………. 9 The McDuster Concepts: The Next Generation of HVAC…………………………………….. 10 Existing General Conditions……………………………………………………………………….. 11 Zoning Layout……………………………………………………………………………………….. 13 Existing HVAC Equipment………………………………………………………………………… 17 Ocean Cooling……………………………………………………………………………………… 19

Solar Heating…………………………………………………………………………………………. 27

Desiccant Conditioning…………………………………………………………………………… 29

Radiant Cooling and Heating……………………………………………………………………… 31 McDuster Air-Handling Unit Design….....………………………………………………………… 38 McDuster Psychrometrics: Proving the Concept……………………………………………… 41

Overview of McDuster Simulation Programs…………………………………………………… 49

McDuster Air-Handling Unit Simulation Program……………………………………………. 50 LiCl Desiccant Wheel Simulation Program……………………………………………………. 57 Humidification With Desiccant Wheel Simulation Program………………………………… 58 Flat Panel Solar Collector Simulation Program…………………………………………………. 63 Hot Water Storage Tank Simulation Program…………………………………………………. 67 Existing Design HVAC Energy Usage and Yearly Costs……………………………………… 71 McDuster Design HVAC Energy Usage and Yearly Costs……………………………………. 74

Building Emissions…………………………………………………………………………………. 76 LEED Green Building Certification……………………………………………………………….. 77 Redundancy and Backup…………………………………………………………………………… 80 Lighting Breadth: Existing Conditions………………………………………………………….. 81 Lighting Breadth: Skylight Redesign …………………………………………………………… 84

TABLE OF CONTENTS

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- DUSTIN M. EPLEE -

The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Structural Breadth: Removal of 5th Floor Mez & Storage Tank Sizing……………………. 26

Electrical Breadth: HVAC Demand Reduction………………………………………………… 95

First Cost Economic Analysis…………………………………………………………………….. 97 Life-Cycle Maintenance Economic Analysis…………………………………………………… 99 Overall Life-Cycle Cost Present Worth Analysis………………………………………………. 100 Potential Challenges: Is the System Too Good to be True?………………………………… 101 Conclusions / Recommendations………………………………………………………………… 103 Works Cited…………………………………………………………………………………………… 104 Appendix A: LiCl SECO Desiccant Wheel Quote……………………………………………… 107 Appendix B: Titanium Heat Exchanger Pricing Quote………………………………………. 108 Appendix C: NSTAR Electric and Keyspan Natural Gas Rates……………………………. 113 Appendix D: Existing Design Carrier HAP Program Simulation……………………………. 117 Appendix E: EES Solar Loss Simulation Code………………………………………………… 122 Appendix F: EES Clear Sky Simulation Code………………………………………………….. 124 Appendix G: First Cost Deductions……………………………………………………………… 126 Appendix H: First Cost Redesign Additions…………………………………………………… 128 Appendix I: Existing Life-Cycle Maintenance………………………………………………….. 129 Appendix J: McDuster Redesign Life-Cycle Maintenance…………………………………… 131

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- DUSTIN M. EPLEE -

The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Table 1 – Air Handling Unit Schedule……………………………….……………………………. 13 Diagram 1 – Floor Plan Perspective Showing General AHU Services………………………… 13 Diagram 2 – 1st Floor AHU 3………………………………………………………………………. 14 Diagram 3 – 2nd Floor AHU 3………………………………………………………………………. 14 Diagram 4 – 3rd Floor AHU 3.………………………………………………………………………. 14 Diagram 5 – 4th Floor AHU 5…..........…….………………………………………………………… 15 Diagram 6 – 4th Floor AHU 2…………………………………………………………………………. 15

Diagram 7 – 4th Floor AHU 1………………………….…………………………………………… 16

Diagram 8 – 3rd Floor AHU 4……………………………………………………………………….. 16 Figure 2 – Yearly Subsurface Temperature Variations ………………………………………… 19 Figure 3 – Seasonal Water Stratification in Boston Harbor.……………………………………. 21 Figure 4 - Yearly Surface Water Temperature Variations………………………………………. 21 Figure 5 – Arial Shot of Boston Harbor……………………………………………………………. 22 Figure 6 – Buoy Data Locations……………………………………………………………………. 22 Figure 7 – Site for the New ICA……………………………………………………………………. 23 Figure 8 – Underwater Ocean Topography………………………………………………………. 23 Figure 9 – Boston Harbor Hourly Water Temperature Profile……………………………………. 24 Figure 10 – 1 Meter Deep Yearly Temperature Variations………………………………………. 24 Figure 11 – 2 Meter Deep Yearly Temperature Variations……………………………………. 25 Figure 12 – Boston Harbor Low Water Tide Depths……………………………………………. 26 Figure 13 – Arial View of Water Channels…………………………………………………………. 26 Figure 14 – ASHRAE Desiccant Comparison Chart……………………………………………. 30 Figure 15 – Cross Section of Radiant Slab System………………………………………………. 31 Table 2 – Radiant Floor Average Slab Temperature……………………………………………. 32 Table 3 – Total Heat Exchange Coefficient………………………………………………………. 33

TABLE OF VISUAL AIDS

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- DUSTIN M. EPLEE -

The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Figure 16 – Radiant Circuit Diagrams……………………………………………………………… 33 Table 4 – Radiant Ceiling Average Temperature………………………………………………… 35 Table 5 – Radiant Cooling Simulation Assumptions…………………………………………….. 36 Table 6 – Radiant Ceiling and Floor Calculation…………………………………………………. 37 Figure 17 – McDuster Air-Handling Unit Schematic…………………………………………….. 38 Figure 18 – McDuster Air-Handling Unit Cross Section………………………………………….. 40 Figure 19 – McDuster Numbered Schematic Diagram………………………………………….. 40 Figure 20 – Manufacture’s Interface Desiccant Modeling Software…………………………….. 57 Table 7 – McDuster Desiccant Humidification……………………………………………………. 58 Table 8 – Flat Panel Collector Constants…………………………………………………………. 63 Table 9 – Solar Meteorological Data……………………………………………………………….. 65 Table 10 – Solar Variable Definitions……………………………………………………………… 66 Table 11 – Detailed Zone Comparison……………………………………………………………. 71 Table 12 – Keyspan Natural Gas Pricing Structure………………………………………………. 72 Table 13 – Original Design Energy Breakdown…………………………………………………… 72 Table 14 – HVAC Annual Electricity Cost…………………………………………………………. 73 Table 15 – McDuster HVAC Annual Electricity Cost…………………………………………….. 74 Table 16 – McDuster Pumping and Fan Energy………………………………………………… 74 Table 17 – Estimated Emissions Associated With On-Site Electricity…………………………. 76 Table 18 – Existing ICA Design Emissions………………………………………………………… 76 Table 19 – McDuster ICA Redesign Emissions ………………………………………………….. 76 Table 20 – ICA Redesign Emissions Savings… ………………………………………………….. 76 Table 21 – LEEDS Accreditation Results ………………………………………………………….. 78 Table 22 – ICA Lighting Compliance With ASHRAE Standard 52 ………………………….….. 82 Figure 21 – Mezzanine Shadowing ………………………………………………………………… 84 Figure 22 – Shadow Lines ………………………………………………………………………….. 84 Figure 23 – Uniform Lighting Achieved ……………………………………………………………. 84

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- DUSTIN M. EPLEE -

The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Figure 24 – Existing Northlight Cross Section ……………………………………………………. 85 Figure 25 – Structural Redesign Opening Up Ceiling For Light Diffusity ………………………. 85 Figure 26 – Final North Light Redesign Cross Section ………………………………………….. 85 Figure 27 – Existing Structural Steel ………………………………………………………………. 86 Table 23 – Mechanical Mezzanine Structural Steel Quantity Take Off ……………………….. 88 Figure 28 – Floor Loading Description and Load Path ………………………………………….. 89 Figure 29 – Hot Water Tank and Mezzanine Removal ………………………………………….. 89 Figure 30 – Load Resolved into Pile Caps ………………………………………………………… 90 Table 24 – Existing Pile Cap Reactions …………………………………………………………… 90 Table 25 – ICA Redesign Pile Calculations ……………………………………………………….. 92 Figure 31 – Original Mechanical Room Configuration …………………………………………… 92 Figure 32 – Redesign Mechanical Configuration …………………………………………………. 93 Table 26 – Triangular Truss Roof Structural Steel Quantity Take Off ………………………….. 94 Table 27 – Electrical First Cost Deductions ……………………………………………………… 96 Table 28 – Actual Low Bid Amount ……………………………………………………………….. 97 Table 29 – First Cost Comparison Summary ……………………………………………………… 98

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- DUSTIN M. EPLEE -

The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

I would like to take the time to thank the many who made this thesis project and my five years at the Pennsylvania State University such an incredible and life-changing experience. I would like to thank my fiancée, Jennifer and my family; including Mom, Dad, Lena, and David, for their love, support, and encouragement they have imparted to me throughout my life. I would also like to thank the Architectural Engineering department for the high quality program they have developed and maintained over the years here at Penn State. Specifically, I would like to make special recognition to Dr. Bahnfleth, Dr. Mumma, Dr. Freihaut, Professor Moses, and Dr. Srebric for the imparted knowledge about mechanical systems design. They have always been there for me and have patiently answered even the most ‘profound’ and seemingly impossible questions. The vision for the future of HVAC shown in this report is a mere reflection of the attitude and dedication the instructors this department have. I would like to thank Dr. Riley, my honors thesis advisor for his help and the amazing trip to Montana to build a straw house. I used the same radiant floor installation technique on my redesign for this 40+ million dollar museum as I learned in the scorching heat of that straw-house crawlspace. To all my friends in this amazing AE class of 2005; thank you for your support and encouragement through all five years of my time here at Penn State. Specifically, I would like to thank Andy Kauffman, Nate Patrick, Jesse Fisher, Jason Jones, Brendon Burley, and Kristen Shehab for supporting all my wild and crazy ideas and molding me into the person and engineer I am. More importantly, thank you for your friendship. People and relationships are the most important gift we have been given here on earth. Love them with everything you’ve got. And finally, the most important thing gained while sweating through senior thesis this year: a friend. Cheers to you, Mark Graybill, for making this thesis project what it is. The ‘McDuster’ just wouldn’t have the same ring without you. I look forward to our six weeks on the Appalachian trial and our continued friendship. (Wine glass holds water only:)

Mark Graybill, 2005

ACKNOWLEDGMENTS

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- DUSTIN M. EPLEE -

The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

This report describes the application and performance of a mechanical HVAC system involving solar reactivated desiccant dehumidification and humidification coupled with ocean source cooling, radiant slabs, and hot water storage. The report objectives are: (1) to redesign the mechanical HVAC system for the Institute of Contemporary Art in Boston, Massachusetts, (2) to investigate the feasibility of integrating solar reactivated LiCl desiccant wheels with ocean source cooling, and (3) to embrace and seek the future in building energy utilization. The Institute of Contemporary Art project is currently under construction with an anticipated completion date of July 2006. This redesign includes combining ocean cooling, solar heating, and desiccant conditioning in a way that completely eliminates the chillers, compressors, and cooling towers. With its current heating and humidification system, the Institute of Contemporary art will use approximately 68,020 therms per year for an annual predicted natural gas cost of $78,388. A detailed model was carried out in Carrier’s Hourly Analysis Program showing that the Institute of Contemporary Art is predicted to consume 1,196,640 kW/yr. The annual electricity consumption cost is estimated to be $185,153. Total Annual Utility costs are predicted to be $263,540. The “McDuster” is named after its two founders, the author along with the help of Mark Graybill. The system is unconventional, unusual, and unique as there are few systems like it currently operating in the world. By combining ocean cooling, solar heating, and desiccant conditioning, the entire building’s sensible and latent loads can be met within 50% +/- 5% relative humidity and 73F+/- 2F. Remarkably, this system operates entirely with pump and fan energy alone. Six (6) detailed program simulations were conducted on the Air-Handling Unit, desiccant wheel, flat-panel solar collector, hot water storage tank, radiant slabs, and pumps. The McDuster system results in an 82% reduction in annual energy costs, saving $214,780. The majority of this electricity is used to drive fans moving minimum dedicated outdoor air, thus further energy savings would prove difficult. Furthermore, it is estimated that the first cost of the McDuster system is $143,884 dollars less than the previous system. The present worth savings value of the McDuster system using a discount rate of 4.5% over 25 years is $4,617,810, which completely covers the first cost of the original HVAC system. Dive into this report and learn more about the next generation of HVAC: The McDuster. Its time has come. McDuster Results at a Glance

82% Reduction Annual Energy Cost Reduction ($263,540 to $48,760 Savings=$214,780) $143,884 Lower First Cost 30% Reduction in Annual Maintenance Costs ($34,463) 67% Reduction in Emissions 81% Reduction in Building HVAC Electrical Demand (537 kW to 104kW) Elimination of Natural Gas Line 255,000 Gallons of Potable Water Saved Annually From Humidification LEED Certified Design Elimination of Entire 5th Floor Mezzanine Level Foundation and Wind Load Reduction Improved Natural Daylight Ceiling Uniformity Decrease in HVAC Noise Improved Architectural Image No Chillers, Boilers, Cooling Towers, Humidifiers, VAV boxes, or Fan Coil Units No Refrigerants/CFCs Improved Air Filtering and Quality No Potable Water Used Independent Temperature and Humidity Control Improved Redundancy Guaranteed Minimum Outdoor Air Reaches Each Space Runs Entirely With Pumps and Fans

EXECUTIVE SUMMARY

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- DUSTIN M. EPLEE -

The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

4 Energy Sources

OceanOcean

SunSun

FanFan PumpPump

4 Passive Devices

Heat ExchangerHeat Exchanger

Desiccant WheelDesiccant Wheel

Solar CollectorSolar Collector

Radiant SlabRadiant Slab

The McDuster concepts are simple, although very different than conventional thinking in the field of heating ventilation and air conditioning.

The four (4) sources of energy needed to drive the McDuster system are: (1) the solar radiation from the sun, (2) the thermal heat sink from water less than 64F, (3) the fan energy supplying minimum dedicated outdoor air, and (4) the pump energy to transfer both hot and cool water.

The four (4) passive equipment devices needed to convert the energy into a usable form are: (1) flat plate solar collector, (2) heat exchanger, (3) low reactivation temperature LiCl desiccant wheel, and (4) radiant floor and ceiling.

A thermal storage device in the form of a hot water tank is needed to deliver hot water when the sun is not shining or conditions are unfavorable.

THE MCDUSTER CONCEPTS: THE NEXT GENERATION OF HVAC

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- DUSTIN M. EPLEE -

The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

The new waterfront building will be the primary home for the Institute of Contemporary Art (ICA) in an attempt to house its unparalleled growth rate over the last five years. The ICA is a non-profit institution devoted exclusively to the presentation of contemporary art and has earned its place as one of New England’s most vibrant cultural organizations. Through a comprehensive schedule of exhibitions of local, national, and international significance and a program of educational outreach, the museum provides the public access to contemporary art, artists, and creative processes.

The bold architectural statement from Diller & Scofidio along with a dramatic waterfront location entwine to produce a vibrant, high tech center for thought provoking showcase space, performances, and instructive activities. The Institute of Contemporary Art anticipates developing and displaying a diverse permanent collection of art comprised in various media formats, which have acted as the driving catalyst for the architectural program. The ICA anticipates receiving individual works and complete traveling exhibitions to be displayed in the new building including sculpture, paintings, and drawings. Video and projection pieces may be shown, either as interpretive material accompanying a show, or as art pieces in their own right.

Viewing these works of art in natural daylight was a prime objective of the institution and consequently influenced many of the architectural components comprising the new Institute of Contemporary Art. North facing skylights will facilitate natural light throughout the building’s main gallery halls, which will be located on the 4th floor. Flexibility was key in designing the interior program. Lighting systems were designed to respond effectively and economically as layouts and displays are changed and also to protect artwork from being damaged or faded by exposure to ultraviolet light. The ICA will be graced with an array of lights, illuminating a “floating box” and radiating a warm, welcoming waterfront persona.

Numerous architectural explorations eventually led to a design surprisingly sensible and straightforward: a steel-frame box building with a column-free 4th level that will radically cantilever out over Boston’s harbor. The cantilevered design embraces a public harbor walk and produces ever-changing panoramic spectacles of the water's edge. Collaboration between architect and engineer early in the design process resulted in a highly efficient structure in which structural elements have been fused to create architecture. This planning will result in a 65,000 ft2 building, which appears to float above land and sea.

Design and construction of a new museum in Boston is an uncommon incidence and opportunity. The new building for the ICA will be the first art museum to be built in Boston in almost 100 years and is destined to embody the architectural potentials of the nation’s most historic cities. In that milieu, it is anticipated that the design creates a pioneering breakthrough museum for art of the 21st century.

The planners and designers envisioned an affordable structure with a striking profile, situated on a small lot atop a reclaimed landfill on the shore of Boston Harbor—one that would incorporate the harbor’s shoreline walkway into the ground floor while boasting a contiguous gallery above. With structural and architectural challenges closely intertwined, the project’s architects at New York-based Diller + Scofidio invited engineers from Arup New York to participate early on in the concept phase.

Fan Pier, at 13 million square feet, makes it the largest proposed private development project on the Southern Boston Waterfront. The land is owned by the Chicago-based Pritzker family and is inherently a key piece of Boston's industrial land. The Institute of Contemporary Art is just one of nine buildings proposed to be built along this waterfront land. In order to obtain the proper permits, developer Spaulding & Slye agreed to construct parks, water transportation, and other publicly accessible buildings during the first stages of the Fan Pier development. These public amenities, including the Institute of Contemporary Art, must be completed early in what could be a decade or more of phased construction.

EXISTING GENERAL CONDITIONS

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- DUSTIN M. EPLEE -

The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

A height limitation of 70 feet was imposed early on in the design of the ICA building in order to escape the title and classification of a high rise. This effort was achieved so that additional codes and regulations could be avoided. The overall size of the project is about 60,000 ft2. The total costs for the project are estimated to be in the region of $45 million of which about $ 30 million are allocated for building construction. Construction is planned to be complete by July 2006.

Building “Use” Groups: Assembly (A-3), Offices and Classrooms (B), Bookstore (M) Square Footage: 62,000 ft2 Building height: 69’-11” (plus mezzanine) Number of floors above grade: 4 (plus mezzanine) Number of floors below grade: 0 Square footage per floor: First Floor: 11,055 sf Second Floor: 8,895 sf Third Floor: 6,425 sf Fourth Floor: 18,450 sf Mezzanine 2,575 sf Type(s) of occupancies: Lobby, Dining Room, Retail, Reheat Kitchen, Offices, Classrooms, Bookstore, Library, Theater, Meeting Room Type(s) of construction: Type 2A Construction Hazardous material: None

Site access arrangement for emergency response vehicles: There is a 24’ wide access road approaching the building via a new roadway. This road provides full access to the Southern side and partial access to the Western and Eastern side of the building. The design for the MEP systems and the location of the chillers & AHUs is driven by space and height constraints of the building program and building design (MR). The current design provides adequate access for day-to-day operations and for the maintenance of the equipment. Even with the outside placements of the units the replacement period should not be shorter than the replacement period for standard indoor equipment, ~ 25 years. Most likely equipment malfunction will occur in the first year of operation and will be covered by the warranty for the systems; the maintenance is independent from the placement of the equipment. The ICA will hire a full time facility manager for the building, responsible for the day-to-day operation and maintenance of the building systems.

External design conditions used for the sizing of building mechanical systems were taken from the ASHRAE Fundamentals Handbook, 2001 edition, for:

City: Boston, Massachusetts.

Latitude: 42.4 degrees

Longitude: 71.0 degrees

Elevation: approximately 30 feet

Summer

Design dry bulb 91°F Design wet bulb 73°F Mean coincident wet bulb 73°F Mean coincident dry bulb 87°F Enthalpy at 91°F/73°F 36.8 Btu/lb Enthalpy at 87°F/73°F 36.8 Btu/lb

Winter Design dry bulb 7°F

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- DUSTIN M. EPLEE -

The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

The following diagrams and tables give a visual reference as to the zones that the building was divided up into for purposes of driving an energy model for the Institute of Contemporary Art (ICA). Table 1 shows the five (5) Air Handling Units serving the ICA. Figure 1 gives a 3D perspective as to where each of the AHUs take care of heating and cooling loads. Figures 2 through 8 are general floor plans with each zone labeled. Only those areas with diffusers directly in their region and consequently the largest impact on energy usage where considered in the energy analysis.

ITEM MANUF TYPE LOCATION AREA SERVED SUPPLY FAN

CFM MIN OA CFM

AHU-1 VENTROL CV ROOF EAST GALLERY 21,150 8,010

AHU-2 VENTROL CV ROOF WEST GALLERY 20,890 6,660

AHU-3 VENTROL VAV ROOF LOBBY/ADMIN/SUPPORT 32,150 10,530

AHU-4 VENTROL CV ROOF THEATER 22,500 4,950

AHU-5 AAON CV MEZZ MER MEDIATHEQUE 4,090 490

Table 1- Air Handling Unit Schedule

Diagram 1- Floor Plan Perspective Showing General AHU Services

1st Floor

2nd Floor

3rd Floor

4th Floor

AHU-4

AHU-5

AHU-2

AHU-3

AHU-1

Roof

ZONING LAYOUT

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- DUSTIN M. EPLEE -

The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Diagram 2- 1st Floor AHU 3

Diagram 3- 2nd Floor AHU 3 Diagram 4- 3rd Floor AHU 3

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- DUSTIN M. EPLEE -

The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Diagram 5- 4th Floor AHU 5

Diagram 6- 4th Floor AHU 2

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- DUSTIN M. EPLEE -

The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Diagram 7- 4th Floor AHU 1

Diagram 8- 3rd Floor AHU 4

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- DUSTIN M. EPLEE -

The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Existing Cooling System Cooling media for the Institute of Contemporary Art is chilled water (CHW). Two (2) chillers located along the center spine roof provide chilled water. The total estimated chiller load for the building is 280 tons while each chiller is sized for 140 tons or 50% of the total cooling capacity. Chilled water (35% propylene glycol) will be supplied to the building at 45ºF supply with a return water temperature of 55ºF. A variable volume pumping system distributes water throughout the building. Chillers are acoustically lined to meet strict noise criteria. Existing Heating System Two (2) gas-fired low temperature hot water boilers provide facility heating. Boilers are located on the 4th floor Mezzanine (Mechanical Engineering Room). Each boiler will be sized for 70% of design heating load. Each boiler is sized for an output capacity of 1500 MBH. Boilers are rated at 48 HP, 1600 MBH, when fired with 2000 CFH of 1000 BTU/CF natural gas. The boiler is a two-drum flexible water tube design with a tangent tube water-wall furnace mounted on a heavy steel frame. Top, bottom and sides of the furnace are water-cooled.

Heating media for the facility is low temperature hot water (HHW) and is distributed to a perimeter finned tube radiation system (See Table 13). The HHW is circulated using a primary-secondary pumping system with temperature reset based on outside air temperature. The secondary pumps are variable volume and powered through variable speed drives The maximum water outlet temperature will be 180oF and minimum return water inlet temperature will be 160oF during the heating season. All HHW control valves located at terminal devices are two-port modulating (air handling units heating coils, fan coil units, hot water unit heaters). Outside air, supplied for ventilation to the air-handling units, is preheated by hot water coils.

Existing Humidification System The areas in the building that will require humidification are as follows:

West Gallery (Zone 41)

East Gallery (Zone 38)

North Gallery (Zone 39 and 42)

The design intent was to achieve the required humidity level in these spaces by adding moisture to the air stream in the form of steam. Two (2) gas fired steam generators located in the Mezzanine MER will generate this steam. Each generator is sized for 50% of system capacity to provide low load control and a measure of system security. Steam supply and condensate return piping is comprised of stainless steel. The two air-handling units serving the Galleries (AHUs 1 & 2) are provided with a humidification section built into them including direct steam dispersion grids with connecting control valves.

The Institute of Contemporary Art includes a factory-packaged system to generate low-pressure steam for building humidification processes. The system consists of two boilers, a duplex boiler feed system with one spare feed water pump, a make-up water softener, a chemical feed system, a blow-down separator with after-cooler, and related control systems. The entire system is factory pre-piped and wired, with field connections required only for condensate return, make-up water, drain, fuel and electric power and steam out. The low-pressure boiler for each skid mounted system consists of 15 hp and is of a vertical multi-port design, completely factory assembled and tested as a self-contained unit. Boiler design and construction are in accordance with ASME Section IV Code for low-pressure boilers. The capacity of the each boiler is 518 lb/hr of steam at 10 psig (212°F) for an equivalent 15 boiler horsepower. Each boiler is equipped to fire Natural Gas via full modulation.

EXISTING HVAC EQUIPMENT

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

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Existing Air Handling Units The building is divided into five (5) different zones:

1) The lobby, retail, administration, and dining room spaces on 1st, 2nd and 3rd floor levels are served by a variable air volume (VAV) air-handling unit located on the Center Spine Roof (AHU-3). Air is distributed to different zones through VAV boxes, which will vary the amount of air supplied to each zone based on its cooling or heating needs. AHU-3 includes particulate filters, preheat and cooling coils, supply and return fans. Airside economizer allows energy conservation during non-peak outdoor conditions.

2) A constant air volume (CV) air handling unit located on the Center Spine Roof (AHU-4) serves the theater located on the 2nd and 3rd floor levels. AHU-4 includes particulate filters, preheat, reheat and cooling coils, supply and return fans. Airside economizer allows energy conservation during non-peak outdoor conditions.

3) A constant volume (CV) air handling unit located on the Center Spine Roof (AHU-1) will serve the Permanent Gallery and North Gallery (half of the space) on 4th floor level. AHU -1 includes particulate filters, preheat, reheat and cooling coils, humidifiers, supply and return fans. Airside economizer allows energy conservation during non-peak outdoor conditions.

4) A constant air volume (CV) air-handling unit located on the Center Spine Roof (AHU-2) will serve the Temporary Gallery and North Gallery (half of the space) on 4th floor level. AHU-2 includes particulate filters, preheat, reheat and cooling coils, humidifiers, supply and return fans. Airside economizer allows energy conservation during non-peak outdoor conditions. The two air handling units serving the 4th floor Gallery spaces (AHU-1 and AHU-2) will be cross-connected to provide redundancy to the space in case of failure of one of the units.

5) A constant air volume (CV) air-handling unit located on Mezzanine MER (AHU-5) will serve the Mediatheque on the 4th floor level. AHU-2 includes particulate filters, preheat, reheat and cooling coils, humidifiers, supply and return fans. Airside economizer allows energy conservation during non-peak outdoor conditions.

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

The Institute of Contemporary Art is located adjacent to Boston’s harbor, which completely exchanges its full water volume with the ocean once every three days, according to studies done by the University of Boston. Data gathered from two buoys located within ½ mile of the Institute of Contemporary Art, show that subsurface water temperatures reach a maximum of 62F during September while surface temperatures climax at 68F during the month of August. The lowest temperatures are recorded late January and early February at 34F. Figure 2 shows the yearly water temperature profile from a Boston Harbor Buoy. This diagram, coupled with a multitude of additionally reliable sources was the basis for developing the following equation: Degrees(F)=44.7110227 - 0.0300404944*Hour + 0.0000283877495*Hour^2 - 1.06157207E-08*Hour^3

+ 2.08837105E-12*Hour^4 - 2.07013453E-16*Hour^5 + 7.96406393E-21*Hour^6 (Where hours start with 12:00AM on January 1st and go up to 8,760 hours.)

Figure 2- Yearly Subsurface Temperature Variations In Boston Harbor

Water will be drawn through an open loop from the bay at low tide depths of 43 ft and high tide depths of 52ft and then pumped through two titanium heat exchangers; only to be returned directly to the bottom of the bay. A closed loop water system will be used directly within the Institute of Contemporary Art to mitigate potential problems with fouling. Chilled floors and ceilings then distribute the water throughout the building in order to maximize the potential cooling and heating effects from this unlimited resource. The water is also used in the Air Handling Units where it pre-cools the outdoor air before it reaches the desiccant wheel as well as re-cools it afterward. Two titanium heat exchangers, each sized for 1,373 gpm are incorporated into the design to prevent corrosion and potential problems down the road. The heat exchangers are redundantly sized so that in the event of a failure of one heat exchanger, the system would operate without loss in performance.

OCEAN COOLING

62F Max

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- DUSTIN M. EPLEE -

The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

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Figure 3 – Seasonal Water Stratification in Boston Harbor

Figure 4 – Yearly Surface Water Temperature Variations in Boston Harbor

68F Max

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

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Figure 5 – Arial Shot of Boston Harbor and Location of Institute of Contemporary Art

Figure 6 – Buoy Data Locations

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Figure 7 – Site For the New Institute of Contemporary Art, Boston MA

Figure 8 – Underwater Ocean Topography Affecting Boston Harbor Water Temperatures

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Boston Harbor Hourly Water Temperature Profile @ 40 Feet Below Low Tide

010203040506070

0

1000

2000

3000

4000

5000

6000

7000

8000

Hours (Starting January 1st)

Deg

rees

(F)

Figure 9 – Boston Harbor Hourly Water Temperature Profile

Figure 10 – 1 Meter Deep Yearly Temperature Variations

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

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Figure 11 – 2 Meter Deep Yearly Temperature Variations

Figure 11B – 50 Meter Deep Yearly Temperature Variations

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Figure 12 – Boston Harbor Low Water Tide Depths and Correlating Ocean Piping Intakes/Outlet

Figure 13 – Arial View of Water Channels in Boston Harbor Affecting Water Temperature

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Solar heating has traditionally been overlooked when considering heating needs in non-residential applications; however, their long-term financial and environmental benefits may prove to be a worthwhile investment. The redesign of the Institute of Contemporary Art calls for 13,000 square feet of flat panel solar collectors coupled to a 100,000 gallon hot water storage tank. The economics are justified as large amounts of heating are required during the summer months, when the building is exposed to the most

amount of radiation and when the solar collectors operate at their highest efficiency. The large heating required for this redesign is primarily due to its use as a means to reactivate a Lithium Chloride desiccant wheel for dehumidification and humidification. The solar panels gather enough energy to satisfy the thirst for warm water from the air handling units, radiant floor, desiccant wheels, and domestic hot water.

The diagram on the following page illustrates the basic hot water

layout for the redesign of the Institute of contemporary art. The 100,000 gallon water tank is a seasonal storage device; as it stores excess energy from the summer months and stores it in a well-insulated tank for use when utilizable solar energy becomes scarce. The flat panel solar collectors are located on the roof of the Institute of Contemporary Art, mounted on the south side of north facing skylights. The collector loop contains a water-glycol solution to lower the freezing point and minimize the risk of damage due to the expansion of ice. In order to separate the glycol from the rest of the system, a flat plate heat exchanger is used. A pump circulates cooler water from the bottom of the tank through the heat exchanger and returns the heated water to the top of the tank. This preserves, and even encourages, stratification in the water storage tank by preventing mixing. With this setup, the hottest water can be supplied to the loads where it is needed, being occasionally tempered with cooler water as needed. An auxiliary heater is utilized if the hot water does not sufficiently meet the demands of the loads. The auxiliary heater is only needed for 37,585 kW during the end of January and beginning of February. The auxiliary heat is minimal and is therefore supplied by an electric heater instead of a natural gas heater. The location of the auxiliary heater is best placed inside the storage tank so that off-peak electricity rates can be taken advantage of. On the return path, the cooler water enters the lower end of the storage tank.

SOLAR HEATING

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- DUSTIN M. EPLEE -

The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

A desiccant wheel was chosen to provide both dehumidification and humidification. This technology blends perfectly with the availability of ‘free’ energy from the solar panels and ocean water. Many different types of desiccants were investigated in order to obtain a perfect match to this specific application. Klingenburg, a German based company, holds the manufacturing patents on a lithium chloride (LiCl) wheel capable of reactivating at extremely low temperatures (104F-158 F). LiCl is common in liquid dehumidification systems, but is rarely used as a desiccant applied to a substrate. Nevertheless, this LiCl wheel provided the exact characteristics that were needed in order to take care of the entire latent load of the Institute of Contemporary Art.

A LiCl desiccant wheel (rotor) works by a process of absorption. Absorption is triggered by the partial pressure differences between the air stream and the wheel’s surface.

Source: http://www.klingenburg.de/ENGLISH/F_engl.htm

The wheel diameter for each of three (3) air handling units is 9 feet (2,750 mm). With 10,500 CFM of dedicated outdoor air, they are more than capable of removing the museum’s latent load. This desiccant wheel does not carry over dirt particles, odor, bacteria, or airborne contaminants. The SECO desiccant wheel is driven by a three-phase synchronous motor which has adjustable rpm speed via a frequency inverter. Typically, the wheel has a maximum rotational speed of 20rph and a minimum of 10rph.

The SECO desiccant rotor can function as both an enthalpy wheel as well as an active desiccant wheel. Its dual use has tremendous advantage and promise for future applications. At 10 revolutions per minute, the SECO is transformed into an enthalpy wheel. With speeds decreased to 20 revolutions per hour, the

DESICCANT CONDITIONING

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

wheel becomes the best performing, low temperature desiccant wheel on the market. The matrix is constructed of cellulose which has a very high capacity for moisture. Figure 14, from the ASHRAE fundamentals, shows that lithium chloride (LiCl) is far more absorbent by weight than any other desiccant material. The SECO is characterized by a very high sorption and desorption rate and a high specific capacity while maintaining low reactivation energy and temperatures.

The wheel has no adverse health effects. In fact, the lithium chloride used as the sorbent is able to attract bacteria to its surface. The heated wheel then kills the organism and it is released into the exhaust stream. Some studies suggest that the killed bacteria may not release from the surface of the wheel. Periodically, the wheel should be sprayed with compressed air to release all trapped particles. The wheel, according to the manufacturer, will not freeze up due to low temperatures. It has no further maintenance requirements and is expected to last over twenty years according to the manufacturer.

Figure 14 – ASHRAE Desiccant Comparison Chart

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

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With the air-handling units only supplying minimum ventilation air and the space sensible and latent loads decoupled, additional zone cooling capacity was needed within the Institute of Contemporary Art. Moderate supply temperatures of 64F were available with ocean water temperatures reaching 62F during the peak late summer months. A unique approach was developed to make the most of these moderate temperatures. Chilled radiant floors coupled with chilled radiant ceilings were utilized in each zone to give the biggest cooling impact as well as best thermal comfort for the occupants.

Heated Radiant Floor/Ceiling

To provide optimum thermal comfort and reduce condensation along perimeter glass surfaces, the redesign for the Institute of Contemporary Art calls for placement of heated radiant floors. As described in the next section, the radiant floor is designed for both heating and cooling. Chilled radiant floors require a much more stringent construction parameters than heating applications. Heated Radiant floors were primarily located along perimeter glass surfaces, replacing the existing fin-tube heating system sunk beneath the surface in a channel. In addition, fin-tube heating will be replaced along the north-light windows with a radiantly heated ceiling. Table 3 shows convective heat exchange coefficients used for the design of the radiant heating system. A maximum floor temperature of 84F was used according to most national and international standards (Olesen).

Figure 15 – Cross Section of Radiant Slab System

Chilled Radiant Floor

While hydronic radiant floor systems are widely used to provide heating to a space, very few systems are used for cooling applications. It would seem obvious that the same system could provide cooling due to the high radiant output and close proximity to the occupants. However, as table 3 depicts, the convective

RADIANT COOLING AND HEATING

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

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heat exchange coefficient for floor cooling is significantly lower than for heating. Other factors that limit the application of chilled radiant floors include dew-point temperature, acceptable floor temperature, vertical air temperature difference, and radiant asymmetry.

Figure 15 depicts a typical floor/ceiling cross section. Steel metal decking and poured concrete slabs were common throughout the building. ¾” flexible polyethylene tubes (PEX tubing from Wirsbo Corporation) were laid over the 6” concrete slab at a spacing of 3”. Close spacing was necessary given the moderate temperatures and importance of slab temperature uniformity. These tubes were then covered with 1 ½” lightweight gypcrete to provide both protection and a mechanism to act as a heat sink. Typical slab finishes found in the original design of the building included ½” tile floor or just finish concrete topping coats. Other finishes include lightweight carpeting and wood flooring. It was very important that the topping coat be of a material with a high conductivity so as not to impede the heat transfer from the tubes to the floor surface. Figure 16 shows the radiant floor thermal circuit with average temperature drops of 3.5°F with 9 BTU/hr of thermal absorption.

qabsorbed = Tslab – Twater

Rtotal

qabsorbed = Tslab – Twater

L tube

kpoly ethy lene · Area +

Lgy pcrete

kgy pcrete · Area +

L tile

ktile · Area

Table 2 - Radiant Floor Average Slab Temperature Material Thickness Conductivity Resistivity Q Absorbed Water Temp Slab Surface Delta T (ft) k (BTU/hr/ft/F) R (hr*F/BTU) (BTU/hr) (F) Temperature (F)

3/4" Polyethylene Tube 0.01040 0.202 0.05 9 65.5 68.6 3.1Gypcrete 0.08330 0.453 0.18 9 65.5 68.6 3.1Clay Tile 0.04170 0.398 0.10 9 65.5 68.6 3.1Totals 0.13540 0.34 69.0 3.1

To successfully evaluate the performance of a radiant floor slab cooling system, it was important to take into account comfort, cooling capacity, control, and design. The biggest limiting factor in the performance of a chilled radiant slab floor system is the surface temperature. According to German DNA standards, floor temperatures should not be lower than 68°F for maximum thermal comfort (Simmonds, Peter). Other sources state that for spaces with seated or standing people, floor temperatures should not be lower than 66°F (Olesen). With thermal comfort of very high priority, average floor slab temperatures for the redesign of the Institute of Contemporary Art do not fall below 69°F, with sections nearest to the cold water supply approaching temperatures of 67°F. In order to achieve 69°F average floor surface temperatures, an increase in temperature of only 3 degrees was assumed. The supply temperature is 64°F while the return temperature is 67°F at design conditions. Pumps are sized accordingly.

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Table 3 - Total Heat Exchange Coefficients (BTU)/(hr*ft^2*F)

Heating Cooling Floor Wall Ceiling Floor Wall Ceiling 1.94 1.41 1.06 1.24 1.41 1.94

Note: For floor areas with direct sun the overall heat transfer is up to 3x's greater. (Source: Bjarne W. Olesen)

The heat exchange coefficient used in calculations between the chilled floor and the room was 1.23 BTU/ft2*h*°F, where 0.97 BTU/ft2*h*°F was radiant heat transfer. Table 3 summarizes the total heat exchange coefficients used in both heating and cooling. The design upper limit temperature for all zones was 76°F, giving a high degree of comfort in the spaces. While the maximum theoretical cooling capacity of a radiant floor without direct sunlight is 16 BTU/h*ft2 (Olesen), supply water temperature constraints and high thermal comfort requirements limit the radiant floor designed for the Institute of Contemporary art to a cooling capacity of 9 BTU/h*ft2. However, the majority of the zones within the building are exposed to direct sunlight or radiation due to the exterior façade being predominately glass. In these cases, direct radiation will raise the temperature of the floor slab and significantly increase the rate at which energy is absorbed. For those perimeter areas exposed to direct sunlight, the chilled floor is capable of absorbing up to 26 BTU/h*ft2 (Oleson).

Figure 16 – Radiant Circuit Diagrams

It is recommended by various sources to limit the air temperature difference between ankles (4” level) and the head (44” level) to 5.4°F. Most of the heat exchange between a cooled floor and the space is by radiation, with temperatures occurring at the ankle considerably higher than floor temperatures of 69F. These results have been confirmed experimentally in studies conducted by Michel and Isoardi in 1993.

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Their results show that with a 69°F floor surface temperature, ankle level temperatures are 3F higher at 72°F. With 76 being the maximum operative temperature, a difference of 4 degrees between the head and ankle is predicted. Displacement ventilation, with moderate temperatures of 67°F will be used and may alter these predictions. Due to the low convective heat exchange at a cooled floor, there should not be any thermal comfort problems brought on by excessive draft. Another major limiting factor for the floor temperature and its cooling capacity is dew-point temperature. The redesign calls for stringent humidity control in all areas, with humidity levels not exceeding 55% (57°F dew point) in the gallery spaces and 65% (63 dew point) in all other areas. Humidity sensors will be used throughout the gallery and emergency, fail-safe devices will be utilized.

Chilled Radiant Ceilings

Due to the high thermal loads required in a museum gallery space, radiant floors are not enough to take care of the entire sensible load. Chilled radiant ceilings are proposed along with the chilled radiant floors. Typical radiant ceiling applications are installed in the ceiling grid along with acoustical tile and lighting fixtures. Although they are effective at cooling the space, they do offer a few drawbacks. First, the amount of effective space that can be used is significantly reduced as the panels must share their territory with a variety of other items including lighting fixtures, acoustical paneling, duct diffusers, sprinkler systems, speaker systems, and duct returns. Secondly, additional metal must be bought to act as the medium to transfer the energy. Lastly, they may impinge or inhibit the look and feel of the space. The Institute of Contemporary Art gallery space ceiling is composed of an open weave, translucent fabric that allows natural daylight into the space via north facing skylights. Installing traditional radiant ceilings would have interrupted and possibly destroyed this important concept.

A unique application and type of radiant ceiling was designed for the Institute of Contemporary art to meet the relatively high loads with moderate source temperature supplies of 64°F. Figure 15 depicts a typical

floor/ceiling cross section. Steel metal decking coupled with concrete slabs was prevalent throughout the original design. Aluminum metal clips were mounted directly to the underside of the metal decking at a spacing distance of 4”. These metal clips will hold ¾” flexible polyethylene tubes (PEX tubing from Wirsbo Corporation). The metal decking acts as a heat transfer medium, efficiently transferring cool thermal energy across the entire ceiling. This effectively creates the potential to cool using 100% of the ceiling area. Additional cooling was achieved in critical spaces such as the theater using horizontally mounted metal sheets with the attached polyethylene tubes.

Some additional modifications were made to the ceiling grid in order to accommodate such an unusual application of chilled ceiling. Traditional acoustically treated ceilings were replaced with an open web, metal/plastic ceiling. The ‘holes’ in this ceiling type allow warm air to rise through them and then to pass back down as it is cooled by the metal decking. The acoustical paneling was then hung from the trusses/beams. This would actually improve the acoustical qualities of the space because both sides of the acoustical absorbing material are exposed. Some additional labor would be required. By locating cooled metal decking above lighting fixtures, heat given off by them is directly absorbed and not transmitted into the space.

The heat exchange coefficient used in calculations between the chilled ceiling and the room was 1.94 BTU/ft2*h*°F and between the heated ceiling and the room was 1.06 BTU/ft2*h*°F. Table 3 summarizes the total heat exchange coefficients used in both heating and cooling. The design upper limit temperature for all the spaces was 76°F, maintaining a high degree of comfort in the spaces. Supply water temperature constraints of 64°F limited the cooling capacity of the ceiling to 19 BTU/h*ft2. However, ceilings exposed to direct radiation involving indirect lighting or powerful stage lights may boost the thermal absorption capacity to 38 BTU/h*ft2 (Oleson). The temperature drop between the average supply

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

water of 65 °F and the metal decking is about one degree. Figure 16 shows a thermal circuit diagram for both floor and ceiling radiant cooling. An average temperature of 66°F is maintained across the metal decking with an assumed energy flow of 19 BTU/hr.

Table 4 - Radiant Ceiling Average Temperature Material Length Conductivity Resistivity Q Absorbed Water Temp Slab Surface Delta T (ft) k (BTU/hr/ft/F) R (hr*F/BTU) (BTU/hr) (F) Temperature (F) 3/4" Polyethylene Tube 0.01040 0.202 0.0515 19 65 66.1 1.0Aluminum Alloy 0.08330 102.2 0.0008 19 65 66.1 1.0AISI 1010 Metal Decking .16670 36.9 0.0045 19 65 66.1 1.0Totals 0.26040 0.0568 19 66.0 1

Radiant Floor and Ceiling Calculation Results

The radiant floor and ceiling were modeled using an excel program along with data obtained from Dr. Olesen’s “Possibilities and Limitations of Radiant Floor Cooling”. Table 5 shows a listing of the assumptions made in the analysis while Table 4 shows the summary of the modeling results. Floor areas and ceiling areas were calculated for each zone. Envelope loads were taken from Carrier’s Hourly Analysis Program and then compared to the original sizing data from Arup Consulting Engineers. Other loads such as lighting, equipment, sensible load from people, and sunlight radiation were added individually. Increased absorption through the floor was taken into consideration for those zones in which the envelope load was a significant contribution to the cooling load and located along the exterior of the building.

The results show that the peak-cooling load was met for 46 zones of the 50 modeled. There are two critical areas in which peak loading was not met, the Theater/Stage area (Zone 34&35) and the Long Gallery North (Zone 39&42). Both of these areas have very high cooling loads per unit area. The Theater/Stage area has a cooling load of 116 BTU/ft2 while the Gallery North has a load of 143 BTU/ft2. Given such high cooling density, additional radiant panels were applied on vertical wall surfaces.

The Gallery North consists of a long narrow band of glass facing East-Northeast and acts as a greenhouse during the early morning hours of the summer. During this time, direct sunlight is focused on all floor areas as well as the entire back wall. Cooling Radiant tubes were designed into the wall surface area with a heat exchange coefficient of 1.41 BTU/hr/ft2. These walls would directly absorb the sunlight and help to keep the artwork cool from the direct sunlight. Additional vertical cooling was located in the ceiling and applied to the trusses, with the acoustical paneling running perpendicular. Even with the additional wall cooling, the results show that only 146,171 BTUs of cooling was achieved by the radiant system. With 194,044 BTUs needed to fully meet the loading requirement, 20% of the load remains unmet. However, temperatures would only reach 78°F instead of the designed 76°F. Given that such a high cooling demand occurs infrequently, it can be assumed that the panels would adequately cool this space. Additional factors, such as the slab’s ability to store thermal energy would play a significant role and might keep the space near 76°F. Additional cooling could be naturally transferred in from adjoining spaces.

The Theater and Stage area represented another critical space with anticipated peak loading of 116 BTU/ft2. This space was exposed to large amounts of direct sunlight given that two sides are completely glass. A picture of this theater can be found in the upper left hand corner of the header on this page.

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

However, direct sunlight does not hit any wall surface directly, limiting the vertical cooling potential. Given this fact, vertical cooling panels were hung off the roof rafters only. Acoustical paneling was then staggered at 90-degree angles from these. An open grid wood ceiling was used to disguise the roof rafters. Significant amounts of direct radiation fall upon both the stage floor as well as the ceiling. The radiant ceiling would immediately pick up indirect lighting and significant heat generated by the lighting equipment, improving its cooling ability. Metal clips with heat transfer surfaces were mounted directly to the underside of the wood floor stage, giving the ability to moderately cool this surface. Even with these improvements, the results show that only 410,216 BTU/hr of the needed 520,640 BTU/hr of cooling are achieved. Without taking any other factors into account, the space would reach 78°F during peak loading, which is still within the thermal comfort of most occupants (assumed 50% humidity). The slabs ability to store thermal energy would play a significant role of shifting the peak loading and may keep the space at the designed 76°F. Additionally, the lighting contributes to approximately 83% of the cooling load in this space. According to design documents and the original design intent for this space, the full lighting load would never exceed a duration of 15 minutes. Given this notion, it can be reasonably presumed that the radiant panels do provide adequate cooling for the peak loading of this space.

Assuming that peak ocean water temperatures coincide with the peak cooling load, a three (3) degree change in temperature between the supply water temperatures and return water temperatures were assumed. Supply temperatures of 64°F and return temperatures of 67°F were used to calculate a total peak loading flow rate of 1,243 GPM. The heat exchangers were sized using this flow rate.

Table 5 - Radiant Cooling Simulation Assumptions 1) Constant Volume Ventilation Supply Air 15-20 CFM per Person 2) Minimum Cooling Supply Air Temperature 67F 3) Floor Slab Temperature 69F 4) Ceiling Slab Temperature 66F 5) Cooling Maximum Design Temperature 76F 6) Maximum Ocean Water Temperature: 62F 7) Design Approach through Heat Exchanger: 2F 8) Panel Supply Temperature: 64F 9) Panel Return Temperature 67F

10) Design Temperature Rise Across Panels: 3F 11) Floor coefficients vary based upon direct light 1.24 - 3.72 12) Theater and North Gallery Utilize Wall Cooling

Page 37: SOLAR REACTIVATED DESICCANT DEHUMIDIFICATION & H … · house. I used the same radiant floor installation technique on my redesign for this 40+ million dollar museum as I learned

Page 37

- DUSTIN M. EPLEE -

The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Table 6 - Radiant Ceiling and Floor Calculations For Design Conditions Sens Ceiling Wall Floor Direct Ceiling Wall Floor Required Total Panel % Flow Gain Area Area Area Sun Capacity Capacity Capacity Cooling Cooling Short Loads Rate

Zone Description (BTU/hr) (ft^2) (ft^2) (ft^2) Area (BTU/hr) (BTU/hr) (BTU/hr) (BTU/hr) (BTU/hr) Met? (GPM)1&2 Lobby (Central/Full) 221,122 3,975 0 3,975 3,975 77,115 0 103,509 180,082 180,624 0% Yes 120.4

3 Classroom (102) 33,375 885 0 885 100 17,169 0 9,418 25,923 26,587 0% Yes 17.74 Coat Room (103) 3,119 320 0 320 0 6,208 0 2,778 2,687 8,986 0% Yes 6.05 Bookstore (101) 33,832 985 0 985 0 19,109 0 8,550 26,056 27,659 0% Yes 18.46 Crawlspace (101B) 4,516 410 0 410 0 7,954 0 3,559 4,516 11,513 0% Yes 7.77 Staff Room/Lockers 18,739 595 0 595 0 11,543 0 5,165 15,715 16,708 0% Yes 11.18 Dressing Rooms 9,521 370 0 370 0 7,178 0 3,212 4,823 10,390 0% Yes 6.99 Office (206A) 3,805 80 0 80 80 1,552 0 2,083 3,589 3,635 0% Yes 2.4

10 Storage (209B) 2,539 260 0 260 0 5,044 0 2,257 2,539 7,301 0% Yes 4.911 Green Room (206) 18,156 620 0 620 0 12,028 0 5,382 11,514 17,410 0% Yes 11.612 Storage(209A) 5,766 735 0 735 0 14,259 0 6,380 5,766 20,639 0% Yes 13.813 Bridge (204) 12,392 280 0 280 280 5,432 0 7,291 12,392 12,723 0% Yes 8.514 Corridor (205) 1,981 415 0 415 0 8,051 0 3,602 1,981 11,653 0% Yes 7.815 Prep 1 (209) 28,600 965 0 965 0 18,721 0 8,376 26,440 27,097 0% Yes 18.116 Elevator Lobby (203) 1,743 365 0 365 0 7,081 0 3,168 1,743 10,249 0% Yes 6.817 Classroom (202) 24,052 480 0 480 480 9,312 0 12,499 21,460 21,811 0% Yes 14.518 Darkroom (202C) 1,396 75 0 75 0 1,455 0 651 1,072 2,106 0% Yes 1.419 Storage (202B) 375 50 0 50 0 970 0 434 375 1,404 0% Yes 0.920 Director (314) 10,234 250 0 250 250 4,850 0 6,510 9,586 11,360 0% Yes 7.621 Offices NE (315) 4,410 160 0 160 0 3,104 0 1,389 3,978 4,493 0% Yes 3.022 Offices NE (316-319) 14,429 480 0 480 0 9,312 0 4,166 12,701 13,478 0% Yes 9.023 Board Room (313) 16,948 415 0 415 200 8,051 0 7,074 13,060 15,125 0% Yes 10.124 Offices SE (320) 5,148 155 0 155 155 3,007 0 4,036 4,716 7,043 0% Yes 4.725 Offices SE (321-324) 8,205 390 0 390 0 7,566 0 3,385 7,125 10,951 0% Yes 7.326 Meeting Room (312) 8,642 280 0 280 0 5,432 0 2,430 6,482 7,862 0% Yes 5.227 Corridor (303) 2,404 315 0 315 0 6,111 0 2,734 2,404 8,845 0% Yes 5.928 Open Office (308) 28,199 1,975 0 1,975 0 38,315 0 17,143 23,015 55,458 0% Yes 37.029 Reception (307) 4,989 330 0 330 0 6,402 0 2,864 4,341 9,266 0% Yes 6.230 Copy/Mail (310) 2,570 135 0 135 0 2,619 0 1,172 2,138 3,791 0% Yes 2.531 Pantry (311) 1,214 155 0 155 0 3,007 0 1,345 1,214 4,352 0% Yes 2.932 Storage (309) 863 110 0 110 0 2,134 0 955 863 3,089 0% Yes 2.133 Elevator Lobby (302) 1,743 365 0 365 0 7,081 0 3,168 1,743 10,249 0% Yes 6.8

34&35 Theater and Stage 574,100 4,950 7,500 4,950 4,000 192,060 105,750 112,406 520,640 410,216 21% No 273.536 Upper Theater (301) 7,533 590 0 590 0 11,446 0 5,121 7,533 16,567 0% Yes 11.0

37 Vestibule/Hall (301A-B) 1,337 280 0 280 0 5,432 0 2,430 1,337 7,862 0% Yes 5.2

38 East Gallery (402) 359,805 9,035 0 8,115 2,200 175,279 0 108,630 283,665 283,909 0% Yes 189.339&42 Long Gallery North 194,044 1,355 2,000 1,355 1,355 26,287 84,600 35,284 183,028 146,171 20% No 97.4

40 Mediatheque (403) 40,098 1,010 0 1,010 400 19,594 0 15,711 34,914 35,305 0% Yes 23.541 West Gallery (401) 335,167 7,795 0 7,795 3,000 151,223 0 119,741 268,423 270,964 0% Yes 180.643 Gallery Lobby (400) 2,043 365 0 365 0 7,081 0 3,168 2,043 10,249 0% Yes 6.844 Dining Room (108) 76,178 1,280 0 1,280 1,280 24,832 0 33,331 56,306 58,163 0% Yes 38.845 Storage (112) 2,980 380 0 380 0 7,372 0 3,298 2,980 10,670 0% Yes 7.146 Bookstore Storage 1,139 145 0 145 0 2,813 0 1,259 1,139 4,072 0% Yes 2.747 Bookstore Office (114) 1,396 135 0 135 0 2,619 0 1,172 1,180 3,791 0% Yes 2.548 Corridor (119) 1,146 240 0 240 0 4,656 0 2,083 1,146 6,739 0% Yes 4.549 Food Prep (121) 5,893 410 0 410 0 7,954 0 3,559 5,029 11,513 0% Yes 7.750 Service Area 1,671 180 0 180 0 3,492 0 1,562 1,023 5,054 0% Yes 3.4

Page 38: SOLAR REACTIVATED DESICCANT DEHUMIDIFICATION & H … · house. I used the same radiant floor installation technique on my redesign for this 40+ million dollar museum as I learned

Page 38

- DUSTIN M. EPLEE -

The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

The “McDuster” is named after its two founders, the author and Mark Graybill. The system is unconventional, unusual, and unique as there are few systems like it currently operating in the world. By combining ocean cooling, solar heating, and desiccant conditioning, the entire building’s sensible and latent loads can be met within 50% +/- 5% relative humidity and 73F+/- 2F. Remarkably, this system operates entirely off of pump and fan power alone. There are a few hours out of the year in which a combination of extreme weather conditions and low solar levels necessitate the use of electric coil heating. Although electric heat is inefficient and expensive, given the rare cases that it would be used and the low first cost, it is a suitable method of heating for this application.

Figure 17 – McDuster Air-Handling Unit Schematic

The McDuster consists of one (1) enthalpy wheel and one (1) active desiccant wheel in series. Together, these wheels are capable of both humidifying and dehumidifying the museum for the entire year, even in dry winter conditions. The Supply Air stream includes one (1) ocean-heated pre-heat coil, one (1) fan, two (2) ocean-cooled cooling coils, two (2) solar heating coils, and one (1) run-around heating system. A bypass around the desiccant wheel is provided for cases in which the desiccant wheel is off and modulating because damage can occur to the wheel if it is left in moist air stream. The LiCl desiccant will

MCDUSTER AIR-HANDLING UNIT DESIGN

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Page 39

- DUSTIN M. EPLEE -

The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

continue to absorb moisture making the weight balance unequal on the wheel. The return air stream includes one (1) enthalpy wheel, (1) sensible wheel, (1) desiccant wheel, and (1) solar heating coils.

To minimize fan energy and the size of the air-handling unit, only ventilation air is passed through in the McDuster system. The cooling and heating that cannot be accomplished with this airflow rate would be achieved through separate radiant floors and ceilings. An electric heating element is placed at the top of the hot water storage tank to maintain a high quality temperature (<158). This can be run during times of off peak rates, as losses from the tank are minimal.

Salt water is pumped via a 1,000 ft long, 10” diameter polyethylene tube reaching depths up to 50 ft beneath the

surface of the ocean to a heat exchanger where it gives up its cooling energy. The water is then gravity driven back into the bay. Both the pump and the heat exchanger are made of corrosion resistant materials such as titanium and stainless steel. A closed loop system within the building keeps corrosion down to a minimum and also decreases pumping energy. There are no CFC’s in the system, with water being the only refrigerant.

All the components in the system are used in both the summer and winter. During humid, summer conditions, cool ocean water is pumped through the radiant floor cooling the space as well as brought through the cooling coils. Typically, the ocean water is not cold enough to dehumidify so the desiccant wheel rotates to compensate. The desiccant wheel is reactivated by solar heated water between temperatures of 104F to 158F. Temperatures above 140F are occasionally needed and would also be run by the solar heated water when available or the electric heaters would give it a boost.

During cold, dry conditions, the ocean water is used to ‘preheat’ the air above the freezing point. The desiccant wheel can be run in ‘reverse’ to draw moisture out of the return air and into the supply air stream. A hot water storage tank is employed to allow for energy use during the night or times when solar radiation is not available. The 100,000 gallon storage tank sized for the Institute of Contemporary Art is big enough to provide heating, dehumidification, and humidification energy. Overall, the McDuster is a straightforward combination of ocean source cooling, solar heating, and desiccant conditioning.

The diagram below shows a three-dimensional representation of what the McDuster Air Handling unit would look like if it were constructed. The dimensions are 17ft high X 9 feet wide X 46 ft long. The unit is sized for 10,500 CFM of dedicated outdoor air. The desiccant wheel diameter is 2,750 mm (9ft). The LiCl desiccant wheel by Klingenburg also can be run as an efficient enthalpy wheel. Thus, each unit actually has two SECO desiccant wheels positioned in series. The original units, producing 4 times the CFM rating, were sized at 17ft high X 10ft wide X 40ft long. For the amount of air passing through the McDuster air-handling unit, it is rather large. This is due to the fact that airflow through the desiccant wheel should be maintained at 2 m/s (400ft/min) to provide the best absorption. Lower flow velocities will produce laminar flows through the wheel and significantly decrease the absorption rates.

Page 40: SOLAR REACTIVATED DESICCANT DEHUMIDIFICATION & H … · house. I used the same radiant floor installation technique on my redesign for this 40+ million dollar museum as I learned

Page 40

- DUSTIN M. EPLEE -

The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Figure 18 – McDuster Air-Handling Unit Cross Section

Figure 19 – McDuster Numbered Schematic Diagram

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Page 41: SOLAR REACTIVATED DESICCANT DEHUMIDIFICATION & H … · house. I used the same radiant floor installation technique on my redesign for this 40+ million dollar museum as I learned

Page 41

- DUSTIN M. EPLEE -

The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

The System operates in many different modes depending on outdoor air conditions and interior room loads. The following charts give insight into how the system behaves at various design conditions.

• Dehumidification, Cooling, Full Occupancy, Summer Design Drybulb, 62F Ocean Water Temp

• Dehumidification, Cooling, Full Occupancy, 55F Ocean Water Temp

• Dehumidification, Cooling, Full Occupancy, 45F Ocean Water Temp

• Dehumidification, Cooling, Full Occupancy, <= 38F Ocean Water Temp

• Humidification, Heating, Full Occupancy, Winter Design Drybulb, Modulating Enthalpy Wheel

• Humidification, Heating, No Occupancy, Winter Design Drybulb

• Humidification, Heating, No Occupancy, Winter Design Drybulb/Wetbulb (Extremely Dry)

MCDUSTER PSYCHROMETRICS: PROVING THE CONCEPT

Page 42: SOLAR REACTIVATED DESICCANT DEHUMIDIFICATION & H … · house. I used the same radiant floor installation technique on my redesign for this 40+ million dollar museum as I learned

Page 42

- DUSTIN M. EPLEE -

The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

20 25 30 35 40 45 50 55 60 65 70 75 80 85 90 95 100 105 110 115 120

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PSYCHROMETRIC CHARTSea LevelBAROMETRIC PRESSURE 29.921 inches of Mercury

Linric Company Psychrometric Chart, www.linric.com

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DehumidificationCoolingSummer Design DryBulbFull OccupancyMinimum Regeneration Temperature

• Point 1-2: 10, 500 CFM of outdoor air passes through

preheat coil (Off)

• Point 2-3: Supply air is dehumidified and cooled by the enthalpy wheel (Eff=.80)

• Point 3-4: Supply air picks up three (3) degrees from the fan and motor

• Point 4-5: Cooling coil supplied by 62F ocean water cools the air to 67F

• Point 5-6: Supply air passes through the heating coil (Off)

• Point 6-7: Supply air is dehumidified and heated by desiccant wheel

• Point 7-8: A second cooling coil, supplied by 62F ocean water, re-cools supply air to 67F

• Point 8-9: Supply air passes through the second heating coil (Off)

• Point 9-10: The supply ventilation air partially cools and entirely dehumidifies the space

• Point 10-11: 73F and 50% return air is humidified and heated by the enthalpy wheel (Eff= .80)

• Point 11-12: 9,450 CFM of return air picks up three (3) degrees from the internal motor/fan

• Point 12-13: Return air is pre-heated to 103F by the sensible wheel (Eff= .85)

• Point 13-14: Return air is heated up to 136F with 374,220 Btu/hr of solar originating hot water

• Point 14-15: Return air reactivates the desiccant wheel: picks up moisture, gives off heat

• Point 15-16: Heat recovered by sensible wheel (Eff= .85) and exhausted out of the building

• Energy: COP= 823,368 / 838,026 = .98

Page 43: SOLAR REACTIVATED DESICCANT DEHUMIDIFICATION & H … · house. I used the same radiant floor installation technique on my redesign for this 40+ million dollar museum as I learned

Page 43

- DUSTIN M. EPLEE -

The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

20 25 30 35 40 45 50 55 60 65 70 75 80 85 90 95 100 105 110 115 120

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PSYCHROMETRIC CHARTSea LevelBAROMETRIC PRESSURE 29.921 inches of Mercury

Linric Company Psychrometric Chart, www.linric.com

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DehumidificationCooling/HeatingSummer Design DryBulbFull Occupancy55F Ocean Water Available (60F Supply Air)

• Point 1-2: 10, 500 CFM of outdoor air passes through preheat

coil (Off)

• Point 2-3: Supply air is dehumidified and cooled by the enthalpy wheel (Eff=.80)

• Point 3-4: Supply air picks up three (3) degrees from the fan and internal motor

• Point 4-5: Cooling coil supplied by 55F ocean water cools the air to 60F

• Point 5-6: Supply air passes through the heating coil (Off)

• Point 6-7: Supply air is dehumidified and heated by desiccant wheel

• Point 7-8: A second cooling coil, supplied by 55F ocean water, re-cools supply air to 60F

• Point 8-9: Supply air passes through the second heating coil (Off)

• Point 9-10: The supply ventilation air partially cools and entirely dehumidifies the space

• Point 10-11: 73F and 50% return air is humidified and heated by the enthalpy wheel (Eff= .80)

• Point 11-12: 9,450 CFM of return air picks up three (3) degrees from the fan and internal motor

• Point 12-13: Return air is pre-heated to 97F by the sensible wheel (Eff= .85)

• Point 13-14: Return air is heated up to 126F with 295,974 Btu/hr of solar originating hot water

• Point 14-15: Return air reactivates the desiccant wheel: picks up moisture and gives off heat

• Point 15-16: Heat recovered by sensible wheel (Eff= .85) and exhausted out of the building

Page 44: SOLAR REACTIVATED DESICCANT DEHUMIDIFICATION & H … · house. I used the same radiant floor installation technique on my redesign for this 40+ million dollar museum as I learned

Page 44

- DUSTIN M. EPLEE -

The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

20 25 30 35 40 45 50 55 60 65 70 75 80 85 90 95 100 105 110 115 120

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PSYCHROMETRIC CHARTSea LevelBAROMETRIC PRESSURE 29.921 inches of Mercury

Linric Company Psychrometric Chart, www.linric.com

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DehumidificationCooling/HeatingSummer Design DryBulbFull Occupancy45F Ocean Water AvailableHalf Flow Regeneration Stream (4,725 CFM)

• Point 1-2: 10, 500 CFM of outdoor air passes through

preheat coil (Off)

• Point 2-3: Supply air is dehumidified and cooled by the enthalpy wheel (Eff=.80)

• Point 3-4: Supply air picks up three (3) degrees from the fan and internal motor

• Point 4-5: Cooling coil supplied by 45F ocean water cools and dehumidifies the air to 50F

• Point 5-6: Supply air passes through the heating coil (Off)

• Point 6-7: Supply air is dehumidified and heated by desiccant wheel

• Point 7-8: A second cooling coil, supplied by 45F ocean water, re-cools supply air to 67F

• Point 8-9: Supply air passes through the second heating coil (Off)

• Point 9-10: The supply ventilation air partially cools and entirely dehumidifies the space

• Point 10-11: 73F and 50% return air is humidified and heated by the enthalpy wheel (Eff= .80)

• Point 11-12: 9,450 CFM of return air picks up three (3) degrees from internal motor/fan

• Point 12-13: Return air passes through sensible wheel (Off)

• Point 13-14: Return air is heated up to 117F with 268,417 Btu/hr of solar originating hot water

• Point 14-15: Return air reactivates the desiccant wheel: picks up moisture and gives off heat

• Point 15-16: Return air passes through sensible wheel (Off) and is exhausted out of the building

Page 45: SOLAR REACTIVATED DESICCANT DEHUMIDIFICATION & H … · house. I used the same radiant floor installation technique on my redesign for this 40+ million dollar museum as I learned

Page 45

- DUSTIN M. EPLEE -

The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

20 25 30 35 40 45 50 55 60 65 70 75 80 85 90 95 100 105 110 115 120

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PSYCHROMETRIC CHARTSea LevelBAROMETRIC PRESSURE 29.921 inches of Mercury

Linric Company Psychrometric Chart, www.linric.com

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DehumidificationCooling/HeatingSummer Design DryBulbFull Occupancy<= 38F Ocean Water Available

• Point 1-2: 10, 500 CFM of outdoor air passes through preheat coil (Off)

• Point 2-3: Supply air is dehumidified and cooled by the enthalpy wheel (Eff=.80)

• Point 3-4: Supply air picks up three (3) degrees from the fan and motor

• Point 4-5: Cooling coil supplied by <=38F ocean water cools the air to 67F

• Point 5-6: Supply air passes through the heating coil (Off)

• Point 6-7: Supply air bypass the desiccant wheel (Off)

• Point 7-8: A second cooling coil, supplied by <=38F ocean water, cools and dehumidifies supply air to 43F, 42 gr/lb

• Point 8-9: Supply air re-heated to 67F with 38,880 Btu/hr of solar originating hot water

• Point 9-10: The supply ventilation air cools and entirely dehumidifies the space

• Point 10-16: 9,450 CFM of return air (73F and 50%) is humidified and heated by the enthalpy wheel (Eff= .80)

• Energy: COP= 823,368 BTU / 896,322 BTU = .92

Page 46: SOLAR REACTIVATED DESICCANT DEHUMIDIFICATION & H … · house. I used the same radiant floor installation technique on my redesign for this 40+ million dollar museum as I learned

Page 46

- DUSTIN M. EPLEE -

The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

-30 -25 -20 -15 -10 -5 0 5 10 15 20 25 30 35 40 45 50 55 60 65 70 75 80 85 90 95 100 105 110 115 120 125 130 135 140 145 150 155 160 165 170 175 180

DRY BULB TEMPERATURE - °F

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-5

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SATU

RAT

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TEM

PER

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- °F

-25 -20 -15 -10 -50

05

510

1015

1520

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40 45

45 50

50 55

55 60

60 65

6570

7075

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95 WET BULB TEMPERATURE - °F

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100

10% RELATIVE HUMIDITY20%

30%

40%

50%

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90%

12.0

13.0

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15.0 SPECIFIC

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ME ft³/lb O

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Y AIR

16.0

17.0

HU

MID

ITY

RAT

IO -

GR

AIN

S O

F M

OIS

TUR

E PE

R P

OU

ND

OF

DR

Y AI

R

PSYCHROMETRIC CHARTSea LevelBAROMETRIC PRESSURE 29.921 inches of Mercury

Linric Company Psychrometric Chart, www.linric.com

.1

.2

.3

.4

.5

.6

.7

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.9

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- °F

1

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211

3

4

14

67

16

95

9,450 CFM Exhaust Air(DB=67.8F, W=6.0 gr/lb)

10,500 CFM Supply Air(DB= 86.6 F, W= 55.2 gr/lb)

HumidificationHeatingWinter Design DrybulbNo OccupancyRegeneration Temperature at Maximum

• Point 1-2: Preheat coil heats 10,500 CFM of outdoor air

with ocean source heating

• Point 2-3: Supply air is humidified and heated by the enthalpy wheel (Eff= .80)

• Point 3-4: Supply air picks up three (3) degrees from the fan and internal motor

• Point 4-5: Run-around heat exchanger preheats supply air to 114F (Eff= .70)

• Point 5-6: Supply air is heated up to 158F with 498,960 Btu/hr of solar originating hot water

• Point 6-7: Supply air is further humidified and cooled by the desiccant wheel

• Point 7-8: Energy recovered through the run-around heat exchanger connecting coils

• Point 8-9: Supply air passes through the second heating coil (Off)

• Point 9-10: The warm and humidified air enters the space, providing complete humidification

• Point 10-11: 73F and 50% return air is dehumidified and cooled by the enthalpy wheel (Eff= .80)

• Point 11-12: Return air picks up three (3) degrees from the fan and internal motor

• Point 12-13: Return air passes through sensible wheel (Off)

• Point 13-14: Return air passes through the heating coil (Off)

• Point 14-15: LiCl Desiccant wheel absorbs moisture and releases heat to return air

• Point 15-16: Return air passes through sensible wheel (Off) and is exhausted out of the building

Page 47: SOLAR REACTIVATED DESICCANT DEHUMIDIFICATION & H … · house. I used the same radiant floor installation technique on my redesign for this 40+ million dollar museum as I learned

-30 -25 -20 -15 -10 -5 0 5 10 15 20 25 30 35 40 45 50 55 60 65 70 75 80 85 90 95 100 105 110 115 120 125 130 135 140 145 150 155 160 165 170 175 180

DRY BULB TEMPERATURE - °F

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RAT

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TEM

PER

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- °F

-25 -20 -15 -10 -50

05

510

1015

1520

2025

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3035

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45 50

50 55

55 60

60 65

6570

7075

75

80

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85

85

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95 WET BULB TEMPERATURE - °F

95

100

10% RELATIVE HUMIDITY20%

30%

40%

50%

60%

70%

80%

90%

12.0

13.0

14.0

15.0 SPECIFIC

VOLU

ME ft³/lb O

F DR

Y AIR

16.0

17.0

HU

MID

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RAT

IO -

GR

AIN

S O

F M

OIS

TUR

E PE

R P

OU

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Y AI

R

PSYCHROMETRIC CHARTSea LevelBAROMETRIC PRESSURE 29.921 inches of Mercury

Linric Company Psychrometric Chart, www.linric.com

.1

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.4

.5

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.7

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.9

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1.1

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95

DEW

PO

INT

- °F

1

10

2

311

4

16

HumidificationHeatingWinter Design DrybulbFull OccupancyEnthalpy Wheel Modulating

Enthalpy Wheel Modulating(Effectiveness= 69%)

10,500 CFM Supply Air(DB= 59.1F, W= 41.7 gr/lb)

9,450 CFM Exhaust Air(DB= 43.5 F, W=23 gr/lb)

• Point 1-2: Preheat coil warms air to 32F with ocean source heating

• Point 2-3: Supply air is humidified and heated by the enthalpy wheel (Eff= .67)

• Point 3-4: Supply air picks up three (3) degrees from the fan and internal motor

• Point 4-5: Supply air passes through first coiling coil (Off)

• Point 5-6: Supply air bypasses first heating coil (Off)

• Point 6-7: Supply air bypasses desiccant wheel (Off)

• Point 7-8: Supply air passes through second coiling coil (Off)

• Point 8-9: Supply air heated to 67F by second heating with solar source energy

• Point 9-10: The warm and humidified air enters the space

• Point 10-11: 73F and 50% Return Air is dehumidified and cooled by the enthalpy wheel

• Point 11-12: Return air picks up three (3) degrees from the fan and motor

• Point 12-13: Return air bypasses sensible wheel (Off)

• Point 13-14: Return air bypasses heating coil (Off)

• Point 14-15: Return air bypasses desiccant wheel (Off)

• Point 15-16: Return air is exhausted out of the building

Page 48: SOLAR REACTIVATED DESICCANT DEHUMIDIFICATION & H … · house. I used the same radiant floor installation technique on my redesign for this 40+ million dollar museum as I learned

Page 48

- DUSTIN M. EPLEE -

The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

-30 -25 -20 -15 -10 -5 0 5 10 15 20 25 30 35 40 45 50 55 60 65 70 75 80 85 90 95 100 105 110 115 120 125 130 135 140 145 150 155 160 165 170 175 180

DRY BULB TEMPERATURE - °F

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ENTH

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Y AI

R

-5

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5

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- °F

-25 -20 -15 -10 -50

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510

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50 55

55 60

60 65

6570

7075

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95 WET BULB TEMPERATURE - °F

95

100

10% RELATIVE HUMIDITY20%

30%

40%

50%

60%

70%

80%

90%

12.0

13.0

14.0

15.0 SPECIFIC

VOLU

ME ft³/lb O

F DR

Y AIR

16.0

17.0

HU

MID

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RAT

IO -

GR

AIN

S O

F M

OIS

TUR

E PE

R P

OU

ND

OF

DR

Y AI

R

PSYCHROMETRIC CHARTSea LevelBAROMETRIC PRESSURE 29.921 inches of Mercury

Linric Company Psychrometric Chart, www.linric.com

.1

.2

.3

.4

.5

.6

.7

.8

.9

1

1.1

1.2

1.3

1.4

1.5

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VAPO

R P

RES

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10 20 25 30 35

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DEW

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- °F

1

10

2

3

11

4

14

6

7

16

59

Supply Air @ Dryest Design Conditions(87F and 54.3 gr/lb)

Relative Humidity= 48%(Still within 45% to 55% Range)

Design Winter ConditionsTemperature=7FHumidity= 5 gr/lb

HumidificationHeatingWinter Design Drybulb and WetbulbNo OccupancyRegeneration Temperature at Maximum

• Point 1-2: Preheat coil heats 10,500 CFM of outdoor air

with ocean source heating

• Point 2-3: Supply air is humidified and heated by the enthalpy wheel (Eff= .80)

• Point 3-4: Supply air picks up three (3) degrees from the fan and internal motor

• Point 4-5: Run-around heat exchanger preheats supply air to 114F (Eff= .70)

• Point 5-6: Supply air is heated up to 158F with 498,960 Btu/hr of solar originating hot water

• Point 6-7: Supply air is further humidified and cooled by the desiccant wheel

• Point 7-8: Energy recovered through the run-around heat exchanger connecting coils

• Point 8-9: Supply air passes through the second heating coil (Off)

• Point 9-10: The warm and humidified provides humidification within tolerances 50% +/- 5%

• Point 10-11: 73F and 50% return air is dehumidified and cooled by the enthalpy wheel (Eff= .80)

• Point 11-12: Return air picks up three (3) degrees from the fan and internal motor

• Point 12-13: Return air passes through sensible wheel (Off)

• Point 13-14: Return air passes through the heating coil (Off)

• Point 14-15: LiCl Desiccant wheel absorbs moisture and releases heat to return air

• Point 15-16: Return air passes through sensible wheel (Off) and is exhausted out of the building

Page 49: SOLAR REACTIVATED DESICCANT DEHUMIDIFICATION & H … · house. I used the same radiant floor installation technique on my redesign for this 40+ million dollar museum as I learned

Page 49

- DUSTIN M. EPLEE -

The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Six (6) detailed program simulations were conducted on the Air-Handling Unit, desiccant wheel, flat-plate solar collector, hot water storage tank, radiant slabs, and pumps. A brief explanation of each follows with a greater amount of detail explained in their respective sections of the report.

McDuster Air Handling Unit Simulation: This model represents the most significant accomplishment in simulating this system. Its extensive nature cannot possibly be conveyed in words or by this report. Microsoft Excel and visual basic were utilized to provide detailed energy calculations at each point the air travels through the air-handling unit. Hourly envelope loads were taken from the HAP’s Hourly Analysis program and inserted into the model. All additional loads were independently controlled and simulated with pain staking accuracy. The McDuster Air Handling Simulation takes over 24 hours to run and calculates energy results for each hour out of the year. The simulation actually exceeded the maximum columns available in Excel.

SECO Lithium Chloride Desiccant Wheel Simulation: This model represents the first true LiCl desiccant wheel simulation at the Pennsylvania State University to date. It uses actual manufacture’s simulation software and links it with Microsoft Excel. Visual basic was utilized extensively to allow the manufacture’s “.dll” file to properly format into Excel. The program calculates, with a high degree of accuracy, the reactivation temperatures needed and the resulting exiting temperatures.

Flat Panel Solar Collector Simulation Program: A thorough analysis into the performance and losses associated with flat panel solar collectors. Extensive arrays of variables were needed to truly assess their performance. Results closely matched with previously know simulation cases.

Hot Water Storage Tank: An hourly model of how the energy in the hot water storage tank changes over a year.

Radiant Chilled/Heated Floors and Ceilings: Extensive calculations were done to assess the radiant floor and ceiling cooling capacity at design loading conditions.

Pumping Energy: With the substantial use of pumping energy, this model helps to better understand the actual energy associated with the McDuster system.

OVERVIEW OF MCDUSTER SYSTEM SIMULATION PROGRAMS

Page 50: SOLAR REACTIVATED DESICCANT DEHUMIDIFICATION & H … · house. I used the same radiant floor installation technique on my redesign for this 40+ million dollar museum as I learned

Page 50

- DUSTIN M. EPLEE -

The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Simulation Assumptions

• Ocean temperature does not exceed 62F

• Weather design conditions are based off of Carrier’s HAP program

• Snow buildup can be removed by running solar pumps in ‘reverse’

• Occupancy varies of a course of the day and is the same in both simulations.

• The energy consumption of one (1) air handling unit can be multiplied by 3 to obtain the entire building’s performance

• Supply Air temperature minimum is 67F.

• Energy to turn the Desiccant Wheel (20 revolutions per hour) is minimal and thus ignored.

• Economic analysis is based off of existing estimates done from Arup

• Desiccant wheel performance does not degrade over time

• Enthalpy wheel effectiveness of .80 was assumed

• Heat Exchanger effectiveness of .85 during summer months (not a factor outside of summer)

• Duct leakage 3%

• Return air is 10% less than supply air due to pressurization

• Assumed north facing skylights can be redesigned to accommodate 45 degree angles.

• Chilled floors produce adequate comfort levels

• Delta T across chilled floors does not exceed 4F due to comfort issues

Original Design Energy Breakdown

Electric Power Grid37.5%

Natural Gas62.5%

McDuster Energy Source

Ocean66.5%

Sun21.9%

ElectricPower Grid

11.6%

MCDUSTER AIR-HANDLING UNIT SIMULATION PROGRAM

Page 51: SOLAR REACTIVATED DESICCANT DEHUMIDIFICATION & H … · house. I used the same radiant floor installation technique on my redesign for this 40+ million dollar museum as I learned

Page 51

- DUSTIN M. EPLEE -

The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Original Design Energy BreakdownReturn Fan

4.5%

Terminal Heating28.7%

Cooling Equip0.2%

Supply Fan6.7%

Humidifier13.2%

Cooling Coil41.8%

Preheat Coil1.9%

Central Cooling0.4%

Central Heating2.7%

McDuster Electrical Energy Breakdown

Supply Fan45.5%

Ocean Pump2.0%

Solar Panel Pump0.4%

Booster Electric Heat

9.4%

Return Fan41.0%

Radiant Floor Pump0.4%

Heating Coil Pump0.7%

Cooling Coil Pump0.6%

Page 52: SOLAR REACTIVATED DESICCANT DEHUMIDIFICATION & H … · house. I used the same radiant floor installation technique on my redesign for this 40+ million dollar museum as I learned

Page 52

- DUSTIN M. EPLEE -

The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

McDuster Electric Energy Breakdown

Fan Energy86.5%

Pump Energy4.1%

Booster Electric Energy9.4%

McDuster Energy Breakdown (All Sources)

Radiant Cooling28.4%

Heating Coil Reheat2.6%

Electric Power Grid10.2%

Preheat Coil2.1% Cooling Coil Before Wheel

6.2%

Fan Heating12.6%

Heating Coil Humidification

8.0%

Cooling Coil After Wheel21.3%

Heating Coil Dehumidification

8.5%

Page 53: SOLAR REACTIVATED DESICCANT DEHUMIDIFICATION & H … · house. I used the same radiant floor installation technique on my redesign for this 40+ million dollar museum as I learned

Page 53

- DUSTIN M. EPLEE -

The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Air Handling Unit Energy Breakdown

Ocean52%Sun

33%

Fan Electric15%

Air Handling Unit Energy Breakdown

Heating Coil Dehumidification17.4%

Cooling Coil After Wheel

43.7%

Cooling Coil Before Wheel

12.8%

Preheat Coil4.4%

Heating Coil Humidification

16.5%

Heating Coil Reheat5.3%

Page 54: SOLAR REACTIVATED DESICCANT DEHUMIDIFICATION & H … · house. I used the same radiant floor installation technique on my redesign for this 40+ million dollar museum as I learned

Page 54

- DUSTIN M. EPLEE -

The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Original HVAC Electric Demand

0

100

200

300

400

500

600

1-Jan 20-Feb 10-Apr 30-May 19-Jul 7-Sep 27-Oct 16-Dec

Day

Tota

l Ele

ctri

c De

man

d (k

W)

McDuster HVAC Energy Demand

0

100

200

300

400

500

600

1-Jan 20-Feb 10-Apr 30-May 19-Jul 7-Sep 27-Oct 16-DecDay

Tota

l Ele

ctri

c D

eman

d (k

W)

Page 55: SOLAR REACTIVATED DESICCANT DEHUMIDIFICATION & H … · house. I used the same radiant floor installation technique on my redesign for this 40+ million dollar museum as I learned

Page 55

- DUSTIN M. EPLEE -

The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Original HVAC Natural Gas Demand

0

500,000

1,000,000

1,500,000

2,000,000

2,500,000

1-Jan 20-Feb 10-Apr 30-May 19-Jul 7-Sep 27-Oct 16-Dec

Day

Tota

l Ele

ctric

Dem

and

(BTU

/hr)

McDuster Energy Demand Using Off-Peak Booster Heating

0

20

40

60

80

100

120

1-Jan 20-Feb 10-Apr 30-May 19-Jul 7-Sep 27-Oct 16-DecDay

Tota

l Ele

ctri

c D

eman

d (k

W)

Page 56: SOLAR REACTIVATED DESICCANT DEHUMIDIFICATION & H … · house. I used the same radiant floor installation technique on my redesign for this 40+ million dollar museum as I learned

Page 56

- DUSTIN M. EPLEE -

The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Original Design Energy Consumed

0

500,000

1,000,000

1,500,000

2,000,000

2,500,000

1-Jan 20-Feb 10-Apr 30-May 19-Jul 7-Sep 27-Oct 16-DecDay

Tota

l Ene

rgy

Dem

and

(BTU

/hr)

McDuster Energy Consumed

0

500,000

1,000,000

1,500,000

2,000,000

2,500,000

1-Jan 20-Feb 10-Apr 30-May 19-Jul 7-Sep 27-Oct 16-Dec

Day

Tota

l Ene

rgy

Dem

and

(BTU

/hr)

Page 57: SOLAR REACTIVATED DESICCANT DEHUMIDIFICATION & H … · house. I used the same radiant floor installation technique on my redesign for this 40+ million dollar museum as I learned

Page 57

- DUSTIN M. EPLEE -

The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Figure 20 – Manufacture’s Interface Desiccant Modeling Software (Not Excel Compatible)

McDuster Dehumidification Energy (Solar Source)

0

100,000

200,000

300,000

400,000

500,000

600,000

1-Jan 20-Feb 10-Apr 30-May 19-Jul 7-Sep 27-Oct 16-DecDay

Tota

l Ele

ctri

c De

man

d (B

TU/h

r)

LICL DESICCANT WHEEL SIMULATION PROGRAM

Page 58: SOLAR REACTIVATED DESICCANT DEHUMIDIFICATION & H … · house. I used the same radiant floor installation technique on my redesign for this 40+ million dollar museum as I learned

Page 58

- DUSTIN M. EPLEE -

The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Table 7 - McDuster Desiccant Humidification at Design Loads During 24 hour Period (January 15th through January 16th)

Time Outdoor Air Conditions Return Air Conditions Supply Air Return Air

01/15/05 - 01/16/05 Temp (F)

Humidity Ratio (gr/lb)

Temp (F)

Humidity Ratio (gr/lb)

Relative Humidity

Temp (F)

Humidity Ratio (gr/lb)

Temp (F)

Humidity Ratio (gr/lb)

7:00 PM 29.1 9.79 71.0 62.34 55.00% 137.0 51.83 40.5 20.308:00 PM 27.1 9.20 71.0 62.34 55.00% 138.0 51.76 38.9 19.849:00 PM 25.2 9.21 71.0 62.34 55.00% 138.0 51.68 37.9 19.83

10:00 PM 23.0 8.85 71.0 62.34 55.00% 137.0 51.69 35.6 19.5611:00 PM 21.0 8.46 71.0 62.30 54.97% 140.0 51.53 34.0 19.2312:00 AM 19.1 7.76 71.0 62.30 54.97% 147.0 51.39 32.5 18.67

1:00 AM 17.1 6.65 71.0 62.30 54.97% 158.0 51.17 30.9 17.782:00 AM 14.9 5.93 71.0 62.00 54.70% 158.0 50.79 29.1 17.143:00 AM 12.7 5.91 71.0 61.30 54.10% 158.0 50.22 27.4 16.994:00 AM 10.2 5.61 71.0 60.70 53.57% 158.0 49.68 25.4 16.635:00 AM 8.6 4.95 71.0 60.00 52.96% 158.0 48.99 24.1 15.966:00 AM 7.7 4.21 71.0 58.80 51.92% 158.0 47.88 23.4 15.137:00 AM 6.6 3.80 71.0 57.10 50.44% 158.0 46.44 22.5 14.468:00 AM 6.6 3.80 71.0 55.30 48.87% 158.0 45.00 23.4 14.109:00 AM 7.7 4.21 71.0 53.60 47.38% 158.0 43.72 23.4 14.09

10:00 AM 8.6 4.56 71.0 52.40 46.33% 158.0 42.83 24.1 14.1311:00 AM 9.7 4.61 71.0 51.60 45.64% 158.0 42.20 25.0 14.0012:00 PM 11.1 5.93 71.0 50.90 45.02% 158.0 41.91 26.1 14.92

1:00 PM 12.4 6.60 71.0 51.40 45.46% 158.0 42.44 27.1 15.562:00 PM 13.2 7.80 71.0 52.40 46.33% 158.0 43.48 27.8 16.723:00 PM 17.1 8.30 71.0 54.30 47.99% 158.0 45.10 30.9 17.504:00 PM 21.0 8.90 71.0 56.30 49.74% 158.0 46.82 34.0 18.385:00 PM 23.0 9.23 71.0 58.40 51.57% 158.0 48.57 35.6 19.066:00 PM 25.0 9.90 71.0 60.50 53.40% NA NA NA NA

Notes: 1) Outdoor Air Conditions Taken From Carrier's Hourly Analysis Program during the driest 24-hour period of the year (Boston, MA)

2) Enthalpy Wheel Effectiveness assumed to be .80

3) Conditioned space under positive pressure (10,500 CFM supply and 9,450 CFM return)

4) Assumed no occupancy in gallery space during 24 hour period

5) Infiltration ignored due to positive pressure, moisture release from building materials, and the presence of security personnel

6) Assumed 3F rise from fan and air stream exposed motor

7) Desiccant wheel performance modeled Klingenburg SECO Desiccant/Enthalpy Rotor software

8) Space must be maintained at 50% +/-5% Relative Humidity

9) LiCl SECO wheel size = 2,750 mm

HUMIDIFICATION WITH DESICCANT WHEEL SIMULATION PROGRAM

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- DUSTIN M. EPLEE -

The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

McDuster Desiccant Humidification at Design Loads During 24 Hour Period (January 15th through January 16th)

40.00%

45.00%

50.00%

55.00%

60.00%

Time of day (hours)

Rel

ativ

e H

umid

ity @

71F

(%)

McDuster Humidification Energy (Solar Source)

0

100,000

200,000

300,000

400,000

500,000

600,000

1-Jan 20-Feb 10-Apr 30-May 19-Jul 7-Sep 27-Oct 16-DecDay

Tota

l Ele

ctric

Dem

and

(BTU

/hr)

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- DUSTIN M. EPLEE -

The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

McDuster Energy Demand Using Instant Booster Heating

0

50

100

150

200

250

300

350

400

450

500

1-Jan 20-Feb 10-Apr 30-May 19-Jul 7-Sep 27-Oct 16-Dec

Day

Tota

l Ele

ctri

c De

man

d (k

W)

McDuster Energy Demand Using Steam Booster Heating

0

50

100

150

200

250

300

350

400

450

500

1-Jan 20-Feb 10-Apr 30-May 19-Jul 7-Sep 27-Oct 16-Dec

Day

Tota

l Ele

ctric

Dem

and

(kW

)

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

McDuster Energy Demand Using Off-Peak Booster Heating

0

50

100

150

200

250

300

350

400

450

500

1-Jan 20-Feb 10-Apr 30-May 19-Jul 7-Sep 27-Oct 16-Dec

Day

Tota

l Ele

ctri

c D

eman

d (k

W)

Daily Desiccant Humidification Energy

0

2,000,000

4,000,000

6,000,000

8,000,000

10,000,000

12,000,000

1-Ja

n

18-J

an

5-Fe

b

23-F

eb

12-M

ar

30-M

ar

17-A

pr

5-M

ay

23-M

ay

9-Ju

n

27-J

un

15-J

ul

2-A

ug

20-A

ug

7-S

ep

25-S

ep

13-O

ct

30-O

ct

17-N

ov

5-D

ec

23-D

ec

Day

Desi

ccan

t Hum

idifi

catio

n En

ergy

(BTU

)

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Desiccant Vs. Steam Humidification(Enthalpy Wheel Assumed in Both Cases)

0

200,000,000

400,000,000

600,000,000

800,000,000

1,000,000,000

1,200,000,000

Humidification withDesiccant

Humidification with SteamYea

rly

Hum

idifi

catio

n Lo

ad (B

TU)

Desiccant Vs. Steam Humidification (Enthalpy Wheel Assumed in Both Cases)

$0

$2,000

$4,000

$6,000

$8,000

$10,000

$12,000

Humidification with Desiccant Humidification with SteamYear

ly H

umid

ifica

tion

Load

(BTU

)

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

An extensive simulation of the flat panel solar collectors was undertaken using a combination of Microsoft Excel, Engineering Equation Solver, and Visual Basic Coding. For the simulation, 13,000 ft2 of panel area was assumed. Panel area covers the entire roof area due to the removal of the entire 5th floor mechanical mezzanine. The flat panel solar collectors have low iron white water glass to decrease the absorptance of the glass and increase its transmittance. The collectors face 20° west of south at an angle of 45° to the roof. Wile angles of 55° to 60° to the roof would optimize the system for winter months, it would decrease the total energy absorbed over the year and would cause the skylights to be at a sub optimal angle, affecting the natural daylight gallery below. Two different methods were used to find the solar radiation to the panels. These include the weighted Monthly Daily Average values and the Clear Sky Model as proposed by Hottel, Liu, and Jordan. In the weighted Monthly Daily Averaged method, the first step was to find the monthly daily averaged radiation values for Boston. Since these values are for the average day of the month, a weighted average value was found by calculating Hconst for each day (equation 1.10.3 in Solar Engineering of Thermal Processes-Duffie, Beckman) and using the following equations.

Hconst = 1 + 0.033 · cos 360 · n

365 · cos ( φ) · cos ( δ ) · sin ( ω s ) +

π · ω s

180 · sin ( φ) · sin ( δ )

Hadjusted = Hconst

Σ · Hconst · HMDA

While these equations did not yield perfect transitions, it weighted each day of the month, creating an adequate semblance of a curve. The Clear Sky Model (Section 2.8 Duffie, Beckman) arrives at significantly different results, yielding higher levels of solar radiation. This possibly comes from the definition of the model as clear sky. Duffie and Beckman note that the day’s radiation using this model is higher than the ASHRAE data and 10% higher than Hottel, Liu, and Jordan’s “standard” day method. Using the hourly radiation from the daily data method described by Duffie and Beckman, hourly radiation labels for each hour were obtained. With the hourly radiation levels know for both models, the simulation proceeds further by splitting the direct beam and diffuse components. For added solar performance, the roof has been redesigned to have a reflective coating. Next, hourly radiation levels to the panels were calculated based on their characteristics as defined in the appendices. Convection and radiation losses affect the utilizable energy of the solar collectors so Engineering Equation Solver was used to model these losses based on an average wind velocity, mean plate temperature, and the total absorbed solar radiation. The graphs obtained from the analysis shows how the collector angle affected the performance of the solar collectors and how much solar radiation levels vary over the year.

Table 8 – Flat Plate Collector Constants

β 45° Fc-s 0.854n 9.000 n 1.526 refractive index β 0.785398rad Fr-c 0.113p 3.000 θd,eff 56.485 effective incidence angleγ -20° Fc-r 0.038m 50.000 θ2,d,eff 33.118 γ -0.34907rad Fc-g 0.109ψ 135.000 θg/r,eff 69.407 effective incidence angleρr 0.8reflector reflectance Area 1200.000m2 θ2,g/r,eff 37.838 ρg 0.1ground reflectance Avail. Area 1200.000total m^2 αd/αn 0.951 αn 0.95plate absorptance Tank Init T 58.000C αg/r/αn 0.849 εp 0.05plate emittance Tank Size 100,000gal K 4 (m-1) - white glass F' 0.9collector efficiency ≈Tank Area 365.000m2 L 3.125 cover thickness (mm) Tank U Val 0.400W/(m2K) KL 0.0125 unitless Ta Tank 16.000C τd 0.9852 transmittance min Util T 30.000C τg/r 0.9843 transmittance max Tank T 99.000C (τ◦I)d 0.8989 (τ◦I)g/r 0.8018

FLAT PANEL SOLAR COLLECTOR SIMULATION PROGRAM

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Theoretical 'Clear Sky' Energy Collected By Solar PanelsDerived from Hottel and Liu Clear Sky Model

100,000

300,000

500,000

700,000

900,000

1,100,000

1,300,000

0-Jan 19-Feb 9-Apr 29-May 18-Jul 6-Sep 26-Oct 15-Dec

Day

Aver

age

Dai

ly E

nerg

y (B

tu/h

r)

On Horizontal PanelsOn Angled PanelsUtilized by Panels

Actual Energy Collected By Solar PanelsDerived from Monthly Averaged Daily Values

100,000

300,000

500,000

700,000

900,000

1,100,000

1,300,000

0-Jan 19-Feb 9-Apr 29-May 18-Jul 6-Sep 26-Oct 15-Dec

Day

Ave

rage

Dai

ly E

nerg

y (B

tu/h

r)

Poly. (On Angled Panels)Poly. (Utilized by Panels)Poly. (On Horizontal Panels)

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Table 9 - Solar Meteorological Data

H KT T DD Ave Day n δ ωs N Hd/H Hb/H Days nth dayApr 15050000 0.44 9 279 15 105 9.415 98.709 13.161 0.490 0.510 30 90Aug 16880000 0.47 22 24 16 228 13.455 102.619 13.683 0.459 0.541 31 212Dec 4580000 0.37 1 549 10 344 -23.050 67.137 8.952 0.539 0.461 31 334Feb 8050000 0.42 -1 538 16 47 -12.955 77.875 10.383 0.476 0.524 28 31Jan 5400000 0.39 -2 618 17 17 -20.917 69.574 9.277 0.513 0.487 31 0Jul 19850000 0.49 23 17 17 198 21.184 110.725 14.763 0.439 0.561 31 181Jun 20630000 0.49 20 40 11 162 23.086 112.906 15.054 0.439 0.561 30 151Mar 11540000 0.44 3 464 16 75 -2.418 87.790 11.705 0.490 0.510 31 59May 18400000 0.47 15 139 15 135 18.792 108.102 14.414 0.459 0.541 31 120Nov 5710000 0.38 7 335 14 318 -18.912 71.769 9.569 0.526 0.474 30 304Oct 10100000 0.48 13 184 15 288 -9.599 81.116 10.815 0.411 0.589 31 273Sep 14300000 0.49 18 67 15 258 2.217 92.026 12.270 0.439 0.561 30 243

Meteorological Data for Boston, MA from p.865 in Solar

Engineering of Thermal Processes

Table 1.6.1

H The monthly average daily radiation on a horizontal surface (J/m2) KT The monthly average clearness index T The 24-hour monthly average ambient temperature © DD The average number of degree days in the month to the base temperature 18.3 C Ave Day Date n Day of the year δ Declination, the angular position of the sun at solar noon with respect to the plane of the equator ωs Hour angle, the angular displacement of the sun east or west of the local meridian N The number of daylight hours Hd/H The ratio of daily diffuse radiation (Hd) to monthly averaged daily total horizontal solar radiation (H) Hb/H The monthly averaged daily beam component ratio Tot Days Total number of days of the month nth day Representative solar day number

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Ocean Cooling, Solar Heating, Desiccant Conditioning

Table 10 – Solar Variable Definitions

Symbol Definition TDB Outside Drybulb Temperature TWB Outside Wetbulb Temperature B Adjustment for solar day of year E Equation of time (minutes)

Sol Time Time based on the apparent angular motion of the sun across the sky ω (MidP) Hour angle, the angular displacement of the sun east or west of the local meridian ω (rad) Hour angle converted to radians

δ Declination found from the equation of Cooper (1969) δ (rad) Declination converted to radians ωs Sunset Hour angle θz Zenith angle, the angle between the vertical and the line to the sun θ Angle of incidence, the angle between the beam radiation on a surface and the normal

Hconst Constant radiation Hfrac Monthly average ratio

a constant developed from relationship between hourly and daily total radiation on horizontal surface b constant developed from relationship between hourly and daily total radiation on horizontal surface rt ratio of hourly total to daily total radiation

Hadjusted Adjustment for radiation fraction I Hourly radiation incident on the collector rd ratio of hourly diffuse to daily diffuse radiation Hd Daily diffuse radiation Id Hourly diffuse radiation Ib Hourly radiation minus Hourly Diffuse radiation Rb geometric factor, the ratio of beam radiation on the tilted surface to that on a horizontal It total incident radiation on the tilted surface of the collector θ2,b Angle of collector adjusted τb Transmittance

(τ◦I)b Transmittance S Difference between incident solar radiation and the optical losses Ul Product of heat transfer coefficient Qu Total energy being absorbed and transmitted to the water Q'u Total energy with the flat plate collector efficiency

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

There is a large difference between the amounts of energy absorbed during the summer compared to those amounts during the winter. In addition, the majority of the stored energy is needed during the night and over the winter for heating and humidification. This results in the need to choose a large storage tank: 100,000 gallons. This tank stores energy from the summer and releases it over the winter or when the available energy to the panels is too low to utilize. Microsoft excel was used to model the performance of the tank over a duration of a year. This model was linked directly to the solar panel simulation, air-handling unit simulation, and desiccant model for the greatest accuracy. The tank receives the utilizable solar energy from each hour and gives up the required heating energy to meet the heating demands of the building as well as losses to the ambient space. Multiple assumptions were made in modeling this tank including a maximum storage temperature of 210F and assuming a well-mixed tank for simplicity of analysis. The 100,000 gallon tank provided excellent seasonal storage capabilities, with the lowest recorded temperature of 91F. With good insulation and its location indoors, the losses from the tank to the ambient surroundings were minimal compared to the heating losses and solar gains.

The following graphs show the change in tank temperature and available energies over time due to the solar gains, load demands, and ambient losses. It is only in late January through early February in which the tank capacity reached its limit. An even larger storage tank could accomplish more seasonal storage, but the cost would be inhibitive in our case due to the tanks location within the confines of an existing duct bank. The combination of 13,000ft2 and 100,000 gallons of storage capacity allows for large energy savings while still keeping the first cost of the entire system below the first cost of the original design.

Hot Water Storage Tank Temperature Yearly Profile

90

110

130

150

170

190

210

1-Ja

n

17-J

an

3-Fe

b

20-F

eb

7-M

ar

24-M

ar

10-A

pr

26-A

pr

13-M

ay

30-M

ay

16-J

un

2-Ju

l

19-J

ul

5-A

ug

21-A

ug

7-S

ep

24-S

ep

11-O

ct

27-O

ct

13-N

ov

30-N

ov

16-D

ec

Day

Avg

Wat

er S

tora

ge T

empe

ratu

re (F

)

HOT WATER STORAGE TANK SIMULATION PROGRAM

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Ocean Cooling, Solar Heating, Desiccant Conditioning

Daily Electric Resistance Heating Jan and Feb

0

500

1000

1500

2000

2500

3000

3500

4000

4500

1-Jan 8-Jan 15-Jan 22-Jan 29-Jan 5-Feb 12-Feb 19-Feb 26-Feb

Day

Elec

tric

Res

ista

nce

Hea

ting

(kW

)

Daily Electric Resistance Heating Utilized To Humidy

0

500

1000

1500

2000

2500

3000

3500

4000

4500

1-Jan 20-Feb 10-Apr 30-May 19-Jul 7-Sep 27-Oct 16-Dec

Day

Elec

tric

Res

ista

nce

Heat

ing

(kW

)

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Lost Heating Capacity- Energy Available to Purify Water

0

100

200

300

400

500

600

700

1-Jan 20-Feb 10-Apr 30-May 19-Jul 7-Sep 27-Oct 16-Dec

Day

Lost

Ene

rgy

Sto

rage

Cap

acity

(kW

)

Hot Water Storage Tank Available Energy

0

20,000,000

40,000,000

60,000,000

80,000,000

100,000,000

120,000,000

1-Ja

n

19-J

an

7-Fe

b

25-F

eb

15-M

ar

2-A

pr

21-A

pr

9-M

ay

28-M

ay

15-J

un

4-Ju

l

22-J

ul

10-A

ug

28-A

ug

16-S

ep

4-O

ct

23-O

ct

10-N

ov

29-N

ov

17-D

ec

Day

Sto

red

Ther

mal

Ene

rgy

(BTU

)

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Hot Water Storage Tank Energy Re-Charging

0

20,000,000

40,000,000

60,000,000

80,000,000

100,000,000

120,000,0001-

Jan

4-Ja

n

8-Ja

n

12-J

an

16-J

an

20-J

an

24-J

an

28-J

an

1-Fe

b

5-Fe

b

9-Fe

b

13-F

eb

17-F

eb

21-F

eb

25-F

eb

29-F

eb

4-M

ar

8-M

ar

12-M

ar

16-M

ar

Day

Stor

ed T

herm

al E

nerg

y (B

TU)

Hot Water Storage Tank Energy Decline

0

20,000,000

40,000,000

60,000,000

80,000,000

100,000,000

120,000,000

1-Ja

n

4-Ja

n

8-Ja

n

12-J

an

16-J

an

19-J

an

23-J

an

27-J

an

31-J

an

4-Fe

b

7-Fe

b

11-F

eb

15-F

eb

19-F

eb

23-F

eb

26-F

eb

1-M

ar

5-M

ar

9-M

ar

13-M

ar

Day

Stor

ed T

herm

al E

nerg

y (B

TU)

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Simulations for the existing building were done through Carrier’s HAP analysis program. Below is a comparison between these results and the original CHVAC program used by Arup. Generally, the HAP analysis produces cooling loads of 15% lower than CHVAC. Those rooms with significant differences (>20%) are explained due to changes in room sizing and function between analysis and final design.

Table 11 – Detailed Zone Comparison HAP Energy For Redesign CHVAC Comparison ARUP Comparative Percent Error Cooling Latent Heating Cooling Latent Heating Cooling Latent Heating

Zone Space name (BTU/hr) (BTU/hr) (BTU/hr) (BTU/hr) (BTU/hr) (BTU/hr) (BTU/hr) (BTU/hr) (BTU/hr)1 Lobby Full-Height 177,711 16,922 77,141 234,698 20,814 78,507 24% 19% 2%2 Lobby Central 64,264 19,545 17,407 78,461 24,794 17,748 18% 21% 2%3 Classroom (102) 33,521 9,255 8,014 41,966 10,256 8,169 20% 10% 2%4 Coat Room (103) 3,108 657 1,196 3,452 770 1,224 10% 15% 2%5 Bookstore (101) 32,309 6,796 12,883 36,165 8,379 13,167 11% 19% 2%6 CrawlSpace (101B) 4,909 198 1,718 4,257 256 1,745 15% 23% 2%7 Staff Room/Lockers 17,955 3,337 11,774 32,249 3,569 11,980 44% 7% 2%8 Dressing Rooms 7,644 6,124 1,635 9,960 6,289 1,618 23% 3% 1%9 Office (206A) 3,578 261 2,894 4,391 309 2,930 19% 16% 1%

10 Storage (209B) 2,744 306 1,887 2,913 343 1,890 6% 11% 0%11 Green Room (206) 14,905 8,740 6,338 19,148 9,046 6,368 22% 3% 0%12 Storage(209A) 6,263 859 3,247 6,640 971 3,215 6% 12% 1%13 Bridge (204) 12,608 317 12,317 15,816 754 13,169 20% 58% 6%14 Corridor (205) 2,248 496 1,833 2,474 548 1,815 9% 9% 1%15 Prep 1 (209) 43,570 2,686 12,980 53,898 3,275 13,081 19% 18% 1%16 Elevator Lobby (203) 1,977 436 1,613 2,176 482 1,597 9% 10% 1%17 Classroom (202) 27,662 3,276 7,809 34,294 3,800 7,883 19% 14% 1%18 Darkroom (202C) 1,364 442 664 1,539 499 667 11% 11% 0%19 Storage (202B) 411 58 221 435 66 219 6% 12% 1%20 Director (314) 11,603 782 6,485 14,454 879 6,552 20% 11% 1%21 Offices NE (315) 4,519 474 2,521 8,243 579 2,538 45% 18% 1%22 Offices NE (316-319) 14,439 1,865 8,341 26,540 2,136 8,074 46% 13% 3%23 Board Room (313) 14,757 5,053 7,794 16,432 5,228 5,810 10% 3% 34%24 Offices SE (320) 5,264 492 3,905 8,684 567 3,951 39% 13% 1%25 Offices SE (321-324) 8,466 1,160 4,864 11,106 1,402 4,899 24% 17% 1%26 Meeting Room (312) 7,631 1,869 3,975 9,623 2,289 3,998 21% 18% 1%27 Corridor (303) 2,903 290 3,221 2,886 325 3,239 1% 11% 1%28 Open Office (308) 27,106 5,646 6,712 30,007 6,772 6,532 10% 17% 3%29 Reception (307) 4,835 780 1,121 5,287 930 1,091 9% 16% 3%30 Copy/Mail (310) 2,459 444 459 2,695 535 446 9% 17% 3%31 Pantry (311) 1,283 139 527 1,357 155 513 5% 10% 3%32 Storage (309) 807 99 374 962 110 364 16% 10% 3%33 Elevator Lobby (302) 786 344 1,380 2,107 365 1,351 63% 6% 2%34 Theater Stage (300) 292,727 5,044 35,675 319,216 5,031 36,073 8% 0% 1%35 Theater (300) 238,107 57,333 31,288 255,594 70,063 22,914 7% 18% 37%36 Upper Theater (301) 8,295 679 7,439 8,405 609 7,494 1% 11% 1%37 Vestibule/Hall (301A-B) 1,446 344 952 1,588 280 926 9% 23% 3%38 East Gallery (402) 313,117 107,944 126,788 373,054 109,734 129,102 16% 2% 2%39 Long Gallery East (404) 94,036 10,321 126,305 115,196 9,064 128,346 18% 14% 2%40 Mediatheque (403) 37,780 5,747 22,972 43,177 7,605 23,397 12% 24% 2%41 West Gallery (401) 297,765 97,525 118,425 349,917 97,513 120,572 15% 0% 2%42 Long Gallery West (404) 86,336 7,621 124,158 108,816 7,163 126,159 21% 6% 2%43 Gallery Lobby (400) 2,124 464 2,114 2,320 422 2,167 8% 10% 2%44 Dining Room (108) 75,019 19,420 30,716 95,841 20,054 31,239 22% 3% 2%45 Storage (112) 3,174 376 1,420 3,375 439 1,454 6% 14% 2%46 Bookstore Storage (115) 1,213 143 542 1,290 167 555 6% 14% 2%47 Bookstore Office (114) 1,381 295 505 1,543 356 516 10% 17% 2%48 Corridor (119) 1,276 242 940 1,412 277 962 10% 13% 2%49 Food Prep (121) 5,749 1,050 1,533 6,321 1,274 1,568 9% 18% 2%50 Service Area 1,505 665 673 1,858 808 689 19% 18% 2%

EXISTING DESIGN HVAC ENERGY USAGE AND YEARLY COSTS

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Ocean Cooling, Solar Heating, Desiccant Conditioning

HVAC Fuel Energy Utilization Data

The Institute of Contemporary Art is comprised off the following equipment burning natural gas: (Energy HVAC usage predictions are based upon detailed HAP carrier simulation).

Two Gas Fired hot water boilers: Capacity input is 2,500,000 BTU/hour, capacity output is 2,000,000 BTU/hour for each of the boilers. The ICA is predicted to utilize 53,280 therms for space heating.

Two Gas Fired steam boilers: Capacity input is 175,000 BTU/hour for one boiler and 420,000 BTU/hour for the second boiler. The ICA is predicted to utilize 11,088 therms for humidification of gallery spaces.

Two Gas Fired domestic water heaters: Capacity input is 160,000 BTU/hour for one water heater and 250,000 BTU/hour for the second water heater. The ICA is predicted to utilize 3,652 therms for the heating of hot water.

Table 10 shows that the ICA is predicted to use 68,020 therms (6,802,000 kBTU) per year. Actual building usage data could not be obtained for this building because it is not schedule for completion until 2006. KeySpan, the largest distributor of natural gas in the Northeast, will deliver service to the new Institute of Contemporary Art upon completion in 2006. KeySpan Energy Delivery is a group of regulated natural gas and electric utilities. KeySpan delivers natural gas at a per energy rate that varies slightly from month to month. There is also an additional fixed monthly customer charge. Appendix C shows documentation showing the detailed rate structure for billing. These rates are summarized in table 12 below. Table 13 outlines an annual predicted cost of $78,388 for annual natural gas consumption.

Table 12- KeySpan Natural Gas Pricing Structure

Customer Charge Per month $127.07 - $131.31

Distribution Charge Per therm $0.1657

KeySpan Natural

Gas Cost of Gas Adjustment Per therm $0.8629 - $0.9636

Table 13 - Original Design Energy Breakdown

AHU-1 East Gallery

AHU-2 West Gallery

AHU-3 Theater

AHU-4 Lobby, Admin

AHU-5 Mediateque Totals

Electrical Usage (kW) (kW) (kW) (kW) (kW) (kW) Cooling Coil Load (COP=2.5) 198,254 181,312 178,349 133,677 9,438 701,030Cooling Equip Load 1,344 1,330 1,301 1,343 1,344 6,662Central Clg Input 3,013 3,013 3,013 3,013 3,013 15,065Supply Fan 71,727 67,602 93,469 44,499 7,811 285,108Return Fan 47,818 45,068 62,313 29,666 5,207 190,072 Totals 1,196,640

Natural Gas Usage (kBTU) (kBTU) (kBTU) (kBTU) (kBTU) (kBTU) Preheat Coil 15,021 6,733 0 246,167 0 267,921Central Heating Coil 212,435 192,195 0 0 37,744 442,374Terminal Heating Coil 1,490,041 1,423,338 1,227,117 55,801 0 4,196,297Humidifier Input 964,211 913,969 0 0 0 1,878,180 Total in kBTU 6,784,772 Total in therms 68,020

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Ocean Cooling, Solar Heating, Desiccant Conditioning

Electricity Energy Utilization Data

Using Carrier’s Hourly Analysis Program v.4.2, it is estimated that the Institute of Contemporary Art will use 1,196,640 kW annually in addition to natural gas consumption. This high-energy value can easily be accounted for by looking at several factors. The Institute of Contemporary Art is a heavy user of lighting energy with an average lighting density of 6.13 W/ft2, which correlates directly to increase cooling load. In addition, the ICA is composed mostly of exterior glass and as a result has a high radiation, thermal, and moisture transmission load.

NSTAR will be the electricity provider for the Institute of Contemporary Art. This company transmits and delivers enough electricity and natural gas to serve nearly 1.4 million residential and business customers located in Eastern Massachusetts. For businesses located in Boston, NStar offers either a general or time-of-use rate structure. Time-of-use rate structures differentiate between peak and off-peak rates, whereas general rate structures do not. For the ICA building, a time-of-use rate structure applies. This rate is for large commercial and industrial customers with a service voltage of less than 10,000 volts and a monthly demand of 10 kW or more. This rate has peak and off-peak periods. The rates are shown in Table 14 below.

Based on the energy data taken from the HAP hourly model and a calculated annual consumption of 1,196,640 kW, the annual electricity consumption cost is calculated, shown in the table below. Based on this calculation, the total annual HVAC electricity consumption cost is estimated to be $185,153.

Table 14 – HVAC Annual Electricity Cost

CHARGE UNIT COST/UNIT COST/YEAR

Customer Charge [1] Per month $166.67 $2000.04

Distribution (Demand) Per kW (Oct-May / June-Sept) $8.18 [2] $17.51 [3] $63,789

Transition (Demand) Per kW (Oct-May / June-Sept) $0.92 [2] $4.77 [3] $13,189

Transition (Energy) Peak [4] Per kWh (Oct-May / June-Sept) $0.01825 $0.03051 $15,547

Transition (Energy) Off-Peak [5] Per kWh (Oct-May / June-Sept) $0.00502 $0.00844 $5,182

Transmission (Demand) Per kW (Oct-May / June-Sept) $2.44 [2] $2.44 [3] $13,049

Default Fixed Charge Per kWh $0.0605 $72,397

TOTAL $ $185,153

NOTES: 1. Customer Charge based on maximum monthly billing demand, calculated to be 537 kW. 2. A 400 kW demand per month was calculated between Oct and May. 3. A 537 kW demand per month was calculated between June and Sept. 4. Peak hours are from 9 a.m. to 6 p.m. weekdays from June through September; and 8 a.m. to 9 p.m. weekdays

October through May. 5. Off-peak hours are all other hours including weekends and the 12 Massachusetts holidays.

The total estimated cost for both natural gas and electricity to power the HVAC equipment is $263,540.

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Based on extensive hourly modeling and a calculated annual consumption of 398,988 kW, the annual electricity consumption cost is calculated, shown in the table below. Based on this calculation, the total annual HVAC electricity consumption cost is estimated to be $48,760.

Table 15 – McDuster HVAC Annual Electricity Cost CHARGE UNIT COST/UNIT COST/YEAR

Customer Charge [1] Per month $166.67 $2000.04

Distribution (Demand) Per kW (Oct-May / June-Sept) $8.18 [2] $17.51 [3] $12,058

Transition (Demand) Per kW (Oct-May / June-Sept) $0.92 [2] $4.77 [3] $2,196

Transition (Energy) Peak [4] Per kWh (Oct-May / June-Sept) $0.01825 $0.03051 $4,203

Transition (Energy) Off-Peak [5] Per kWh (Oct-May / June-Sept) $0.00502 $0.00844 $1,401

Transmission (Demand) Per kW (Oct-May / June-Sept) $2.44 [2] $2.44 [3] $2,762

Default Fixed Charge Per kWh $0.0605 $24,139

TOTAL $ $48,760

NOTES: 6. Customer Charge based on maximum monthly billing demand, calculated to be 537 kW. 7. A 104 kW demand per month was calculated between Oct and May. 8. A 75 kW demand per month was calculated between June and Sept. 9. Peak hours are from 9 a.m. to 6 p.m. weekdays from June through September; and 8 a.m. to 9 p.m. weekdays

October through May. 10. Off-peak hours are all other hours including weekends and the 12 Massachusetts holidays.

There is no natural gas consumption for the McDuster System. The total annual energy amount is $48,760.

Table 16 - McDuster Pumping and Fan Energy Description (# of devices) (Total kW/year) HP (each unit) Max Pressure Drop (ft) Ocean Pump (3) 7,873 15 41.5 Heating Coil Pump (2) 2,810 3 14 Cooling Coil Pump (2) 2,364 4 15 Radiant Coil Pump (2) 1,615 6 33 Radiant Heating Pump (2) 0 3 33 Solar Heating Pump (2) 1.615 Supply Fan (3) 182,272 10 4.5 in wg Return Fan (3) 164,045 9 4.5 in wg Electric Booster Heat (1) 37,585 - -

MCDUSTER DESIGN HVAC ENERGY USAGE AND YEARLY COSTS

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Annual HVAC Energy Comparison

1,362,146

14,473,840

0

2,000,000

4,000,000

6,000,000

8,000,000

10,000,000

12,000,000

14,000,000

16,000,000

McDuster Energy Use Original Energy Use

Ener

gy (k

BTU

)

Annual HVAC Utility Cost Comparison

$48,760

$263,540

$0

$50,000

$100,000

$150,000

$200,000

$250,000

$300,000

McDuster Energy Cost Original Energy Cost

Annu

al H

VAC

Util

ity B

ill ($

)

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

The redesign for the Institute of Contemporary Art reduces total building emissions by 67%. Annual building emissions from both the onsite burning of natural gas as well as electricity usage are calculated for the Institute of Contemporary Art. Table 17 comes from “Electric Power Annual 1999” and gives an average Pollutant value for electricity generated in the United States. Manufacture’s data for boilers to be installed in the Institute of Contemporary Art were utilized to give an estimation of pollutants generated from onsite natural gas consumption. Tables 18 through 20 give details of the pollutant breakdown. Table 17 - Estimating Emissions Associated with On-Site Electricity Use U.S. Power Generation Mix Short Tons lbm Pollutant /kWh US

Fuel kWh(1999) % Total SO2 NOx CO2 Particulat

es SO2/kWh NOx/kWh CO2/kWh Coal 1.77E+12 55.7 1.13E+07 6.55E+06 1.90E+09 1.10E-03 1.28E-02 7.41E-03 2.15E+00 Oil 8.69E+10 2.7 6.70E+05 1.23E+05 9.18E+07 1.10E-03 1.54E-02 2.83E-03 2.11E+00

Nat. Gas 2.96E+11 9.3 2.00E+03 3.76E+05 1.99E+08 0.00E+00 1.35E-05 2.54E-03 1.34E+00 Nuclear 7.25E+11 22.8 0.00E+00 0.00E+00 0.00E+00 0.00E+00 0.00E+00 0.00E+00 0.00E+00

Hydro/Wind 3.00E+11 9.4 0.00E+00 0.00E+00 0.00E+00 0.00E+00 0.00E+00 0.00E+00 0.00E+00 Totals 3.18E+12 100.0 1.20E+07 7.05E+06 2.19E+09 6.42E-04 7.54E-03 4.44E-03 1.38E+00

Table 18 - Existing ICA Design Emissions

Natural Gas Pollution Per Year

Natural Gas Usage per year (Therms) Particulates (lbm) S02 (lbm) Nox (lbm) Co2 (lbm)

68,017 Therms 51 5 669 562

Electricity Pollution Per Year

Electricity Usage Per Year (kW) Particulates (lbm) S02 (lbm) Nox (lbm) Co2 (lbm)

1,196,640 769 9,018 5,310 1,650,846

Institute of Contemporary Art Total Yearly Pollution

Electricity and Natural Gas Sources Particulates (lbm) S02 (lbm) Nox (lbm) Co2 (lbm)

Total Pollution 820 9,022 5,979 1,651,408

Table 19 - McDuster ICA Redesign Emissions

Natural Gas Pollution Per Year

Natural Gas Usage per year (Therms) Particulates (lbm) S02 (lbm) Nox (lbm) Co2 (lbm)

0 Therms 0 0 0 0

Electricity Pollution Per Year

Electricity Usage Per Year (kW) Particulates (lbm) S02 (lbm) Nox (lbm) Co2 (lbm)

398,988 256 3,007 1,770 550,431

Institute of Contemporary Art Total Yearly Pollution

Electricity and Natural Gas Sources Particulates (lbm) S02 (lbm) Nox (lbm) Co2 (lbm)

Total Pollution 256 3,007 1,770 550,431

Table 20 - ICA Redesign Emission Savings Electricity and Natural Gas Sources Particulates (lbm) S02 (lbm) Nox (lbm) Co2 (lbm)

Total Pollution 564 6,016 4,208 1,100,977

BUILDING EMISSIONS

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

The Leadership in Energy and Environmental Design (LEED) Green Building Rating System is employed as a national standard for the design and development of sustainable buildings. Sustainability is “Meeting the needs of the present without compromising the ability of future generations to meet their own needs.” A sustainable building incorporates building materials, systems, and processes that promote environmental quality, economic vitality, and social benefit through the design, construction and operation of the building environment. Most buildings falling under the classification of commercial, institutional, and residential can be certified with ratings of silver, gold, or platinum. The existing systems within the Institute of Contemporary Art (ICA) were evaluated in all categories of the LEED point system. The results of this analysis show that the existing design for the ICA earned only 18 out of a possible of 69 possible points, shown in Table 21. Therefore, the building fell short of the minimum eligibility requirements (26-32 credits) for the LEED certification. Points earned by category follow: Original Design: Sustainable Sites: 5 Water Efficiency: 2 Energy and Atmosphere: 1 (but failed in refrigerant category) Materials and Resources: 4 Indoor Environmental Quality: 6 Innovation and Design Process: 0 Total 18 Implementing the McDuster System into the Institute of Contemporary Art will result in LEEDS certification. Table 21 shows the detailed breakdown of the analysis used to determine its rating. Rows highlighted in red are areas that would be impacted if ocean cooling, desiccant conditioning, and solar heating were implemented. The analysis was done conservatively only to prove that certification is possible. Conservatively, the McDuster would add the additional 12 points needed to certify the building. The exact rating at which the building would achieve was not pursued. McDuster Design: Sustainable Sites: 6 Water Efficiency: 2 Energy and Atmosphere: 15 (no refrigerants used) Materials and Resources: 4 Indoor Environmental Quality: 6 Innovation and Design Process: 5

Total 38

LEED GREEN BUILDING CERTIFICATION

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Table 21- Leeds Accreditation Results

Credit Number Category

Possible Credits

Credits Received Comments

Sustainable Sites (14 Possible Points)

Prereq 1 Erosion & Sedimentation Control Required Passed Professional Geological survey done and Erosion Control Plan Enacted

Credit 1 Site Selection 1 0 Located within 100 feet of Boston Harbor

Credit 2 Urban Redevelopment 1 1 Located in an area with high density and exceeds 60,000 ft2 per acre

Credit 3 Brownfield Redevelopment 1 1 Site located on reclaimed fill land Credit 4 Alternative Transportation, (Public Transportation) 1 1 Located within 1/2 mile of train, 1/4 mile of bus, and water taxi Credit 5 Alternative Transportation, (Bicycle Storage) 1 1 Bicycle racks, changing rooms, and showers provided

Credit 6 Alternative Transportation, (Alternative Fuel Vehicles) 1 0 No alternative fueling in design

Credit 7 Alternative Transportation, (Parking Capacity) 1 0 Parking shows no preference for carpooling vehicles Credit 8 Reduced Site Disturbance, (Protect or Restore) 1 0 Credit 9 Reduced Site Disturbance, (Development Footprint) 1 0 Credit 10 Storm water Management, (Rate and Quantity) 1 0

Credit 11 Storm water Management, (Treatment) 1 1 Storm water run-off catch basin located in bay to limit particle releases

Credit 12 Heat Island Effect, (Non-Roof) 1 0 Area surrounding the building is entirely paved surface Credit 13 Heat Island Effect, (Roof) 1 1 Substantial heat absorption through hot water solar collectorsCredit 14 Light Pollution Reduction 1 0 Extensive floodlights will be used to make this building 'glow'

Water Efficiency (5 Possible Points) Credit 1 Water Efficient Landscaping, (Reduce by 50%) 1 1 No irrigation used Credit 2 Water Efficient Landscaping, (No Potable Use)) 1 1 No irrigation used Credit 3 Innovative Wastewater Technologies 1 0 Credit 4 Water Use Reduction, 20% Reduction 1 0 Credit 5 Water Use Reduction, 30% Reduction 1 0

Energy & Atmosphere (17 Possible Points) Prereq 1 Fundamental Building Systems Commissioning Required Passed Commissioning Authority and commissioning plan establishedPrereq 2 Minimum Energy Performance Required Passed Meets ASHRAE Standard 90.1-1999 Prereq 3 CFC Reduction in HVAC&R Equipment Required Passed No refrigerants used at all (Water with antifreeze additive) Credit 1-10 Optimize Energy Performance 10 10 Energy use is just fans and pumps Credit 11 Renewable Energy, (5%) 1 1 Credit 12 Renewable Energy, (10%) 1 1 Credit 13 Renewable Energy, (20%) 1 1 Credit 14 Additional Commissioning 1 0 Credit 15 Ozone Depletion 1 1 Over 80% reduction in the HVAC emissions Credit 16 Measurement & Verification 1 1 Extensive building controls are included in design Credit 17 Green Power 1 0 No plan to buy energy from green sources

Materials & Resources (13 Possible Points) Prereq 1 Storage & Collection of Recyclables Required Passed Low to no cost implemenation Credit 1 Building Reuse, (Maintain 75% of Existing Shell) 1 0 Credit 2 Building Reuse, (Maintain 100% of Existing Shell) 1 0 Credit 3 Building Reuse, (Maintain 100% Shell & 50%) 1 0 Credit 4 Construction Waste Management, (Divert 50%) 1 1 50% of Construction/Demolition Waste Could be Recycled Credit 5 Construction Waste Management, (Divert 75%) 1 0 Credit 6 Resource Reuse, (Specify 5%) 1 0 Specified all new construction Credit 7 Resource Reuse, (Specify 10%) 1 0 Specified all new construction

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Credit 8 Recycled Content, (Specify 5%) 1 0 Specified all new construction Credit 9 Recycled Content, (Specify 10%) 1 0 Specified all new construction

Credit 10 Local/Regional Materials, (20% Manufactured Locally) 1 1 Steel to be bought from source within 500 miles

Credit 11 Local/Regional Materials, (20% in Mrc.5.1) 1 1 Steel to be bought from source within 500 miles Credit 12 Rapidly Renewable Materials 1 0 Credit 13 Certified Wood 1 1 Very little wood used: Wood complies with FSC

Indoor Environmental Quality (15 Possible Points)

Prereq 1 Minimum IAQ Performance Required Passed Meets ASHRAE Standard 62 Addendum N (Tech Assignment #1)

Prereq 2 Environmental Tobacco Smoke (ETS) Control Required Passed Non-Smoking Building Credit 1 Carbon Dioxide (CO2) Monitoring 1 0 Constant Volume air cannot be adjusted by CO2 sensors Credit 2 Ventilation Effectiveness 1 1 Dedicated outdoor air system Credit 3 Construction IAQ Management Plan, (During) 1 0 Credit 4 Construction IAQ Management Plan, (Before) 1 0 Credit 5 Low-Emitting Materials, (Adhesives & Sealants) 1 0 Credit 6 Low-Emitting Materials, (Paints) 1 0 Credit 7 Low-Emitting Materials, (Carpet) 1 0 Credit 8 Low-Emitting Materials, (Composite Wood) 1 0 Credit 9 Indoor Chemical & Pollutant Source Control 1 1 Very high standards are set with museum air quality standardsCredit 10 Controllability of Systems, (Perimeter) 1 0 No operable windows allowed for museums Credit 11 Controllability of Systems, (Non-Perimeter) 1 0 System pre-set for artwork preservation

Credit 12 Thermal Comfort, (Comply with ASHRAE 55-1992) 1 1 Meets ASHRAE Standard 55-1992 for Humidity and Temp Control

Credit 13 Thermal Comfort, (Permanent Monitoring System) 1 1 Temperature and Humidity Monitoring System Installed

Credit 14 Daylight & Views, (Daylight 75% of Spaces) 1 1 Entire 4th Floor Ceiling is diffuse light from North-Facing Skylights

Credit 15 Daylight & Views, (Views for 90% of Spaces) 1 1 Exterior façade is mostly glass, North-Facing Skylights in Roof

Innovation and Design Process (5 Possible Points) Credit 1 Innovation in Design 1 1 Ocean cooling Credit 2 Innovation in Design 1 1 Solar reactivated desiccant wheel Credit 3 Innovation in Design 1 1 Hot Water Storage Tank Credit 4 Innovation in Design 1 1 Desiccant Humidification Credit 5 LEED Accredited Professional 1 1 Engineers are accredited

Totals

Totals 69 30 (existing design was at 17)

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Existing Redundancy and Backup Overview This section of the report is an evaluation of the HVAC Equipment Redundancy for the ICA project. The HVAC design consists of two (2) air-cooled chillers, two (2) gas fired hot water boilers, two (2) gas fired steam humidifiers, associated chilled water / hot water pumps (primary and stand-by) and air handling units. No redundant mechanical systems or equipment is included in the design. The general strategy adopted is to provide multiple units of all the major equipment sized to have a combined capacity of 100%. In this way, failure of any one of these major components will not result in a complete system shutdown but only in a reduced level of service to the building. Design documents show an assumption that in the event of a power failure or other major building systems failure the building will be closed. The following is a brief description of the provisions made for component failure in each of the main mechanical systems.

1. Heating System: Two (2) boilers (sized for 70% load) and one (1) duplex set of pumps (primary and standby at 100% each) are included in the design. The system is capable of running and maintaining a reduced level of service (70% load) in the event of failure of a boiler.

2. Cooling System: Two chillers (each sized at 50% of the building load) and one (1) duplex set of pumps (one primary and one secondary at 100% each) are provided. The system is capable of running and maintaining a reduced level of service (50% load) in the event of one (1) chiller failure.

3. Humidification System: Two steam generators (each sized at 50% of the building load) are included in the design. The system is capable of running and maintaining a reduced level of service in the event of failure of a steam generator.

4. Air Handler: No specific air handling redundancy is provided for in the design. However, the level 4 gallery air-handling units are adjacent to each other and cross-connected such that if a failure of a gallery air-handling unit occurs then air can be supplied from the operable gallery unit to both gallery supply systems.

Due to the lack of mechanical redundancy in the HVAC design, it is likely the Institute of Contemporary Art will incur higher premium insurance costs over the long term for preserving / exposing artwork in its facility. In the case of mechanical reliability issues, the ICA could also lose the ability to display particularly environment sensitive or valuable artwork, creating an impact on the operation of the gallery space over the years. However, the design does allow for the possibility to upgrade to a level of redundancy to that of other institutions.

McDuster Improved Redundancy

5. Heating System: The 100,000 gallon storage tank provides a very large source for heating and it can be drawn at almost any rate. Storage tanks have proven themselves to be both reliable and predictable. An electric heating coil located at the top of the tank would provide for adequate backup in case the tank reached a sub optimal temperature level.

6. Cooling System: The cooling system features three pumps with one redundant. The titanium heat exchangers are also sized so that failure of one will not affect the performance of the system. Ocean water temperatures are stable, and if they did exceed design data criteria, it would be for only short durations.

7. Humidification System: Three Desiccant wheels are used to dehumidify the museum. Even at design conditions, two of the three would cover the needed dehumidification. The supply ducts are cross-linked for air handling unit redundancy.

REDUNDANCY AND BACKUP

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Existing Lighting Conditions

A section on lighting is included in this report due to its inherent effects for sizing the HVAC systems located within the Institute of Contemporary Art. The Institute of Contemporary Art anticipates developing and displaying a diverse permanent collection of art comprised of various media. Flexibility was of fundamental importance in the lighting design of the Institute of Contemporary Art. Lighting systems have been designed to effectively and economically accommodate changes in layouts and displays.

The lighting scheme addresses the following key program requirements: Flexibility is of fundamental importance Lighting systems must respond as layouts and displays change Flexible in achieving optimum lighting levels and light distribution Utilizes both daylight and electric light where appropriate Flexible in space planning Suitable for the conservation of all artworks Easy and inexpensive to operate and maintain Energy Efficient Keep the ceilings as uncluttered as possible

The lighting scheme is designed to avoid damage or fading by exposure to light based upon the following principles:

Sensitivity of the artwork to light Level of illumination Period of time over which artwork is exposed to illumination Spectral content of light including ultraviolet

A balance between increased illumination for easier viewing and conservation of artwork by limiting exposure to light was a primary focus for lighting of the 4th floor galleries. Fixtures were selected based on color temperature and color rendering properties of the light sources. For all display spaces, fixtures with a color-rendering index of 90 or greater are specified. All surfaces in the Gallery are finished with a neutral matte, white color. Lighting fixtures were also chosen with respect to their uniformity of illumination. Directional lights, via track lighting, are positioned to produce lighting angles of between 25-40 degrees from the art at eyelevel in order to reduce glare. A bus track is included with anticipation of supporting greater lighting loads, power taps, and small hanging loads. The Gallery floor is kept low to avoid bright reflections of the floor in some artworks. Diffusing layers on the inside of windows and illumination of building exteriors combine to minimize distracting reflections of the interior. Sub-division of the galleries through the use of walls and display cases has been accounted for in the lighting plan. All light sources in display spaces have a low direct heat radiation factor to avoid damage from excess heat. Linear fluorescent fixtures are fitted with Filter-Ray acrylic UV filters while track lighting is fitted with Optivex glass UV filters. Direct sunlight has been minimized through a diffusing ceiling material and north-facing skylights.

Daylight is used to provide ambient background light because of the following reasons: Good color rendering due to a more compete color spectrum Energy savings Contact with the external environment gives an awareness of the external environment and time

of day.

The daylight delivery system consists of a series of horizontal north-facing skylights. The system allows for changes in direct solar radiation on the roof to be dampened out. The skylights include a perforated reflector that improves ceiling luminance uniformity by reducing light towards the south and increasing light toward the north. The 4th floor galleries have translucent ceilings made up of specially formulated

LIGHTING BREADTH: EXISTING CONDITIONS

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fabric. This fabric is 100% Trivera CS and white in color producing a visible light transmission of at least 70%. Mechanical blackout shades, linked with the building control system, provide for the optimum amount of light passing through the skylight system.

Lighting in Non-Public Areas

Lighting in non-public areas is predominately high efficiency, fluorescent fixtures with occupancy sensors where additional energy savings can be realized. Lamps are rapid start T-8 fluorescent with electronic ballast and compact fluorescent with high power factor ballast. All lamps have a color temperature of 3500k. Pendant mounted Industrial type 4-foot fixtures are used for electrical, mechanical, communication and utility closets. Exit lights are used in office spaces and open areas respectively. Self-powered LED ‘Edge lit’ type exit lights are specified. The following table, taken from design documents, shows general ranges for lighting in non-public areas:

Area Lighting Design Level (Foot-candles)

Mechanical and Electrical Equipment rooms 20 Stairways, Corridors 20

Utility Rooms, Office Break rooms 30

Table 22 - INSTITUTE OF CONTEMPORARY ART LIGHTING COMPLICANCE WITH ASHRAE STANDARD 92 Area Lighting Watts Lighting/Area Standard 90 Compliance

Zone Space name Building Type: Museum ft2 Watts Watts/ft2 Watts/ft3 Pass / Fail 1 Lobby Full-Height Lobby 1,640 6,092 3.71 1.8 Fail 2 Lobby Central Lobby 2,335 6,538 2.80 1.8 Fail 3 Classroom (102) Classroom 885 1,416 1.60 1.6 Pass 4 Coat Room (103) Active Storage 320 448 1.40 1.4 Pass 5 Bookstore (101) Lobby 985 3,645 3.70 1.8 Fail 6 CrawlSpace (101B) Inactive Storage 410 533 1.30 1.4 Pass 7 Staff Room/Lockers Restrooms 595 476 0.80 1.0 Pass 8 Dressing Rooms Restrooms 370 296 0.80 1.0 Pass 9 Office (206A) Office-Enclosed 80 120 1.50 1.5 Pass

10 Storage (209B) Inactive Storage 260 338 1.30 1.4 Pass 11 Green Room (206) Office-Open Plan 620 496 0.80 1.3 Pass 12 Storage(209A) Inactive Storage 735 956 1.30 1.4 Pass 13 Bridge (204) Atrium-First three floors 280 392 1.40 1.3 Fail 14 Corridor (205) Corridor/Transition 415 581 1.40 0.7 Fail 15 Prep 1 (209) Food Preparation 965 2,413 2.50 2.2 Fail 16 Elevator Lobby (203) Lobby 365 511 1.40 1.8 Pass 17 Classroom (202) Classroom 440 704 1.60 1.6 Pass 18 Darkroom (202C) Office-Enclosed 75 16 0.21 1.5 Pass 19 Storage (202B) Inactive Storage 50 60 1.20 1.4 Pass 20 Director (314) Office-Enclosed 250 375 1.50 1.5 Pass 21 Offices NE (315) Office-Enclosed 160 240 1.50 1.5 Pass 22 Offices NE (316-319) Office-Enclosed 480 720 1.50 1.5 Pass 23 Board Room (313) Conference Meeting 415 621 1.50 1.5 Pass 24 Offices SE (320) Office-Enclosed 155 232 1.50 1.5 Pass 25 Offices SE (321-324) Office-Enclosed 390 585 1.50 1.5 Pass 26 Meeting Room (312) Conference Meeting 280 420 1.50 1.5 Pass 27 Corridor (303) Corridor/Transition 315 441 1.40 0.7 Fail

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28 Open Office (308) Office-Open Plan 1,975 2,560 1.30 1.3 Pass 29 Reception (307) Lobby 330 583 1.77 1.8 Pass 30 Copy/Mail (310) Office-Enclosed 135 202 1.50 1.5 Pass 31 Pantry (311) Active Storage 155 201 1.30 1.4 Pass 32 Storage (309) Active Storage 110 143 1.30 1.4 Pass 33 Elevator Lobby (302) Lobby 365 511 1.40 1.8 Pass 34 Theater Stage (300) Audience/Seating 1,950 91,000 46.67 1.8 Fail 35 Theater (300) Audience/Seating 2,270 49,000 21.59 1.8 Fail 36 Upper Theater (301) Audience/Seating 590 1,652 2.80 1.8 Fail

37 Vestibule/Hall (301A-B) Lobby 280 392 1.40 1.8 Pass

38 East Gallery (402) Lobby 8,115 40,575 5.00 1.8 Fail

39 Long Gallery East (404) Lobby 755 3,775 5.00 1.8 Fail

40 Mediatheque (403) Classroom 1,010 1,818 1.80 1.6 Fail 41 West Gallery (401) Lobby 7,795 38,975 5.00 1.8 Fail

42 Long Gallery West (404) Lobby 600 3,000 5.00 1.8 Fail

43 Gallery Lobby (400) Lobby 365 511 1.40 1.8 Pass 44 Dining Room (108) Dining Area 1,280 1,904 1.49 1.4 Fail 45 Storage (112) Inactive Storage 380 494 1.30 1.4 Pass

46 Bookstore Storage (115) Inactive Storage 145 189 1.30 1.4 Pass

47 Bookstore Office (114) Office-Enclosed 135 201 1.49 1.5 Pass

48 Corridor (119) Corridor/Transition 240 336 1.40 1.4 Pass 49 Food Prep (121) Food Preparation 410 615 1.50 2.2 Pass 50 Service Area Food Preparation 180 270 1.50 2.2 Pass

Total 43,840 268,572 6.13 1.6 Fail

Excluding Theater and Gallery Spaces Total 43,840 42,247 0.96 1.6 Pass

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The above section illustrated the importance of the natural daylight gallery space located on the 4th floor of the Institute of Contemporary Art. A translucent fabric material transmits light through from north facing skylights. The original design was limited by four (4) factors:

1) The 5th floor Mechanical Mezzanine produced a significant shadowing effect upon parts of the gallery space during the day. Figure 21 shows the effects of this barrier upon interior lighting conditions.

2) The structural triangular space frame and related dry wall impeded the light transmittance through the skylights and into the gallery space. Figure 22 shows the uneven ‘line’ pattern upon the ceiling as a result of this constraint.

3) The mechanical ductwork was extensive and needed to travel through the ceiling. Due to its large diameter, running the ducts through the floor was not possible. This created additional light disturbances and shadowing upon the ceiling

4) The building height was constricted to 70 feet early in the design process as to avoid the code penalties for a ‘high’ rise building. Increasing ceiling cavity depth is therefore not an option

Figure 21 – Mezzanine Shadowing

Figure 22 – Shadow Lines

Figure 23 – Uniform Lighting Achieved

The main purpose of the lighting redesign is to improve the uniformity across the ceiling in the natural daylight art gallery. This is achieved, in part, due to the implementation of the McDuster dedicated outdoor air-handling units. The flow to the ducts running through the gallery ceiling was reduced by 75%, thus reducing the duct size substantially. The reduced duct size allowed for the placement of the ducts into the floor joist cavity, thus freeing up the roof cavity. The structural triangular space frame had originally been designed to provide support for the ducts as well as hide their appearance from the occupants. With the ducts displaced, the space frame can be redesigned as a standard open-web joist. The associated drywall and finishing materials were no longer necessary. Figure 6 shows the improved uniformity after these changes were implemented. The following diagrams depict the cross sectional views of the roof and their corresponding changes necessary to improve the uniformity of the ceiling.

LIGHTING BREADTH: SKYLIGHT REDESIGN

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Figure 24 – Existing Northlight Cross Section Showing Light Dispersion Blockage

Figure 25 – Structural Redesign Opening Up Ceiling for Light Diffusity

Figure 26 - Final North Light Redesign Cross-Section: Improved Light Diffusity

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Background

Three (3) major structural modifications were investigated as a result of the proposed mechanical redesign for the Institute of Contemporary Art. The first modification was discussed in the section marked ‘Lighting Breadth’ and consists of replacing the roof triangle planar truss with more conventional open-web trusses. The second modification results from the removal of the entire 5th floor, due to substantial reductions in needed mechanical floor space. The third modification is to accommodate a 100,000 gallon thermal hot water storage vessel located within the building. Overall, these structural modifications result in significant weight and cost reductions for the structural system.

Numerous architectural explorations for the Institute of Contemporary Art eventually led to a design surprisingly sensible and straightforward: a steel-frame box building with a column-free 4th level that radically cantilevers out over Boston’s harbor. The art museum has a striking fourth level cantilever that demands attention. The 48-foot cantilever achieved with the utilization of four mega-trusses (25ft depth) with a 96-foot back span. The trusses are each supported by two mega-columns, one in the middle and one on the backside. The gallery space load is distributed by eight mega-columns positioned at the south edge of each truss and 96 feet in along the back span. Below the gallery the interior program divides in two halves by a central core strip of elevators and stairways. The floor systems of the theater, 2nd, and 3rd floors are comprised of composite steel deck. A lightweight triangular truss roof allows for both the dispersion of daylight as well as the distribution system for the MEP services. North-facing skylights create a 6ft wide void in the roof system. The cantilevered design embraces a public harbor walk and produces ever-changing panoramic spectacles of the water’s edge. Collaboration between architect and engineer early in the design process resulted in a highly efficient structure in which structural elements have been fused to create architecture.

Figure 27 – Existing Structural Steel

STRUCTURAL BREADTH: REMOVAL OF 5TH FLOOR MEZ & STORAGE TANK

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All loads are resolved into deep driven piles at ground level. These piles are comprised up of 11,000 linear feet of 215-ton H-section bearing piles and rely mainly on soil friction to carry the building’s load with some end bearing capacity. Due to the corrosive properties found at the site, a corrosion epoxy is applied to the piles up to 60 feet deep. An impressed current cathodic protection system has also been implemented to prevent corrosion. Ground beams are supported at pile cap locations. Ground slabs are designed as suspended slabs spanning across ground beams allowing for settling of the soil beneath them over time.

Triangular truss roof redesign

Refer to ‘Lighting Breadth’ for the background on the replacement of the Institute of Contemporary Art’s triangular planar truss roof system. This redesign is discussed at the end of this section.

Removal of 5th floor Mezzanine Level

The mechanical redesign of the Institute of Contemporary Art eliminates the floor space needed for two (2) air handling units, six (6) boilers, two (compressors), 5 air-cooled chillers, and corresponding electrical rooms. Thus, the entire 5th floor mezzanine level can be effectively removed. Figure 27 shows the original structural configuration, with the 5th floor represented by the gray box on top. Table 32 shows the detailed breakdown of all the structural elements eliminated, resulting in a load reduction of 14.58 tons. The original structural loading design of the mezzanine level consisted of relatively heavy and arguably conservative assumed dead and live loads. Figure 28 shows the 5th floor level broken down into two slab colors, maroon representing the roof load and the orange representing the original mechanical room loading. The total floor area of the mezzanine level was 3,456 ft2. It is assumed the roof added back to the building will be typical of the rest of the building. Total Load reduction resulting from the removal of the 5th floor mezzanine level is 404.5 PSF or 1,397,952 lbs (1,400K). The following presents the load descriptions of the original 5th floor mezzanine level:

Roof Load Removed

Dead Load:

Composite Metal Deck 50PSF

Superimposed Dead Load

4” Machine Slab 38PSF

Services 5 PSF

Ceiling & Lighting 10PSF

Live Load:

Machine (lieu of snow) 150PSF

Total Load: 253PSF

Floor Load Removed

Dead Load:

Composite Metal Deck 50PSF

Superimposed Dead Load

4” Machine Slab 38PSF

Services 5 PSF

Ceiling & Lighting 10PSF

Live Load:

Machine (lieu of snow) 150PSF

Total Load: 253PSF

Roof Load Added

Dead Load:

Steel Deck 3 PSF

Superimposed Dead Load

Glazing 2 PSF

Secondary Steel 2 PSF

Diffuser 2 PSF

MEP, Lighting 10 PSF

Gypsum 13 PSF

Insulation 2 PSF

Waterproofing Cover 4 PSF

Snow Load:

Sawtooth roof 52.5PSF

Total Load: 110.5PSF

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Table 23 - Mechanical Mezzanine Structural Steel Quantity Take-Off

Shape-Size Lb./foot Length Quantity Total Lbs. Total Tonnage 1 W8 10 8.7 1 87 0.04 2 W8 10 2 2 40 0.02 3 W8 10 4 2 80 0.04 4 W8 15 3.3 1 49.5 0.02 5 W8 15 13.3 1 199.5 0.10 6 W8 15 7.5 1 112.5 0.06 7 W8 15 7.2 1 108 0.05 8 W8 15 9.2 1 138 0.07 9 W10 17 10.4 3 530.4 0.27

10 W10 17 15 2 510 0.26 11 W10 17 7.1 2 241.4 0.12 12 W10 17 12.75 2 433.5 0.22 13 W10 17 22.3 2 758.2 0.38 14 W10 17 18.8 2 639.2 0.32 15 W12 19 8.7 1 165.3 0.08 16 W12 19 11.6 2 440.8 0.22 17 W12 19 14.8 2 562.4 0.28 18 W12 19 8.7 2 330.6 0.17 19 W12 19 14.7 2 558.6 0.28 20 W12 19 6.3 2 239.4 0.12 21 W12 19 17.7 2 672.6 0.34 22 W12 19 2.75 1 52.25 0.03 23 W12 19 10.33 1 196.27 0.10 24 W12 19 12.3 1 233.7 0.12 25 W12 19 8.9 1 169.1 0.08 26 W12 19 11 2 418 0.21 27 W12 19 13 2 494 0.25 28 W12 19 11 2 418 0.21 29 W12 19 13 2 494 0.25 30 W12 19 5.6 2 212.8 0.11 31 W12 19 6.5 2 247 0.12 32 W12 19 18.5 1 351.5 0.18 33 W12 19 22.3 3 1271.1 0.64 34 W12 19 24 8 3648 1.82 35 W12 26 24 1 624 0.31 36 W12 30 24 3 2160 1.08 37 W12 35 24 2 1680 0.84 38 W12 45 24 1 1080 0.54 39 W12 50 24 1 1200 0.60 40 W12 53 24 1 1272 0.64 41 W12 65 24 1 1560 0.78 42 W21 44 24 1 1056 0.53 43 W12 19 9.8 3 558.6 0.28 44 W12 26 15 2 780 0.39

Total Pieces 72 Total Lbs. 26504.72 Total Tonnage 13.25 10% Waist and Connections 14.58 Tons

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Figure 28 - Floor Loading Description and Load Path

Figure 29 - Hot Water Tank and Mezzanine Removal

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100,000 Gallon Hot Water Storage Tank

A 100,000 gallon hot water storage tank is needed to support the mechanical system redesign. The tank is 15 feet in diameter and approximately 75 feet high running the full height of the building. Figure 54 depicts the tank (blue) and its location in the building. The tank is located in an existing mechanical duct shaft that ran the full height of the building. Due to the substantial reductions in supplied airflow rates, the duct diameters are substantially reduced and dispersed throughout the building via other means. An emergency stairwell will wrap around the tank providing additional floor area. The empty weight allotted for the tank is 64,000 lbs (64K). 100,000 gallons of water weighs approximately 836,000 lbs (836K) for a total effective tank weight of 900,000 lbs (900K). The load is transferred directly into four (4) existing pile caps. Additional reinforced concrete must be poured to transfer the load from the tank to the pile caps. The approximate dimensions are 24’ X 21.3’ X 3’, or 88 yards of reinforced concrete, with an estimated weight of 213,721 lbs (214K). Total load increase resulting from the installation of the water tank is 1,049,721 lbs (1,050 K).

Foundation & Bearing Pile Redesign

All loads are resolved into deep driven piles at ground level. These piles are comprised up of 11,000 linear feet of 215-ton H-section bearing piles and rely mainly on soil friction to carry the building’s load with some end bearing capacity. The Pile design capacities are based upon the geotechnical information prepared by Haley & Aldrich, INC. The following axial load capacities were used in the foundation design for the Institute of Contemporary Art: 430 K (Compression) and –100 K (Tension). Figure 30 shows the load path followed by the changes in the original design. Due to the megatruss design, all the load reductions from the elimination of the mezzanine level travel down through only 4 mega columns. The load from the water tank transfers through into 4 pile caps, resulting in a total of 6 affected pile caps. Table 24 shows the forces on the original pile caps. Effects of lateral forces were ignored as the result of conversation with the original designers of the structure.

Figure 30 – Load Resolved Into Pile Caps

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Table 24 - Existing Pile Cap Reactions Affected By Addition of the 100,000 Gallon Water Storage Tank and Mezzanine Level Removal

Number Grid Vertical Designation Location Dead Live Snow Wind Seismic

#15 F-2.8 329 171 0 ±24 ±68#21 H-2.8 162 99 0 0 0#16 F-1 391 +348/-112 +89/-44 ±193 ±442#22 H-1 391 +397/-100 +102/-41 ±205 ±480#12 F-9 1883 1267 294 ±360 ±963#18 H-9 1847 1312 283 ±360 ±963

Grid Lateral X Location Dead Live Snow Wind Seismic

#15 F-2.8 0 0 0 0 0#21 H-2.8 0 0 0 0 0#16 F-1 0 0 0 0 0#22 H-1 0 0 0 0 0#12 F-9 0 0 0 0 0#18 H-9 0 0 0 0 0

Grid Lateral Y Location Dead Live Snow Wind Seismic

#15 F-2.8 0 0 0 0 0#21 H-2.8 0 0 0 0 0#16 F-1 7 2 1 ±29 ±54#22 H-1 20 5 1 ±88 ±161#12 F-9 25 13 0 ±166 ±434#18 H-9 0 0 0 0 0

Table 25shows a summary of the calculations performed to obtain the final results concerning the number of piles to be added or removed. Mega columns F-9 and H-9 are located mid span along the mega trusses and thus had the greatest load reduction. One (1) pile was removed from location F-9 and one (1) pile was removed from location H-9. Mega columns F-1 and H-1 were actually sized upon soil tension properties due to the large cantilever on the fourth floor. Recalculating this cantilever effect was not justified because load was evenly taken off of the 4th floor by way of the complete removal of the mezzanine level. Effectively, by placing the large water storage tank at the south side of the building and overtop of Columns F-1 and H-1, it acts as a counterweight to the cantilevering effect. No change was warranted for piles located on grid line F-1 and H-1 with an even trade between the weight reduction of the mezzanine level and the additional load of the tank. However, if the storage tank is emptied than the potential uplift forces may exceed that of the pile tension capability. It is such an unlikely event that Seismic, Wind, and Snow would occur at the same time the tank is empty that additional piles are not justified. Columns F-2.8 and H-2.8 are not affected by the reductions in the mezzanine levels since they only carry loading up to the third level. Pile location F-2.8 was over designed originally and thus is capable of supporting ¼ of the water storage tank without any changes. However, Pile location H-2.8 requires the addition of one (1) pile for the increased loading. Overall, two (2) piles were removed and one (1) pile was added for a net decrease of one (1) pile.

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Table 25 - Institute of Contemporary Art Redesign Pile Calculations Description Effected Pile Grid Locations

F - 2.8 H - 2.8 F - 1 H - 1 F - 9 H - 9 Current Design Maximum Compression Reaction (K) 592 261 1463 1575 4767 4765

Current Design Maximum Tension Reaction (K) NA NA -400 -435 NA NA

Current Design Pile Cap Type P2 P1 P4A P5A P11A P11

Current Number of Piles 2 1 4 5 11 11

Compression Pile Axial Load Capacities (430 K per pile) 860 430 1720 2150 4730 4730

Tension Pile Axial Load Capacities 200 100 400 500 1100 1100

Mezzanine Load Reduction (Design Loading) 0 0 234 234 467 467

Mezzanine Load Reduction (Steel Tonnage) 0 0 4.86 4.86 9.72 9.72

100,000 Gallon Water Storage Tank (Empty Weight- K) 16 16 16 16 0 0

100,000 Gallon Water Storage Tank (Water Weight-K) 209 209 209 209 0 0

Weight of new Pile Cap (K) (Approx: 24' X 3' X 21.3') 53 53 53 53 0 0

New Maximum Compression Reaction (K) 870 539 1503 1615 4291 4288

New Maximum Tension Reaction (K) NA NA -361 / -570 -396 / -605 NA NA

Which dictates sizing (Compression or Tension) Compression Compression Tension Tension Compression Compression

New Number of Piles 2 2 4 5 10 10

Changes warranted by re-design No Change Add 1 Pile Potential Problem Potential Problem Remove 1 Pile Remove 1 Pile

Figure 31 - Original Mechanical Room Configuration

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Figure 32 - Redesign Mechanical Configuration

Figures 31 and 32 show the MEP equipment locations before and after the structural changes. Additional mechanical room is needed for locating two (2) titanium heat exchangers, three (3) pumps, represented in Figure 7 as the green-blue box on the 1st floor. This space is currently used as storage and is located under the grand stairway leading up to the theater. Additional major structural changes are not required. Pile caps and piles are able to hold the extra 13PSF anticipated in the conversion to a mechanical room. The loading pattern is presented as follows:

Existing Storage Load Description

Dead Load:

8” Slab 100PSF

Superimposed Dead Load

2” Floor Finish 25PSF

Live Load: 100PSF

Total Load: 225PSF

Redesign Storage Load Description

Dead Load:

Composite Metal Deck 50PSF

Superimposed Dead Load

4” Machine Slab 38PSF

Live Load:

Machine 150PSF

Total Load: 238PSF

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Triangular truss roof redesign

Refer to ‘Lighting Breadth’ for the background on the replacement of the Institute of Contemporary Art’s triangular planar truss roof system. The system was replaced with 4-foot deep traditional “I” type open web trusses.

Table 26 - Triangular Truss Roof Structural Steel Quantity Take-Off Shape-Size Lb./foot Length Quantity Total Lbs. Total Tonnage A.3 - F P3.5 9.11 56.5 2 1029.43 0.51 Primary Top Cord A.3 - F P4 10.79 50.5 1 544.895 0.27 Primary Bottom Cord A.3 - F P2.5 5.79 6 10 347.4 0.17 Primary Right Edge Diagonal A.3 - F P2.5 5.79 6 10 347.4 0.17 Primary Left Edge Diagonal A.3 - F P2 3.65 6 16 350.4 0.18 Primary Center Diagonal A.3 - F P3.5 9.11 8 8 583.04 0.29 Primary Top Diagonal A.3 - F P3.5 9.11 11 1 100.21 0.05 Primary Top Diagonal A.3 - F P3.5 9.11 6 8 437.28 0.22 Primary Top Horizontal 56 3740.055 1.8700275 H - M P3.5 9.11 52 2 947.44 0.47 Primary Top Cord H - M P4 10.79 46 1 496.34 0.25 Primary Bottom Cord H - M P2.5 5.79 5 10 289.5 0.14 Primary Edge Diagonal H - M P2.5 5.79 6 10 347.4 0.17 Primary Edge Diagonal H - M P2 3.65 5 12 219 0.11 Primary Center Diagonal H - M P3.5 9.11 8 7 510.16 0.26 Primary Top Diagonal H - M P3.5 9.11 11 1 100.21 0.05 Primary Top Diagonal H - M P3.5 9.11 6 7 382.62 0.19 Primary Top Horizontal 50 3292.67 1.646335 A.3 - F 15 840 56100.825 28.05 H - M 15 750 49390.05 24.70 1590 105490.875 52.75 1 - 15 TS 3x3x0.1875 6.87 6 28 1154.16 0.58 Secondary Top Cord 1 - 15 TS 3x3x0.1875 6.87 166 1 1140.42 0.57 Secondary Bottom Cord 1 - 15 TS 4x4x0.25 12.21 6 28 2051.28 1.03 Secondary Diagonal 1 - 15 TS 3x3x0.1875 6.87 6 14 577.08 0.29 Secondary Top Diagonal 71 4922.94 2.46 1 - 15 4 ea 284 19691.76 9.85 Total Pieces 1874 Total Lbs. 125182.635 Total Tonnage 62.59

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Ocean Cooling, Solar Heating, Desiccant Conditioning

With significant reductions in the mechanical equipment needed to run the Institute of Contemporary Art, additional reductions in the electrical service can be achieved as well. This breadth was primarily focused on a rough estimation of the cost reduction associated with the electrical power for the building. It was not the intent to try and rearrange panel boards and provide accurate electrical wiring sizes for the new equipment installed. The only additional major load investigated is the electric resistance heating elements used to ‘boost’ water temperatures up during the wintertime.

Existing Electrical Service Overview

Theater Loads:

The electrical loads for the theatre area, according to the theatre consultant, are 288 Kw.

Utility Service:

Electrical power for the Institute of Contemporary Art is obtained via a single 480V, three phase, 4 wire service provided by the local Electrical Utility Company. The transformer, provided by the Utility Company, is pad mounted at grade. The service provided by the Utility is the “Standard Service” type. Electrical drawings call for 2500 amps @ 480V, 3 phase electric service.

Electrical Service:

The electrical service is routed from the utility transformer to the Buildings main 480V switchgear located at grade level. Power is further distributed at 480V via cable feeders in conduit to loads within the building. Vertical distribution is via electrical riser closets. Electrical closets are arranged to form a continuous vertical shaft where possible and contain cable feeders. Branch circuits for 277V/480V and 120V/208V distribute from panel boards contained in the electrical closets. Power is transformed locally to 120V/208V in the electrical closets. Emergency power is also distributed via panel boards contained within separate emergency power electrical closets. There is a minimum of one ‘normal’ and one ‘emergency’ electrical closet on each floor. UPS power is provided for the communication, security and BMS equipment. The UPS units are distributed and located locally at the equipment served. Raceways are provided for audio-visual, secretly voice and data systems. Disconnect switches for lighting and power are provided for the elevators. Cable feeds are provided to local motor controllers in mechanical equipment rooms throughout the building for mechanical equipment.

Lightning Protection:

A Master Label Lightning Protection System has been designed. The lightning protection system consists of air terminals on the roof of the building subject to a direct lightning strike. The air termination network is bonded to the structure for down conduction. A separate emergency power switchboard is provided to distribute emergency power to loads throughout the building.

Rough Cost Reductions of the Electrical systems

The following were eliminated from the original electrical systems cost estimate:

Two (2) Chillers Two (2) Air Handling Units Nine (9) fan coil units Eleven (11) Hot water unit heaters

ELECTRICAL BREADTH: HVAC DEMAND REDUCTION

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Ocean Cooling, Solar Heating, Desiccant Conditioning

The following were added to the original electrical systems cost estimate:

Three (3) Electric water booster heaters

Three (3) Ocean water pumps

Table 27 – Electrical First Cost Deductions

Description Quantity Unit Cost/Unit Cost Savings Chillers (2) Power/Panel board 400A NFSS NEMA-3R (Chillers) 2 no 1,970.00 3940 Connection 400A Connection 2 no 490.00 980 Distribution Feeder 400A feed - complete 400 lf 54.00 21600 Air Handling Units (2) 0 Power/Panel board 100A NFSS (CWP, AHUs, EF etc.) 2 no 480.00 960 Connection 100A Connection 2 no 196.00 392 Distribution Feeder 100A Feed 150 lf 11.15 1672.5 Fan Coil Units (9) 0Connection 20/30A Connection 9 no 82.00 738 Distribution 20/30A Feed 1350 lf 6.26 8451 Hot Water Unit Heaters (11) 0Connection 20/30A Connection 11 no 82.00 902 Distribution 20/30A Feed 1650 lf 6.26 10329 Total Savings: 49964.5

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

A detailed cost estimation was done to compare the first cost difference between the original system and the proposed McDuster system. A detailed cost breakdown of the original system was obtained and a condensed summary chart of deductions made follows. Pricing for the new proposed redesign of the Institute of Contemporary Art was obtained from the original pricing structure, actual bids, and RSmeans 2004 Mechanical Cost Data. Adjustments of 1.15 were made for the Boston, Massachusetts’s area. See Appendix G for detailed cost breakdown.

Total Deductions: $2,642,480

Total Additions: $2,498,604

First Cost Savings: $143,876

The McDuster Redesign has a first cost $143,876 less than the original design for the Institute of Contemporary Art!

Initial Start-up Costs

The initial start-up costs or capital costs for the Institute of Contemporary Art where compiled from Macomber Construction Estimates. A summary and detailed breakdown from this cost estimate is shown in Appendix G. The total initial start-up construction cost estimate for the ICA building is $33,667,308. Actual Bidding data from HVAC, Electrical, Plumbing, and Fire Protection is summarized in Table 28. The costs analyzed for the utility portion total $10,259,527 of the overall cost.

Table 28- Actual Low Bid Amounts HVAC Electrical Plumbing Fire Protection Low Bid $ 5,060,000 $ 4,312,000 $ 477,000 $ 261,000 Total MEP bid: 10,259,527

Base Date

The base date is the point in time to which all project-related costs are discounted in a Lifetime Cycle Cost Estimate. Start of construction for the Institute of Contemporary Art is July 2004.

Service Date

The ICA building has a projected service date, or occupancy, of September 2006.

First COST ECONOMIC ANALYSIS

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Ocean Cooling, Solar Heating, Desiccant Conditioning

Table 29 – First Cost Comparison Summary

Item Description McDuster Total Existing Total Cost Savings Original Building Costs 22,650,571 25,293,058 2,642,488

General Requirements 125,000 125,000 -

Site Construction 2,114,750 2,123,035 8,285

Concrete 1,088,250 1,105,530 17,280

Metals 3,838,049 3,920,027 81,978

Wood & Plastics 353,299 353,299 -

Thermal & Moisture Protection 2,035,356 2,111,399 76,043

Doors & Windows 3,332,266 3,333,566 1,300

Finishes 2,640,574 2,739,502 98,928

Specialties 125,092 171,392 46,300

Equipment 648,490 648,490 -

Furnishings 336,794 336,794 -

Special Construction 288,650 288,650 -

Conveying Systems 657,500 657,500 -

Plumbing 273,330 352,480 79,150

HVAC 1,286,695 3,469,953 2,183,259

Electrical 3,506,476 3,556,441 49,965

Redesign Building Costs 2,498,604 1,603,141 (895,463)

Radiant Floor 487,188 - (487,188)

Radiant Ceiling 472,314 - (472,314)

Radiant Wall 58,995 - (58,995)

Air Handling Units 494,090 - (494,090)

Solar Collectors 578,941 - (578,941)

Storage Tanks 133,135 - (133,135)

Concrete Foundations 26,400 - (26,400)

Ocean Cooling Piping System 247,541 - (247,541)

Site Work Costs 1,603,141 1,603,141 -

Site Preparation 51,000 51,000 -

Site Improvement 1,525,017 1,525,017 -

Site Mechanical Utilities 21,124 21,124 -

Site Electrical Utilities 6,000 6,000 -

Other Site Construction - - -

Indirect Costs 3,890,370 3,890,370 -

General Conditions 2,100,000 2,100,000 -

Permits 312,180 312,180 -

Insurance 361,966 361,966 -

Fee 1,116,224 1,116,224 -

Bond - - -

Contingencies 3,383,355 3,383,355 -

Design Program Contingency 1,650,417 1,650,417 -

Escalation - - -

Construction Contingency 1,732,938 1,732,938 -TOTAL 34,026,041 34,169,924 143,884

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Ocean Cooling, Solar Heating, Desiccant Conditioning

Maintenance Costs

Maintenance costs were obtained from design documents and represent the estimated mechanical, electrical, plumbing, fire protection, and elevator services in the building.

The main method for estimating the maintenance costs was based on the RS Means Facilities Maintenance and Repair Cost Data. This source gives the recurring annual and nonrecurring costs associated with the equipment in the building.

Estimates of the nonrecurring costs associated with these services along with detailed maintenance data are shown in Appendix I . Maintenance data was extracted from service contracts provided by local companies on their equipment with an estimated service value of $114,996 for the original design of the Institute of Contemporary Art.

Elimination of most of the mechanical equipment throughout the building brings significant reductions in estimated service value. The service value for the Institute of Contemporary Art with the McDuster modification is $80,533, with annual savings of $34,463.

Steel Tank Maintenance Cost Analysis:

Following are estimates for sandblasting, primer, and finish coat maintenance sessions for the hot water storage tank proposed for the redesign of the Institute of Contemporary Art. The total costs per size are based on four maintenance sessions for the life of the tank.

Tank coating square footage and sandblasting/coating cost estimates per session:

• 100,000 gallon tank: (75' high x 15' diameter is 1,650 sq. ft x 1 sides = 7,069 sq. ft. at $2.75/sq. ft.) $19,438 per session

The Institute of Contemporary Art is not equipped with a spare tank or another structure, which can be used for temporary storage, an alternate temporary solution will need to be provided to supply water. This is done with a temporary store and pump service. This factor was not accounted for in the maintenance cost analysis. Steel tanks normally need to be repainted on a nominal 12-year cycle. The average cost for sandblasting, removal of debris, electrical consumption for light (and heat) and re-coating a tank is approximately $2.75 per square foot for an epoxy coat (e.g. a DuPont or MAB primer plus epoxy finish). Typically, above ground tanks need to be coated on the inside and outside surfaces. However, the tank at the Institute of Contemporary art will be completely enclosed and only inside resurfacing is accounted for. Another item to consider is the down time during the maintenance stage. The nominal "down time" for a tank while undergoing service is 37 days. During this time an alternate water source or storage capacity will need to be made available. Again, given the infrequency at which this would occur, it was not considered.

Ocean Intake Filters

It was assumed that the ocean filters would need to be cleaned often by a scuba diver. $2,000 dollars per year was assumed to be enough to cover this annually reoccurring cost. Every five (5) years the filters would be replaced at an additional cost of $5,000.

Flat Plate Solar Collectors

Solar collectors are generally a low maintenance item. It was assumed that the only cost would be to clean the surfaces every two months. For this, $1,000 dollars was used.

LIFE-CYCLE MAINTENANCE ECONOMIC ANALYSIS

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9/2006 Years of Project Service: [1] 25 FEMP Fiscal Year: [3] 2006 DOE Region: [5] Northeast0 Years in Analysis Period: [2] 25 Disc. Rate: [4] 5.0% Analysis Sector: [6] Commercial

ELECTRIC COSTS NATURAL GAS COSTS ANNUAL TOTAL COSTS RECURRING COSTS

Annual Electric Discounted Annual Nat Gas Discounted Annual Discounted DiscountedRecurring Differential Electric Recurring Differential Nat Gas Recurring Recurring Total Electric Escalation w/Fuel Esc. Nat Gas Escalation w/Fuel Esc. (e.g., maintenance) Year Costs

Constant $ [9] % [10] PV $ Constant $ [11] % [12] PV $ Constant $ [13] PV $ Date PV $$263,540 $78,388 $0 $10,259,527$263,540 -6.45% $234,791 $78,388 -6.44% $69,850 $114,996 $109,520 2006 $414,161$263,540 -4.92% $212,618 $78,388 -3.69% $64,066 $114,996 $104,305 2007 $380,989$263,540 -3.90% $194,596 $78,388 -1.46% $60,128 $114,996 $99,338 2008 $354,061$263,540 -1.60% $182,356 $78,388 -0.13% $57,188 $127,637 $105,007 2009 $344,551$263,540 2.30% $177,670 $78,388 -1.48% $53,659 $116,550 $91,320 2010 $322,649$263,540 1.64% $171,986 $78,388 -1.23% $50,477 $114,996 $85,812 2011 $308,275$263,540 1.85% $166,818 $78,388 1.10% $48,604 $155,682 $110,640 2012 $326,063$263,540 3.49% $164,415 $78,388 2.05% $47,238 $134,238 $90,858 2013 $302,511$263,540 2.84% $161,040 $78,388 2.28% $46,013 $114,996 $74,127 2014 $281,180$263,540 2.04% $156,504 $78,388 1.83% $44,625 $585,506 $359,450 2015 $560,579$263,540 1.29% $150,979 $78,388 1.41% $43,101 $114,996 $67,236 2016 $261,315$263,540 1.19% $145,506 $78,388 0.25% $41,152 $130,259 $72,533 2017 $259,191$263,540 0.49% $139,253 $78,388 0.00% $39,193 $115,104 $61,042 2018 $239,488$263,540 0.00% $132,622 $78,388 -0.25% $37,232 $128,558 $64,931 2019 $234,785$263,540 -0.08% $126,205 $78,388 -0.51% $35,279 $249,590 $120,057 2020 $281,541$263,540 0.32% $120,585 $78,388 0.13% $33,642 $134,238 $61,496 2021 $215,723$263,540 0.81% $115,770 $78,388 1.40% $32,488 $115,148 $50,239 2022 $198,497$263,540 0.16% $110,434 $78,388 0.13% $30,980 $114,996 $47,783 2023 $189,197$263,540 -0.60% $104,544 $78,388 -0.13% $29,468 $212,667 $84,160 2024 $218,172$263,540 0.40% $99,967 $78,388 -0.25% $27,994 $721,102 $271,776 2025 $399,737$263,540 0.80% $95,969 $78,388 -0.25% $26,594 $128,557 $46,145 2026 $168,708$263,540 0.48% $91,836 $78,388 0.25% $25,392 $115,149 $39,364 2027 $156,591$263,540 0.36% $87,774 $78,388 0.38% $24,274 $114,996 $37,439 2028 $149,487$263,540 0.32% $83,858 $78,388 0.25% $23,176 $136,860 $42,436 2029 $149,470$263,540 0.35% $80,147 $78,388 0.37% $22,155 $360,447 $106,441 2030 $208,743

$6,588,500 $3,508,243 $1,959,700 $1,013,967 $4,587,260 $2,403,453 $17,185,190

9/2006 Years of Project Service: [1] 25 FEMP Fiscal Year: [3] 2006 DOE Region: [5] Northeast0 Years in Analysis Period: [2] 25 Disc. Rate: [4] 5.0% Analysis Sector: [6] Commercial

ELECTRIC COSTS NATURAL GAS COSTS ANNUAL TOTAL COSTS RECURRING COSTS

Annual Electric Discounted Annual Nat Gas Discounted Annual Discounted DiscountedRecurring Differential Electric Recurring Differential Nat Gas Recurring Recurring Total Electric Escalation w/Fuel Esc. Nat Gas Escalation w/Fuel Esc. (e.g., maintenance) Year Costs

Constant $ [9] % [10] PV $ Constant $ [11] % [12] PV $ Constant $ [13] PV $ Date PV $$48,760 $0 $0 $10,259,527$48,760 -6.45% $43,441 $0 -6.44% $0 $80,533 $76,698 2006 $120,139$48,760 -4.92% $39,338 $0 -3.69% $0 $80,533 $73,046 2007 $112,384$48,760 -3.90% $36,004 $0 -1.46% $0 $80,533 $69,568 2008 $105,572$48,760 -1.60% $33,739 $0 -0.13% $0 $93,174 $76,655 2009 $110,394$48,760 2.30% $32,872 $0 -1.48% $0 $162,259 $127,134 2010 $160,006$48,760 1.64% $31,821 $0 -1.23% $0 $80,533 $60,095 2011 $91,916$48,760 1.85% $30,865 $0 1.10% $0 $80,533 $57,233 2012 $88,098$48,760 3.49% $30,420 $0 2.05% $0 $99,775 $67,532 2013 $97,952$48,760 2.84% $29,796 $0 2.28% $0 $80,533 $51,912 2014 $81,708$48,760 2.04% $28,956 $0 1.83% $0 $339,264 $208,279 2015 $237,235$48,760 1.29% $27,934 $0 1.41% $0 $80,533 $47,086 2016 $75,020$48,760 1.19% $26,921 $0 0.25% $0 $95,796 $53,343 2017 $80,264$48,760 0.49% $25,765 $0 0.00% $0 $80,641 $42,766 2018 $68,530$48,760 0.00% $24,538 $0 -0.25% $0 $80,533 $40,675 2019 $65,212$48,760 -0.08% $23,350 $0 -0.51% $0 $156,879 $75,462 2020 $98,812$48,760 0.32% $22,310 $0 0.13% $0 $99,775 $45,708 2021 $68,019$48,760 0.81% $21,420 $0 1.40% $0 $80,533 $35,136 2022 $56,556$48,760 0.16% $20,432 $0 0.13% $0 $80,533 $33,463 2023 $53,896$48,760 -0.60% $19,343 $0 -0.13% $0 $178,205 $70,522 2024 $89,864$48,760 0.40% $18,496 $0 -0.25% $0 $351,833 $132,602 2025 $151,098$48,760 0.80% $17,756 $0 -0.25% $0 $80,533 $28,907 2026 $46,663$48,760 0.48% $16,991 $0 0.25% $0 $80,533 $27,530 2027 $44,522$48,760 0.36% $16,240 $0 0.38% $0 $80,533 $26,219 2028 $42,459$48,760 0.32% $15,515 $0 0.25% $0 $102,397 $31,750 2029 $47,265$48,760 0.35% $14,829 $0 0.37% $0 $336,737 $99,439 2030 $114,268

$1,219,000 $649,093 $0 $0 $3,143,668 $1,658,761 $12,567,380

OVERALL LIFE-CYCLE COST PRESENT WORTH ANALYSIS

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

The following list represents potential challenges to implementation of the McDuster System and their respective responses. The McDuster System would need to overcome these in order to be successfully implemented on a real project.

Paradigm Paralysis

o As fossil fuels and energy become scarce and costs continue to escalate, new alternatives to traditional HVAC systems must be developed. As this report shows, energy saving technology is available today and makes economic sense now. There will be no room for ‘Paradigm Paralysis’ for the next generation of HVAC designers.

Future buildings blocking the solar collectors

o This does represent a major hit on the McDuster system, as the basic concept involves drawing large amounts of energy from the sun. However, derivatives of the McDuster can be developed for situations in which adequate sun is not available. Micro turbine technology could be used to drive a cogeneration system in which lower grade waste heat would drive this system. The possibilities of applying concepts developed within this paper are only limited by the designer’s creativity.

Permits/Studies needed to draw water from the Boston Harbor

o Currently, permits have been issued to discharge sewage effluent from the Deer Island Wastewater Treatment Plant into Massachusetts Bay! Permits are obtained from the Massachusetts Water Resources Authority. Extensive studies on water quality and current movement have already been done and are already paid for. The Boston harbor complete changes once every three days with the tidal changes. Localized water temperatures may be changed, but given the vastness of the harbor no effect would be felt. The Massachusetts Water Resource Authority is dedicated to protecting the water quality as well as supporting systems that make sense: the McDuster system makes sense and its environmental impact due to increased water temperature could easily be studied.

Storage tank emptied for maintenance

o With the storage tank empty for up to a month every 12 years for maintenance, alternative preparations would have to be made. Ideally, the existing diesel backup engine could temporarily compensate and develop much of the heat needed for running the Institute of Contemporary Art. By hooking up the diesel generator to a smaller tank temporarily located outdoors, it would essentially act as a cogeneration machine and economically create high-grade heat. Technology is available to lower the emissions from a diesel generator and allow for legal operation.

LiCl delaminates from substrate/ It is corrosive to equipment

o Quoted from the manufacture:

“The LiCi is permanently bonded to the substrate in a unique process that will not allow run off. Also, in the process the LiCl is treated making it non-corrosive. The only caution is that the rotor should not be exposed to excessive temperatures. At some point above 158F, the solution will depart from the substrate in powder form.”

LiCl continues to absorb moisture and failure occurs

o Quoted from the manufacture:

POTENTIAL CHALLENGES: IS THE SYSTEM TOO GOOD TO BE TRUE?

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

“Yes, the LiCl is extremely hydroscopic and it will absorb moisture even when it is off. So, to avoid uneven weight distribution the Klingenburg controller rotates the rotor at predetermined intervals during the off cycle.”

Temperatures in the tank are not high enough

o Electric resistance ‘booster’ heating elements are designed into the McDuster system. Ideally, these would be located inside the tank at the top to boost the temperature of the water using off peak electric. Energy losses to the surrounding environment are small and thus ignored.

Air handling unit is too complex

o It is true, the proposed McDuster air-handling unit involves many more components than is traditionally associated with most units. The term complex should be held loosely though. One could successfully argue that chillers, boilers, and compressors are ‘complex’ devices; none of which are needed with this system. The components within the unit, except for the LiCl desiccant wheel, are commonly employed and their performance characteristics are well understood by the professional HVAC community. New concepts are inherently difficult to understand and may, at first, seem ‘complex’.

Desiccant wheel cannot possibly humidify during those dry winter days

o The LiCl wheel was simulated with a link directly the manufacture’s performance program. The manufacturer, Klingenburg, has been in the market delivering the highest quality desiccant wheels for over 60 years. Using an enthalpy wheel along with the desiccant wheel further helps to increase its ability to humidify. Although, there is no substitute for real time data. Results show that the wheel can maintain 50% humidity.

Trying to find a contractor who will install at reasonable cost

o An exhaustive and detailed cost analysis was performed with this system. The components of the system are well known to most contractors, although the way they are pieced together is unique. System pricing for custom designing was accounted for. See the first cost analysis. As time progresses, and the system installation becomes more common, the contractor’s installation cost will fall further.

Radiant ceilings ‘rain’ down on occupants and artwork

o Strict humidity control is the principle advantage for the McDuster system. With 50% relative humidity maintained, it would take surface temperatures below 53F before condensation would even start to form. Fail safe condensate sensors would be used in addition.

Radiant floors condense and cause slippery floors

o Again, strict humidity control is the principle advantage of the McDuster System. See above note.

Pump failure o The McDuster system relies heavily upon pumps to distribute energy directly to where it

is most efficiently utilized. However, pumps are among the most reliable piece of equipment in an HVAC designer’s arsenal. Redundant pumps were designed into every loop in the system. Failure of one pump will not have any effect. Failure of multiple pumps at the same time represents catastrophic failure and the building would be closed. Existing reasonable designs do not contend with such events.

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

This report has identified many of the system components to give a detailed overall picture of the mechanical systems within the Institute of Contemporary Art. Due to the nature of this museum, energy efficiency, simplicity, and reliability took a backseat to program needs bigger such as architecture, structure, and natural day lighting. First cost had a huge influence on the mechanical system design. Construction was delayed more than a year due to gross budget overruns and redesigns. With these aspects in mind, this unique building simulation is presented. Energy simulations predict that the ICA will use approximately 68,020 therms per year with an annual predicted cost of natural gas starting out at $78,388. A detailed model was carried out in Carrier’s Hourly Analysis Program v.4.2 showing that the Institute of Contemporary Art is predicted to consume 1,196,640 kW/yr. Using Nstar utility rates, the annual electricity consumption cost is estimated to be $185,153. The relatively high use of energy is also paid for in lost usable space. Approximately 8,700ft2, or approximately 14% of the ICA is ‘unusable’ space due to Utility space. The total initial start-up construction cost estimate for the ICA building is $33,667,308. Actual Bidding data from HVAC, Electrical, Plumbing, and Fire Protection shows a first cost for these systems to be $10,259,527. The net present value for mechanical, electrical, plumbing, fire protection, and elevator services at the Institute of Contemporary Art (ICA) building is $16,570,577, almost half of the overall first cost. Thus, long term predicted operating costs would cost the Institute of Contemporary Art large sums of money. This energy results in a significant environmental impacts as well as being a financial burden. The ICA is predicted to release 820 pounds of particulates, 9,022 pounds of So2, 5,979 pounds of Nox, and 1,651,408 pounds of C02. The Institute of Contemporary Art is a bold architectural statement and is sure to attract the attention of all who pass by, but it comes with a hefty energy price tag as well as environmental impact. The McDuster solves every one of the previously defined problems. By combining ocean cooling, solar heating, and desiccant conditioning, the entire building’s sensible and latent loads can be met within 50% +/- 5% relative humidity and 73F+/- 2F. Remarkably, this system operates entirely off of pump and fan power alone. A detailed analysis of the McDuster system was presented in this report and the results show an amazing 82% reduction in the annual utility bill, a savings of $214,780. Furthermore, it is estimated that the first costs of the McDuster system is $143,884 dollars less than the currently designed system. The McDuster does not use any CFCs, reduces first cost, reduces energy consumption, decreases noise production, and is environmentally friendly. The present worth savings value of the McDuster system using a discount rate of 4.5% over 25 years is $4,617,810, which completely covers the first cost of the original HVAC system. Guaranteed future rises in energy are bound to increase this figure and make the McDuster an even bigger financial payoff. It is the strong recommendation of the author that this system be investigated further. Additional research should be geared toward producing a prototype so that simulated results can be verified. As energy prices continue to rise and the earth continues to choke under emissions released from buildings, the need for a new breed of HVAC systems will become inevitable. This report represents the next generation of HVAC as we look optimistically toward the future. The McDuster: its time has come.

― THE MCDUSTER: ― THE NEXT GENERATION OF HVAC

CONCULSIONS / RECOMMENDATIONS

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Akbari, Hashem, “Cool Roofs Save Energy”, ASHRAE Transactions: Symposia, 1998. Brunk, M.F., “Cooling Ceilings-An Opportunity To Reduce Energy Costs By Way of Radiant Cooling”,

ASHRAE Transactions: Symposia, 1993. Busweiler, U., “Air Conditioning With a Combination of Radiant Cooling, Displacement Ventilation, and

Desiccant Cooling”, ASHRAE Transactions: Symposia, 1993. “Boston Harbor”, http://www.mwra.state.ma.us/harbor/html/wklyintr.htm, MWRA online, 2005. Carli, Michele De, “Field Measurements of Thermal Comfort Conditions in Buildings with Radiant Surface

Cooling Systems”, Clima 2000/Napoli 2001 World Congress, September 2001. Chau, C.K. and William M. Worek, “Interactive Simulation Tools For Open-Cycle Desiccant Cooling

Systems”, ASHRAE Transactions: Symposia, 1995. “Cornell University Lake Source Cooling”, Humphreys Service Building, Ithaca, NY, December 2, 2004. Deighan, James, “SEC Heat Exchangers”, Quote from SEC, January 18, 2005. “Desiccant Dehumidification and Pressure Drying Equipment”, Chapter 22, 2000 ASHRAE Systems and

Equipment Handbook, 2000. “Development of Plastic Heat Exchangers for Ocean Thermal Energy Conversion”, StormingMedia,

www.stormingmedia.us, January 12, 2005. Duffie, John A and William A. Beckman, Solar Engineering Of Thermal Processes, John Wiley & Sons,

Inc., 1991. “DWSC System Configerations and Design Considerations”,

http://www.energy.rochester.edu/idea/cooling/1995/dwsc/config.htm, 2005. Fischer, J., Hallstrom, A, and Sand J., “Desiccant-Based Preconditioning Market Analysis”, June 2000. Freund, Sebastian., S.A. Klein, and D.T. Reindl, “A Semi-Empirical Method to Estimate Enthalpy

Exchanger Performance and a Comparison of Alternative Frost Control Strategies”, HVAC&R Research, October 2003.

Ginestet, Stephane, Pascal Stabat, and Dominique Marchio, “Control Strategies of Open Cycle Desiccant

Cooling Systems Minimising Energy Consumption”. Gretarsson, S.P., “Development of a Fundamentally Based Stratified Thermal Storage Tank Model For

Energy Analysis Calculations”, ASHRAE Transactions: Symposia, 1994. Hiller, Carl C., “New Hot Water Consumption Analysis and Water-Heating System Sizing Methodology”,

ASHRAE Transactions: Symposia, 1998. Jiang, Mingshun and Meng Zhou, “Comparison Report Between HydroQual and University of

Massachusetts Boston Runs”, Department of Environmental, Coastal, and Ocean Sciences, University of Massachusetts Boston, September 2, 2003.

WORKS CITED

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Kilkis, B.I., “Radiant Ceiling Cooling With Solar Energy: Fundamentals, Modeling, and A Case Design”, ASHRAE Transactions: Symposia, 1993.

KingSolar, http://kingsolar.com/catalog/mfg/aet/ae-32.html, 2005. Klingenburg, “SECO Desiccant/Enthalpy/dehumidification rotors”, Energy Recovery Catalogue, Gladbeck,

Germany, 2005. Klingenburg, “Design Program for SECO Dessicant-/Enthalpy-Regenerators 32-Bit Windows DLL:

SECO.DLL”, 2002. Kulpmann, R.W., “Thermal Comfort and Air Quality in Rooms With Cooled Ceilings- Results of Scientific

Investigations”, ASHRAE Transactions: Symposia, 1993. Lowenstein, Andrew, “The Seasonal Performance of a Liquid-Desiccant Air Conditioner”, ASHRAE

Transactions: Symposia, 1995. Massport: Waterfront Planing and Development,

http://www.massport.com/business/water_water_south.html, 2005 Meierhans, R.A., “Slab Cooling and Earth Coupling”, ASHRAE Transactions: Symposia, 1993. Mueller Heat Transfer Products, http://www.muel.com/products/heattransfer/plate/hvac.cfm, 2005. “Ocean Thermal Energy Conversion”, National Renewable Energy Laboratory,

www.nrel.gov/otec/electricity_heat_exchangers.html, January 12, 2005. Olesen, Bjarne W., “Cooling and Heating of Buildings By Activating the Thermal Mass With Embedded

Hydronic Systems”, ASHRAE Transactions, CIBSE Dublin 2000. Olesen, Bjarne W., “Possibilities and Limitations of Radiant Floor Cooling”, ASHRAE Transactions:

Research. Radiant Panel Association, http://www.radiantpanelassociation.org/i4a/pages/index.cfm?pageid=140,

2005. Rafferty, Kevin D., “Heat Exchangers”, Gene Culver Geo-Heat Center. “Seawater Cooling System for Buildings”, Natural Resources Canada, November 20, 2004. Simmonds, P., “Control Strategies For Combined Heating and Cooling Radiant Systems”, ASHRAE

Transactions: Symposia, 1994. “The State of Boston Harbor”, http://www.mwra.state.ma.us/harbor/html/2002-09.htm, MWRA

Massachuetts, 2005. Sterling, “Radiant Cooling Panel”, Design Guide for Sizing Radiant Ceiling, 2005. Stewart, William E., Lihong Cai, and C.W. Sohn, “Thermal Stratification of Chilled-Water Slot Flows Into

Storage Tanks”, ASHRAE Transactions: Research. Udagawa, M., “Simulation of Panel Cooling Systems With Linear Subsystem Model”, ASHRAE

Transactions: Symposia”, 1993.

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

“USGS Contaminants in the Coastal Ocean”, www.marine.usgs.gov/fact-sheets/fs172-97/contaminants.html, December 3, 2004.

“Statistics of Current and Temperature Obervations”,

http://pubs.usgs.gov/dds/dds74/MBLT_rep/Web_Pages/stats_cur_temp.htm, “USGS Science for a changing world”.

Vineyard, Edward., James R. Sand, and David J. Durfee, “Parametric Analysis of Variables That Affect the Performance of a Desiccant Dehumidification System”, ASHRAE Tranactions: Research. Vineyard, Edward., “Performance Characteristics for a Desiccant System at Two Extreme Ambient

Conditions”, ASHRAE Transactions: Symposia, 2002. West, Michael K., “Analysis of a Field-Installed Hybrid Solar Desiccant Cooling System”, ASHRAE

Transactions: Symposia, 1995. West, Michael K., “Specifying Desiccant Dehumidifiers”, HPAC Engineering, November 2004. Wirsbo, http://www.wirsbo.com/main.php?pm=1&mm=0&sm=0&pc=homeowner/ho_mm0sm0.php,

Radiant Floor Systems, 2005. Zhou, Meng, “Test Results of the Massachusetts Bay Hydrodynamic Model (Year 1994)”, Environmental

Coastal and Ocean Sciences, University of Massachusetts Boston, January 15, 2002. Zweifel, G. Dipl, “Simulation of Displacement Ventilation and Radiant Cooling With Doe-2”, ASHRAE

Transactions: Symposia, 1993.

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

1. Cost associated with yearly maintenance: The wheel media doesn’t need any maintenance. As such there are no fixed costs associated with yearly maintenance unless there is a failure with the motor and any mechanical components.

2. Life Expectancy of the wheel: About 20 years. 3. Estimate for installation of just the wheel: The OEM’s whom we sell these components to, are

expected to install them. The installation should be fairly easy.

APPENDIX A: LICL SECO DESICCANT WHEEL QUOTE

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

APPENDIX B: TITANIUM HEAT EXCHANGER PRICING QUOTE

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

APPENDIX C: NSTAR ELECTRIC AND KEYSPAN NATURAL GAS RATES

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Monthy Simulation Results for AHU 1 East Gallery

Month

Preheat Coil Load

(kBTU)

Preheat Coil Input

(kWh)

Central Cooling Coil

Load(kBTU)

Central Cooling Eqpt

Load(kBTU)

Central Unit Clg Input

(kWh)

Central Heating Coil Load

(kBTU)

Central Heating Coil Input

(kWh)January 10772 3157 807 13 7 0 0

February 1331 390 5421 12 7 2397 702

March 1268 372 1674 20 12 0 0

April 0 0 27501 168 86 6399 1875

May 0 0 111545 477 300 11916 3492

June 0 0 294519 717 495 33011 9675

July 0 0 425764 838 621 43352 12705

August 0 0 409241 843 615 44212 12957

September 0 0 229688 752 473 32105 9409

October 0 0 116413 508 299 23191 6797

November 0 0 55385 191 95 15252 4470

December 2637 773 995 5 3 601 176

Total 16008 4691 1678952 4544 3013 212435 62258

Month

Terminal Heating Coil

Load (kBTU)

Terminal Heating Coil

Input (kWh)

Humidifier Load

(lb)

Humidifier Input

(kBTU)Supply Fan

(kWh) Return Fan

(kWh)Lighting

(kWh)January 208309 61049 119232 132347 6092 4061 15178

February 162683 47678 108311 120225 5502 3668 13709

March 165309 48447 130292 144624 6092 4061 15178

April 122658 35948 95733 106264 5895 3930 14689

May 97369 28536 95413 105908 6092 4061 15178

June 65195 19107 11902 13211 5895 3930 14689

July 59410 17411 1802 2001 6092 4061 15178

August 63357 18568 1609 1786 6092 4061 15178

September 87862 25750 33564 37256 5895 3930 14689

October 118972 34867 71407 79262 6092 4061 15178

November 144613 42382 86936 96499 5895 3930 14689

December 194303 56945 112459 124829 6092 4061 15178

Total 1490041 436688 868659 964211 71727 47818 178712

APPENDIX D: EXISTING DESIGN CARRIER HAP PROGRAM SIMULATION

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Monthy Simulation Results for AHU 2 West Gallery

Month

Preheat Coil Load

(kBTU)

Preheat Coil Input

(kWh)

Central Cooling Coil

Load(kBTU)

Central Cooling Eqpt

Load(kBTU)

Central Unit Clg Input

(kWh)

Central Heating Coil Load

(kBTU)

Central Heating Coil Input

(kWh)January 4948 1450 761 13 7 0 0

February 665 195 4798 12 7 2055 602

March 275 80 1577 20 12 0 0

April 0 0 24540 164 86 4899 1436

May 0 0 103431 477 300 10914 3198

June 0 0 270789 717 495 29782 8728

July 0 0 391228 838 621 39507 11578

August 0 0 376784 843 615 40403 11841

September 0 0 212953 752 473 29397 8615

October 0 0 107948 508 299 20890 6122

November 0 0 50969 191 95 13809 4047

December 846 248 880 5 3 539 158

Total 6733 1973 1546659 4540 3013 192195 56327

Month

Terminal Heating Coil

Load (kBTU)

Terminal Heating Coil

Input (kWh)

Humidifier Load

(lb)

Humidifier Input

(kBTU)Supply Fan

(kWh) Return Fan

(kWh)Lighting

(kWh)January 196732 57656 110230 122355 5742 3828 14540

February 153504 44988 102013 113234 5186 3457 13133

March 158070 46326 123678 137283 5742 3828 14540

April 118369 34690 91946 102060 5556 3704 14071

May 94206 27609 91247 101285 5742 3828 14540

June 62951 18449 11402 12657 5556 3704 14071

July 56850 16661 1747 1939 5742 3828 14540

August 60766 17809 1537 1706 5742 3828 14540

September 84740 24835 32312 35866 5556 3704 14071

October 114768 33635 68594 76139 5742 3828 14540

November 139253 40811 83334 92501 5556 3704 14071

December 183129 53670 105357 116947 5742 3828 14540

Total 1423338 417139 823396 913969 67602 45068 171202

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Monthy Simulation Results for AHU 3 Theater

Month

Preheat Coil Load

(kBTU)

Preheat Coil Input

(kWh)

Central Cooling Coil

Load(kBTU)

Central Cooling Eqpt

Load(kBTU)

Central Unit Clg Input

(kWh)

Terminal Heating Coil

Load(kBTU)

Terminal Heating Coil

Input(kWh)

January 0 0 1052 13 7 119149 34919

February 0 0 1544 12 7 103492 30331

March 0 0 2181 20 12 112633 33010

April 0 0 22366 149 86 101588 29773

May 0 0 111175 474 300 99210 29076

June 0 0 274343 706 495 89582 26254

July 0 0 397496 838 621 90419 26499

August 0 0 382280 843 615 91651 26860

September 0 0 206303 724 473 93894 27517

October 0 0 89047 497 299 102578 30063

November 0 0 33351 159 95 105651 30963

December 0 0 239 5 3 117269 34368

Total 0 0 1521377 4440 3013 1227117 359632

Month Supply Fan

(kWh) Return Fan

(kWh) Lighting

(kWh)

Electric Equipment

(kWh)January 7938 5292 48613 0

February 7170 4780 43909 0

March 7938 5292 48613 0

April 7682 5122 47045 0

May 7938 5292 48613 0

June 7682 5122 47045 0

July 7938 5292 48613 0

August 7938 5292 48613 0

September 7682 5122 47045 0

October 7938 5292 48613 0

November 7682 5122 47045 0

December 7938 5292 48613 0

Total 93469 62313 572380 0

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Monthy Simulation Results for AHU 4 Lobby, Admin, and Back Sup

Month

Preheat Coil Load

(kBTU)

Preheat Coil Input

(kWh)

Central Cooling Coil

Load(kBTU)

Central Cooling Eqpt

Load(kBTU)

Central Unit Clg Input

(kWh)

Terminal Heating Coil

Load(kBTU)

Terminal Heating Coil

Input(kWh)

January 55604 16296 1544 17 7 17053 4998

February 43520 12755 1205 13 7 8879 2602

March 45447 13319 1860 23 12 6757 1980

April 16908 4955 13357 169 86 1410 413

May 4789 1404 84475 495 300 809 237

June 145 43 237108 709 495 27 8

July 0 0 323967 838 621 0 0

August 0 0 292402 843 615 0 0

September 605 177 127558 759 473 68 20

October 6383 1871 40943 538 299 1180 346

November 24041 7046 14886 175 95 5024 1472

December 48723 14279 1010 5 3 14594 4277

Total 246167 72144 1140314 4584 3013 55801 16354

Month Supply Fan

(kWh) Return Fan

(kWh) Lighting

(kWh)

Electric Equipment

(kWh)January 2811 1874 12878 17598

February 2727 1818 11632 15895

March 3170 2113 12878 17598

April 3480 2320 12463 17030

May 4160 2773 12878 17598

June 4596 3064 12463 17030

July 4844 3229 12878 17598

August 4750 3167 12878 17598

September 4199 2799 12463 17030

October 3786 2524 12878 17598

November 3129 2086 12463 17030

December 2848 1899 12878 17598

Total 44499 29666 151633 207204

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Monthy Simulation Results for AHU 5 Mediateque

Month

Preheat Coil Load

(kBTU)

Preheat Coil Input

(kWh)

Central Cooling Coil

Load(kBTU)

Central Cooling Eqpt

Load(kBTU)

Central Unit Clg Input

(kWh)

Central Heating Coil Load

(kBTU)

Central Heating Coil Input

(kWh)January 0 0 101 12 6 10686 3132

February 0 0 289 13 7 6524 1912

March 0 0 765 25 12 5962 1747

April 0 0 2996 181 84 1365 400

May 0 0 8101 534 300 368 108

June 0 0 15049 723 495 40 12

July 0 0 18637 838 621 0 0

August 0 0 17247 843 615 0 0

September 0 0 10080 728 464 56 17

October 0 0 5206 527 293 916 268

November 0 0 1935 151 87 3202 938

December 0 0 110 11 3 8625 2528

Total 0 0 80517 4586 2987 37744 11062

Month Supply Fan

(kWh) Return Fan

(kWh) Lighting

(kWh)

Electric Equipment

(kWh)January 663 442 622 2671

February 599 399 562 2413

March 663 442 622 2671

April 642 428 602 2585

May 663 442 622 2671

June 642 428 602 2585

July 663 442 622 2671

August 663 442 622 2671

September 642 428 602 2585

October 663 442 622 2671

November 642 428 602 2585

December 663 442 622 2671

Total 7811 5207 7326 31453

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

FUNCTION Term(Ra,beta) Check:=1-1708/(Ra*cos(beta)) IF(Check<0) THEN Term:=0 ELSE Term:=Check ENDIF END FUNCTION Term2(Ra,beta) Check:=(Ra*cos(beta)/5830)^(1/3)-1 IF(Check<0) THEN Term2:=0 ELSE Term2:=Check ENDIF END FUNCTION wind(V,L) wind=max(5,8.6*V^.6/L^.6) END "INTERNAL CONVECTION" "Inputs" L_c=25/1000 "distance b/w plate and cover (m)" T_pm=85 "T_pm_ENG*convert('F','C')" "mean plate temperature (C) - might somehow calculate this later" T_a=T_a_ENG*convert('F','C') "ambient temperature (C)" "T_cover" "cover temperature (C) - calculated in HEAT LOSS COEFFICIENT section" beta=45 "collector angle" "Convection Analysis" P1=1*convert('atm','Pa') T1=(T_cover+T_pm)/2 "average temperature for properties of enclosed air" mu=VISCOSITY(Air,T=T1) "dynamic viscosity" nu=mu/rho "kinematic viscosity" rho=DENSITY(Air,T=T1,P=P1) "density" Pr=PRANDTL(Air,T=T1) "Prandtl number" c_p=CP(Air,T=T1)*1000 alpha=k/(rho*c_p) Gr=9.81*(1/(T_a+273))*(T_pm-T_cover)*L_c^3/(nu*alpha) "Grashoff number" Ra=Gr*Pr "Raleigh number" k=CONDUCTIVITY(Air,T=T1) "conductivity" "Convection Results" theTerm=Term(Ra,beta)

APPENDIX E: EES SOLAR LOSS SIMULATION CODE

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

theTerm2=Term2(Ra,beta) Nus=1+1.44*(1-1708*(sin(1.8*beta))^1.6/(Ra*cos(beta)))*theTerm+theTerm2 "Nusselt Number" h_c_pc=Nus*k/L_c "convection, plate to cover" "HEAT LOSS COEFFICIENT" "Additional Inputs" epsilon_c=.88 "cover emittance" epsilon_p=.95 "plate emittance" V=20000 "building volume (m^3)" Vel=5 "wind velocity (m/s)" L=40 "building characteristic length (m)" sigma=5.67*10^(-8) "Stefan-Boltzman constant" T_wb=T_wb_ENG*convert('F','C') "wetbulb temperature" "Hr" "hour from midnight" "Heat Loss Analysis" T_cover=T_pm-U_t*(T_pm-T_a)/(h_c_pc+h_r_pc) "cover temperature (C)" T_s+273=(T_a+273)*(.711+.0056*T_dp+.000073*T_dp^2+.013*cos(15*Hr))^.25 T_dp=DEWPOINT(AirH2O,T=T_a,P=P1,B=T_wb) "dewpoint temperature" h_r_pc=sigma*((T_pm+273)^2+(T_cover+273)^2)*(T_pm+273+T_cover+273)/(1/epsilon_p+1/epsilon_c-1) "radiation, plate to cover" h_r_ca=epsilon_c*sigma*((T_cover+273)^2+(T_s+273)^2)*(T_cover+273+T_s+273) "radiation, cover to ambient" h_w=wind(Vel,L) "convection, cover to ambient" "Heat Loss Results" U_t=(1/(h_c_pc+h_r_pc)+1/(h_w+h_r_ca))^(-1) "USEFUL ENERGY" "Inputs" "S" "total absorbed solar radiation" A_c=13000*convert('ft^2','m^2') "collector area" "Analysis" U_b=k/L_c U_l=U_t+U_b "Results" Losses=U_l*(T_pm-T_a) Q_u=A_c*(S-Losses)

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

PROCEDURE Factors(type:r_0,r_1,r_k) row:=lookuprow('Correction Factors','Index',type) r_0:=lookup('Correction Factors',row,3) r_1:=lookup('Correction Factors',row,4) r_k:=lookup('Correction Factors',row,5) END PROCEDURE Daylight(theta_z:day) IF(theta_z>=90) THEN day=0 ELSE day=1 ENDIF END "GENERAL INPUTS" type=0 "Standard Climate" phi=42.4 "Latitude" A=0 "Altitude (km)" "Hr=8" "Current Hour (Std Time)" hem=1 "Hemisphere (+ North, - South)" "n=1" "Day of Year" midHr=1 "Calculate Average at Midpoint of Hour? (1 yes, 0 no)" L_st=71.05 "Standard Longitude" L_loc=75 "Longitude of Time Zone Reference" K_t=.444 "Clearness Ratio" beta=60 "Solar Collector Angle" "INITIAL CALCULATIONS" "Solar Time" time=Hr+.5*midHr+(4*(L_st-L_loc)+E)/60 E=229.2*(.000075+.001868*cos(B)-.032077*sin(B)-.014615*cos(2*B)-.04089*sin(2*B)) B=(n-1)*360/365 omega=(time-12)*15 delta=hem*23.45*sin(360*(284+n)/365) theta_z=arccos(cos(phi)*cos(delta)*cos(omega)+sin(phi)*sin(delta)) "BEAM RADIATION" Call Factors(type:r_0,r_1,r_k) a_0*r_0=.4237-.00821*(6-A)^2 a_1*r_1=.5055+.00595*(6.5-A)^2 k*r_k=.2711+.01858*(2.5-A)^2 Call Daylight(theta_z:day) G_sc=1367*day G_on=G_sc*(1+.033*cos(360*n/365))

APPENDIX F: EES CLEAR SKY SIMULATION CODE

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

I_cb=G_on*3600*tau_b*cos(theta_z) interim=cos(theta_z) tau_b=(a_0+a_1*exp(-k/interim))*day tau_d=.271-.294*tau_b I_d=G_on*3600*tau_d*cos(theta_z) I_c=I_cb+I_d

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Item_Desc Takeoff_Quantity Takeoff_Unit UnitCost Total Existing Design Total Difference in Cost

Piles - Steel H PileH Piles- end bearing at building - inc 1 test 76.00 no 7,350.00 558,600 565,950 7,350 Pile coating 1.00 ls 35,065.00 35,065 36,000 935

Concrete SuperstructureConcrete on metal decking 41,135.00 sf 5.00 205,675 222,955 17,280

Structural Steel - Structural steel 313.00 ton 3,150.00 985,950 1,033,200 47,250

Floor DeckMetal deck 45,594.00 sf 3.21 146,357 157,451 11,094

Stairs & LaddersMisc. stairs at mechanical mezzanine 0.00 flt 7,878.00 23,634 23,634

Building Insulation3" rigid insulation at mechanical penthouse 0.00 sf 4.75 - 2,537 2,537

FireproofingFireproofing 45,594.00 sf 3.68 167,786 180,504 12,718

Siding - AluminumMechanical Mezzanine Aluminum Siding/Mesh Exterior 0.00 sf 28.00 - 60,788 60,788

Doors - Hol MetalHM doors, 90 min, single 17.00 ea 650.00 11,050 12,350 1,300

DrywallReturn duct plenum, GWB enclosure at Gallery 0.00 sf 12.00 - 98,928 98,928

Louvers Metal OperableMetal louvers 0.00 sf 45.00 - 4,500 4,500 50% open perforated suspended panels 0.00 sf 10.00 - 41,800 41,800

Fuel & Gas Piping6" black steel pipe welded with hangers 0.00 lf 125.00 - 50,000 50,000 Boiler Piping to equipment 0.00 ls 10,000.00 - 10,000 10,000 Gas Venting 0.00 ls 2,000.00 - 8,000 8,000 Boiler Connections 0.00 no 2,500.00 - 10,000 10,000 Gas meter connection 0.00 no 400.00 - 400 400 WH Connections 0.00 no 750.00 - 750 750

EquipmentSteam boiler gas fired 212 MBH 0.00 no 7,500.00 - 15,000 15,000 Hot water boiler gas fired 1,500 MBH 0.00 no 19,000.00 - 38,000 38,000 Chiller air cooled 143 ton 0.00 no 102,000.00 - 204,000 204,000 Pump hot water end suction 150 GPM with VFD 0.00 no 3,625.00 - 7,250 7,250 Pump chilled water end suction 772 GPM with VFD 0.00 no 7,300.00 - 14,600 14,600 Pump hot water 44 GPM 0.00 no 1,700.00 - 3,400 3,400 Pump hot water 36 GPM 0.00 no 1,400.00 - 2,800 2,800 Pump hot water 22 GPM 0.00 no 850.00 - 1,700 1,700 Condensate pump 55 GPM 0.00 no 250.00 - 1,500 1,500 Condensate cooling tank 0.00 no 2,500.00 - 2,500 2,500 AHU 30,500 CFM 0.00 no 144,875.00 - 144,875 144,875 AHU 22,500 CFM 0.00 no 106,875.00 - 106,875 106,875 AHU 20,890 CFM 0.00 no 99,227.00 - 99,227 99,227 AHU 21,150 CFM 0.00 no 100,462.00 - 100,462 100,462 Computer AC 2,500 CFM 5 ton with humidifier 0.00 no 5,000.00 - 5,000 5,000 Computer AC 1,415 CFM 2.5 ton with humidifier 0.00 no 2,900.00 - 2,900 2,900 Computer AC 900 CFM 2 ton with humidifier 0.00 no 1,800.00 - 1,800 1,800 Fan coil unit 4,000 CFM with cooling coil 0.00 no 8,000.00 - 8,000 8,000 Fan coil unit 2,500 CFM with cooling coil 0.00 no 6,000.00 - 6,000 6,000 Fan coil unit 2,000 CFM with cooling coil 0.00 no 4,500.00 - 4,500 4,500 Fan coil unit 1,400 CFM with cooling coil 0.00 no 3,000.00 - 3,000 3,000 Fan coil unit 500 CFM with cooling coil 0.00 no 1,200.00 - 1,200 1,200 Fan coil unit 450 CFM with cooling coil 0.00 no 1,100.00 - 1,100 1,100 Fan coil unit 660 CFM 0.00 no 950.00 - 2,850 2,850 Fan coil unit 210 CFM 0.00 no 470.00 - 940 940 Make-up air fan 35,200 CFM 0.00 no 26,400.00 - 26,400 26,400 Dust collection system for woodshop (allowance) 0.00 no 1,800.00 - 1,800 1,800 Radiant heat panel to include mounting & connections 0.00 no 250.00 - 46,250 46,250 Steam humidifier 201 lbs/hr 0.00 no 3,300.00 - 3,300 3,300 Steam humidifier 233 lbs/hr 0.00 no 3,825.00 - 3,825 3,825 VAV unit 2,200 CFM 0.00 no 1,650.00 - 3,300 3,300 VAV unit 1,995 CFM 0.00 no 1,496.00 - 1,496 1,496 VAV unit 1,920 CFM 0.00 no 1,440.00 - 2,880 2,880 VAV unit 1,800 CFM 0.00 no 1,350.00 - 1,350 1,350 VAV unit 1,600 CFM 0.00 no 1,200.00 - 4,800 4,800 VAV unit 1,525 CFM 0.00 no 1,143.00 - 1,143 1,143 VAV unit 1,500 CFM 0.00 no 1,125.00 - 1,125 1,125 VAV unit 1,450 CFM 0.00 no 1,087.00 - 3,261 3,261 VAV unit 1,250 CFM 0.00 no 937.00 - 3,748 3,748 VAV unit 1,245 CFM 0.00 no 933.00 - 1,866 1,866 VAV unit 1,200 CFM 0.00 no 900.00 - 2,700 2,700 VAV unit 1,150 CFM 0.00 no 862.00 - 862 862 VAV unit 1,000 CFM 0.00 no 750.00 - 750 750 VAV unit 810 CFM 0.00 no 607.00 - 607 607

APPENDIX G: FIRST COST DEDUCTIONS

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

VAV unit 800 CFM 0.00 no 600.00 - 600 600 VAV unit 780 CFM 0.00 no 585.00 - 585 585 VAV unit 760 CFM 0.00 no 570.00 - 570 570 VAV unit 680 CFM 0.00 no 510.00 - 510 510 VAV unit 675 CFM 0.00 no 506.00 - 506 506 VAV unit 660 CFM 0.00 no 495.00 - 495 495 VAV unit 550 CFM 0.00 no 412.00 - 412 412 VAV unit 450 CFM 0.00 no 337.00 - 337 337 VAV unit 400 CFM 0.00 no 300.00 - 300 300 VAV unit 375 CFM 0.00 no 281.00 - 281 281 VAV unit 300 CFM 0.00 no 225.00 - 225 225 Transfer fan 1,600 CFM 0.00 no 3,200.00 - 3,200 3,200 Transfer fan 1,500 CFM 0.00 no 3,000.00 - 9,000 9,000 Transfer fan 1100 CFM 0.00 no 2,200.00 - 4,400 4,400 Transfer fan 950 CFM 0.00 no 1,900.00 - 1,900 1,900 Cabinet unit heater 1,100 MBH 0.00 no 850.00 - 3,400 3,400 Unit heater 630 CFM 0.00 no 1,100.00 - 1,100 1,100 Unit heater 300 CFM 0.00 no 510.00 - 510 510 Unit heater 210 CFM 0.00 no 360.00 - 2,160 2,160 Fin tube radiation 0.00 lf 75.00 - 48,750 48,750 Sound attenuator 5' 0.00 no 3,000.00 - 30,000 30,000 VFD's for required equipment 0.00 no 5,200.00 - 36,400 36,400 Computer AC-4 0.00 no 1,800.00 - 1,800 1,800

Hot Water6" black steel pipe welded with hangers 0.00 lf 66.00 - 13,200 13,200 3" black steel pipe welded with hangers 0.00 lf 35.00 - 31,500 31,500 2 1/2" black steel pipe with fittings & hangers 0.00 lf 30.00 - 27,900 27,900 2" black steel pipe with fittings & hangers 0.00 lf 23.00 - 28,750 28,750 1 1/2" black steel pipe with fittings & hangers 0.00 lf 18.00 - 51,876 51,876 1 1/4" black steel pipe with fittings & hangers 0.00 lf 17.00 - 28,900 28,900 1" black steel pipe with fittings & hangers 0.00 lf 14.00 - 9,660 9,660 Boiler connection 0.00 no 6,000.00 - 12,000 12,000 Hot water pump connection end suction 0.00 no 2,800.00 5,600 5,600 Hot water pump connection inline 0.00 no 750.00 4,500 4,500 Unit heater connection 0.00 no 400.00 - 3,200 3,200 Cabinet unit heater connection 0.00 no 450.00 - 1,800 1,800 AHU coil connection 0.00 no 1,000.00 - 4,000 4,000 Fan coil unit connection 0.00 no 750.00 - 8,250 8,250

Chilled WaterChiller connection 0.00 no 7,000.00 - 7,000 7,000 AHU coil connection 0.00 no 1,150.00 - 4,600 4,600 Fan coil unit connection 0.00 no 800.00 - 4,800 4,800

Steam Piping3" black steel pipe welded with hangers 0.00 lf 35.00 - 5,250 5,250 2" black steel pipe welded with hangers 0.00 lf 25.00 - 10,000 10,000 1" black steel pipe with fittings & hangers 0.00 lf 14.00 - 4,200 4,200 1/2" black steel pipe with fittings & hangers 0.00 lf 12.00 - 3,000 3,000 Steam boiler connection 0.00 no 5,500.00 - 11,000 11,000 steam humidifier connection 0.00 no 2,000.00 - 4,000 4,000

InsulationPipe Insulation 0.00 lf 6.00 - 90,912 90,912 Duct insulation 74,392.00 lf 1.25 92,990 185,980 92,990

SheetmetalMedium pressure duct with fittings & hangers 44,949.00 lbs 7.00 314,643 629,286 314,643 Low pressure duct with fittings & hangers 19,316.00 lbs 6.50 125,550 251,102 125,552 Stainless steel welded with fittings & hangers 1,977.00 lbs 11.50 22,735 45,483 22,748 Boiler stacks 0.00 lf 125.00 - 15,000 15,000 Flow bar 1,142.50 lf 35.00 39,987 79,975 39,988 Lay-in supply diffuser with hard connection 46.00 no 70.00 3,220 6,440 3,220 Lay-in return register with hard connection 29.00 no 65.00 1,885 3,770 1,885 Exhaust grille with hard connection 27.00 no 32.50 878 1,755 878 Fire smoke damper 37.00 no 600.00 22,200 44,400 22,200 Smoke damper 5.00 no 475.00 2,375 4,750 2,375 Motorized damper 0.00 no 1,050.00 - 15,750 15,750 Louver inside building 0.00 sf 40.00 - 2,400 2,400

MiscellaneousAir & water balancing 1.00 ls 23,500.00 23,500 47,000 23,500

Distribution Feeders400A feed - complete 1,095.00 lf 54.00 59,130 80,730 21,600

Mechanical Power100A NFSS (CWP, AHU's, EF etc.) 12.00 no 480.00 5,760 6,720 960 400A NFSS NEMA-3R (Chillers) 0.00 no 1,970.00 - 3,940 3,940 20/30A Connection 45.00 no 82.00 3,690 5,330 1,640 100A Connection 12.00 no 196.00 2,352 2,744 392 400A Connection 1.00 no 490.00 490 1,470 980 20/30A Feed 6,675.00 lf 6.26 41,786 60,566 18,780 100A Feed 905.00 lf 11.15 10,090 11,763 1,673

Total Reductions: 2,642,488

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Item_Desc Takeoff_Quantity Takeoff_Unit UnitCost Total

Radiant Floor 487,188 rd 3/4" Oxygen barrier type tubing, PEX (cross-linked polyethylene) 178,440 lf 2.1 374,724

1-1/2" Concrete topping, (25,447 ft^2 already with finished topping) 19163 sf 4.12 78,952 Copper Manifold 1-1/4"X3/4"x72" Lg, 2" sweet drops, 24 circuit 8 Ea 370 2,960 Motorized zone valve with operator complete, 24V and 3/4" 192 Ea 100 19,200 Radiant Heating Pump: 600 GPM Centrifugal end suction with VFD 2 Ea 5,676 11,352

Chilled Ceiling (attached to metal decking) 472,314 3/4" Oxygen barrier type tubing, PEX (cross-linked polyethylene) 136590 lf 2.1 286,839 3/4" Aluminum heat transfer ceiling clips 136590 lf 1.07 146,151 Copper Manifold 1-1/2"X3/4"x72" Lg, 2" sweet drops, 24 circuit 6 Ea 370 2,220 Motorized zone valve with operator complete, 24V and 3/4" 144 Ea 100 14,400 Radiant Cooling Pump: 1200 GPM Centrifugal end suction with VFD 2 Ea 11,352 22,704

Chilled Wall (attached to wall/joists) 58,995 3/4" Oxygen barrier type tubing, PEX (cross-linked polyethylene) 14250 lf 2.1 29,925 Preformed "Zern" plate metal with preformed grooves for tubing 4750 sf 6 28,500 Copper Manifold 1-1/2"X3/4"x72" Lg, 2" sweat drops, 24 circuit 1 Ea 370 370 Motorized zone valve with operator complete, 24V and 3/4" 2 Ea 100 200

Air Handling Units 494,090 AHU 10,500 CFM 3 Ea 49,874 149,622 Surcharge for custom made 10,500 CFM AHU's (2 x's more) 3 Ea 49,874 149,622 LiCl SECO Desiccant Wheel, VFD 3 Ea 20,500 61,500 Enthalpy Wheel 3 Ea 20,500 61,500 Sensible Wheel 3 Ea 10,500 31,500 Extra Cooling Coils 3 Ea 5,000 15,000 Run-Around pump 3 Ea 250 750 AHU Heating Pump: 600 GPM Centrifugal end suction with VFD 2 Ea 5,676 11,352 AHU Cooling Pump: 700 GPM Centrifugal end suction with VFD 2 Ea 6,622 13,244

Solar Collectors 578,941 Collector panels, liquid with copper absorber plate, 4'X8', 5/32" 406 Ea 690 280,140 Collector panel mounting, Roof clamps 406 set 14 5,684 Propylene glycol 50 Gal 26.5 1,325 Air purger, 1" pipe size 1 Ea 85 85 Expansion Tank, up to 5 gal 1 Ea 69.4 69 6" black steel pipe welded with hangers 200.00 lf 66.00 13,200 3" black steel pipe welded with hangers 900.00 lf 35.00 31,500 2 1/2" black steel pipe with fittings & hangers 930.00 lf 30.00 27,900 2" black steel pipe with fittings & hangers 1,250.00 lf 23.00 28,750 1 1/2" black steel pipe with fittings & hangers 2,882.00 lf 18.00 51,876 1 1/4" black steel pipe with fittings & hangers 1,700.00 lf 17.00 28,900 1" black steel pipe with fittings & hangers 690.00 lf 14.00 9,660 Pipe Insulation Solar, Storage tank, domestic hot water 10,000.00 lf 6.00 60,000 Solar Panel Pump: 600 GPM Centrifugal end suction with VFD 2 Ea 5,676 11,352 Solar Loop Plate and Frame Heat exchanger 2 Ea 14250 28,500

Storage Tank 133,135 Custom welded Hot Water Storage Tank, 100,000 gallon, no weather 1 ea 100,000 100,000 Hot Water Storage Tank Insulation 13,254 sf 2.5 33,135

Concrete Foundations 26,400 Pile caps for 100,000 gallon Hot Water Storage Tank 88.00 cy 300.00 26,400

Ocean Cooling Piping/System 247,541 Polyethylene 160 psi, S.D.R. 7, 10" diameter 920 lf 2.39 2,199 Chlorine Treatment System 4000 each 1 4,000 Intake Filter 2 Ea 5000 10,000 Excavate and Backfill 800 lf 6 4,800 Underwater dredging/digging hole for return ocean water 20 cy 100 2,000 8" black steel pipe welded with hangers 200.00 lf 86.00 17,200 6" black steel pipe welded with hangers 500.00 lf 66.00 33,000 4" black steel pipe welded with hangers 550.00 lf 43.00 23,650 3" black steel pipe welded with hangers 300.00 lf 35.00 10,500 2 1/2" black steel pipe with fittings & hangers 530.00 lf 30.00 15,900 1 1/2" black steel pipe with fittings & hangers 150.00 lf 18.00 2,700 Water pump connection end suction 2.00 no 3,200.00 6,400 Ocean Water Pump: 900 GPM Centrifugal end suction with VFD 3 Ea 8,514 25,542 Titanium Plate Heat Exchanger Bid, 10psi, 1,373 gpm (no installation) 2 Ea 25,800 51,600 Titanium Plate Heat Exchanger Installation 2 Ea 4425 8,850 Vacuum Pump: 60 SCFM, 10 HP 1 Ea 29200 29,200

Total Cost Added 2,498,604

APPENDIX H: FIRST COST REDESIGN ADDITIONS

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

APPENDIX I: EXISTING LIFE-CYCLE MAINTANANCE

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- DUSTIN M. EPLEE -

The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

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The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

APPENDIX J: MCDUSTER REDESIGN LIFE-CYCLE MAINTANANCE

Non-Recurring CostsYear 1 Year 2

Year Cost Total Cost13900.120 Sprinkler Systems

Sprinkler Head 550 28.7 15785.00 20 66.95 36822.5 0.2% 24% 11.1% -$ -$ Fire System Test 1 950 950.00 0 0 0 0.2% 24% 11.1% -$ -$

18592.59 -$ -$ 14200.000 Elevators

Glass elevator, passenger, traction 1 1850 1850.00 0 0 0 0.2% 24% 11.1% -$ -$ Standard finish elevator, holeless hydraulic 1 5075 5075.00 0 0 0 0.2% 24% 11.1% -$ -$

7693.68 -$ -$ 15400.000 Plumbing

Water Meter 2 100 200.00 13 48.5 97 0.2% 24% 11.1% -$ -$ 25 7175 14350 0.2% 24% 11.1% -$ -$

Circulation Pumps 2 119 238.00 5 71.22 142.44 0.2% 24% 11.1% -$ -$ 15 3419 6838 0.2% 24% 11.1% -$ -$

Water Heater Gas 0 0 0.00 0 0 0 0.2% 24% 11.1% -$ -$ 12 2360 0 0.2% 24% 11.1% -$ -$

Valves 40 24 960.00 0 0 0 0.2% 24% 11.1% -$ -$ 1553.18 -$ -$

15500.000 HVACGas Fired Steam Boiler 0 0 0.00 0 0 0 0.2% 24% 11.1% -$ -$ Gas Fired H.W. Boiler 0 0.2% 24% 11.1% -$ -$ Air Cooled Chiller 0 0 0.00 0 0 0 0.2% 24% 11.1% -$ -$ Chemical Feed System 1 1100 1222.10 15 730.47 730.47 0.2% 24% 11.1% -$ -$ AHU's 3 5000 16665.00 10 38476 115428 0.2% 24% 11.1% -$ -$ Pumps 13 91 1314.31 0 0 0 0.2% 24% 11.1% -$ -$ Condensate Return Pump 0 0 0.00 0 0 0 0.2% 24% 11.1% -$ -$ Computer AC Units 0 0 0.00 0 0 0 0.2% 24% 11.1% -$ -$

0.00 0 0 0 0.2% 24% 11.1% -$ -$ Fan Coil Units (5 Tons) 0 0 0.00 0 0 0 0.2% 24% 11.1% -$ -$

0.00 0 0 0 0.2% 24% 11.1% -$ -$ Smoke Exhaust Fan 3 71.5 238.31 20 13428 40284 0.2% 24% 11.1% -$ -$ Exhaust Fans 13 66 953.24 15 1733 22529 0.2% 24% 11.1% -$ -$ Steam Humidifier 0 0 0.00 0 0 0 0.2% 24% 11.1% -$ -$ VAV Boxes 0 64 0.00 0 0 0 0.2% 24% 11.1% -$ -$ Transfer Fan 0 0 0.00 0 0 0 0.2% 24% 11.1% -$ -$ Cabinet Unit Heater 0 0 0.00 0 0 0 0.2% 24% 11.1% -$ -$

0.00 0 0 0 0.2% 24% 11.1% -$ -$ Unit Heater 0 0 0.00 0 0 0 0.2% 24% 11.1% -$ -$

0.00 15 722 0 0.2% 24% 11.1% -$ -$ Fin-Tube Radiator 0 0 0.00 0 0 0 0.2% 24% 11.1% -$ -$ Expansion Tank 2 0 0.00 5 12.35 24.7 0.2% 24% 11.1% -$ -$ Hot Water Storage Tank 1 0 0.00 12 19179 19179 0.2% 24% 11.1% -$ -$ Flat Plate Solar Collectors 1 1000 1000.00 0 0.2% 24% 11.1% -$ -$ Ocean Intake Filters 2 1000 2000.00 5 2500 5000 0.2% 24% 11.1% -$ -$

23392.96 -$ -$ 15500.218 Fuel Oil Specialties

Fuel Oil Tank 1 265 265.00 0 0 0 0.2% 24% 11.1% -$ -$ Fuel Oil Pump 1 91 91.00 0 0 0 0.2% 24% 11.1% -$ -$ Fuel Oil Meter 1 0 0.00 5 31 31 0.2% 24% 11.1% -$ -$

20 3753 3753 0.2% 24% 11.1% -$ -$ Oil Filter 1 5.6 5.60 0 0 0 0.2% 24% 11.1% -$ -$

401.74 -$ -$ 16000.000 Electrical16002.017 Emergency Power

450KW Generator 277/480V (indoor) 1 1250 1250.00 25 191450 191450 0.2% 24% 11.1% -$ -$

1387.50 -$ -$ 16002.030 Distribution

2500A Switchboard 277/480V 2 835 1670.00 0 0 0 0.2% 24% 11.1% -$ -$ Transformer "T-7" (K-rated) 28 206 5768.00 15 200.5 5614 0.2% 24% 11.1% -$ -$

8263.62 -$ -$

Lighting 1 15782 17533.80 0 0 0 0.2% 24% 11.1% -$ -$

16002.065 Signal & Comm. SystemWall phone location 10 0 0.00 8 44.34 443.4 0.2% 24% 11.1% -$ -$ Voice/Data location 124 0 0.00 8 44.34 5498.16 0.2% 24% 11.1% -$ -$ FACP (fire alarm control panel) 1 805 805.00 5 285.9 285.9 0.2% 24% 11.1% -$ -$

15 2856.45 2856.45 0.2% 24% 11.1% -$ -$ Security Alarm System 1 280 280.00 5 142.95 142.95 0.2% 24% 11.1% -$ -$

15 857.45 857.45 0.2% 24% 11.1% -$ -$

Material Index

Installation Index

+ Inst. IndexUnits

Service Contract Costs (Annual)

Total Annual Service Cost

Non-Recurring Costs

Page 132: SOLAR REACTIVATED DESICCANT DEHUMIDIFICATION & H … · house. I used the same radiant floor installation technique on my redesign for this 40+ million dollar museum as I learned

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- DUSTIN M. EPLEE -

The McDuster: The Next Generation of HVAC INSTITUTE OF CONTEMPORARY ART

Ocean Cooling, Solar Heating, Desiccant Conditioning

Year 9 Year 10 Year 11 Year 12 Year 13 Year 14 Year 15 Year 16 Year 17 Year 18 Year 19

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